US3882705A - Roll eccentricity correction system and method - Google Patents

Roll eccentricity correction system and method Download PDF

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Publication number
US3882705A
US3882705A US448869A US44886974A US3882705A US 3882705 A US3882705 A US 3882705A US 448869 A US448869 A US 448869A US 44886974 A US44886974 A US 44886974A US 3882705 A US3882705 A US 3882705A
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Prior art keywords
roll
force
eccentricity
stand
gauge
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US448869A
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English (en)
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Richard Q Fox
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AEG Westinghouse Industrial Automation Corp
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Westinghouse Electric Corp
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Priority to US448869A priority Critical patent/US3882705A/en
Priority to FR7507305A priority patent/FR2272759B1/fr
Priority to JP50027259A priority patent/JPS50122453A/ja
Priority to BE154106A priority patent/BE826408A/fr
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Publication of US3882705A publication Critical patent/US3882705A/en
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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    • 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 unloaded ro'll opening and the speed at each tandem mill stand or for each reversing mill pass are set up by the operator to produce successive workpiece (strip or plate) reductions resulting in work product delivered at the desired gauge.
  • the loaded roll opening at a stand equals the stand delivery gauge on the basis of the usually justifiable assumption that there is little or no elastic workpiece recovery.
  • a stand automatic gauge control system is employed such that the stand delivery gauge can be closely controlled.
  • a stand gauge control system is normally used for a reversing mill stand and for predetermined stands in tandem rolling mills.
  • the well known gauge meter or roll force gauge control system has been widely used to produce stand gauge control in metal rolling mills, and particularly in tandem hot steel strip rolling mills and reversing plate mills where experience has demonstrated that roll force control is particularly effective.
  • Earlier publications and patents such as an article entitled Installation and Operating Experience with Computer and Programmed Mill Controls by M. D. McMahon and M. A. Davis in the 1963 Iron and Steel Engineer Yearbook at pages 726 and 733, an article entitled Automatic Gauge Control for Modern Hot Strip Mills by J. W. Wallace in the December 1967 Iron and Steel Engineer at pages 75 to 86, U.S. Pat. No. 3,561,237 issued Feb. 9, 1971 to Eggers et al. and U.S. Pat. No.
  • the roll force gauge control system uses Hookes law in controlling the screwdown position at a rolling stand, i.e. the loaded roll opening under workpiece rolling conditions equals the unloaded roll opening or screwdown position plus the mill spring stretch caused by the separating force applied to the rolls by the workpiece.
  • a load cell or other force detector measures the roll separating force at each controlled roll stand and the screwdown position is controlled to balance roll force changes from a reference value and thereby hold the loaded roll openinig at a substantially constant value.
  • the roll force gauge control system is an analog arrangement including analog comparison and amplification circuitry which responds to the roll force signal F and the screwdown position signal SD to control the screwdown position and hold the following equality:
  • the rolling operation is begun and the screwdowns are controlled to regulate the workpiece delivery gauge from the reversing mill stand or from each roll force controlled tandem mill stand, such that the loaded roll opening SD is maintained constant or nearly constant.
  • the lock-on screwdown position and the lock-on roll separating force are measured to establish what strip gauge should be maintained out of that roll stand.
  • the roll stand separating force and the roll stand screwdown position values are monitored and any undesired change in roll separating force is detected and compensated for by a corresponding correction change in screwdown position.
  • the lock-on gauge LOG is equal to the lock-on screwdown LOSD plus the lock-on force LOF multiplied by the mill stand spring modulus K.
  • the workpiece strip delivery gauge G leaving the roll stand at any time during the rolling operation is equal to the unloaded screwdown position SD plus the roll separating force F multiplied by the mill spring modulus K.
  • the gauge error is derived by subtracting the lock-on gauge from the delivery gauge.
  • Equations 2, 3 and 4 set forth these relationships.
  • the invention isapplicable to various types of rolling mill stands in which roll force gauge control is employed.
  • the invention can be suitably adapted for application in hot steel plate reversing andother rolling mills.
  • a workpiece 14 enters the roll stand 10 at the entry end and it is reduced in thickness as it is transported throughone or more roll stands to the delivery end of the rolling mill.
  • the entry workpiece would be of known steel grade and it typically would have a known j gauge or thickness.
  • the delivered workpiece would have a desired thickness based upon the production order for which it is intended.
  • a control system and method for controlling delivery gauge or thickness of workstrip product leaving a metal rolling mill stand includes the measurement of the eccentricity of each back-up roll when there is no workstrip positioned between the work rolls of the roll stand, with the work rolls rotating at a relatively slow speed such as thread speed of operation and the control of the roll stand in accordance with that eccentricity. The measured eccentricity is then used in the control of the product delivery thickness.
  • FIG. 1 shows a schematic diagram of a roll stand and a gauge control system arranged for operation in accor-.
  • FIG. 3 shows an illustrative logic flow chart of the eccentricity determination program operative in relation to a roll stand
  • FIG. 4 shows a logic flow chart to illustrate the operation of the back-up roll eccentricity measurement program operative with the gauge control system shown in FIG. 1;
  • FIG. 5 shows a flow chart to illustrate the operation of the back-up roll eccentricity implementation program operative with the gauge control system shown in FIG. 1; and 1
  • FIG. 6 is a functional illustration of the eccentricity.
  • the. sum of the unloaded work roll opening and the mill stretch substantially defines the workpiece gauge delivered from any particular stand in accordance with I-Iookes law.
  • a pair of screwdown motors 26 position respective screwdowns 28 (only one shown for the roll stand) which clamp against opposite ends of the back-up rolls and thereby apply pressure to the work rolls.
  • the screwdown motors26 are merely illustrative of roll opening positioning devices, and well known hydraulic positioning cylinder devices having a faster response to gauge error may be preferred in actual practice.
  • a conventional roll opening position detector orencoder 30 provides an electrical signal representation of screwdown position.
  • Roll force detection is provided atthe roll stand 10 by a conventional load cell 32 which generates an electrical analog signal proportional to the roll separating force between the work rolls 20 and 22.
  • a conventional load cell 32 which generates an electrical analog signal proportional to the roll separating force between the work rolls 20 and 22.
  • each roll force con- there is shown in FIG. 1 a four high rolling mill stand I stand 10.
  • the gauge control system 12 can include a programmed general purpose process control digital computer system, which is interfaced with the various mill sensors and the various mill control devices to provide control over the operation of the mill stand 10. According to user preference, the gauge control system 12 can also include well known and conventional manual and/or automatic analog controls for back-up operation in performing other preselected mill functions.
  • a suitable digital computer system for the on-line roll force gauge control system 12 would be a Prodac 2000 (P2000) Sold by Westinghouse Electric Corporatiton.
  • P2000 Prodac 2000
  • a descriptive book entitled Prodac 2000 Computer Systems Reference Manual has been published in 1970 by Westinghouse Electric Corporation and made available for the purpose of describing in greater detail this computer system and its operation.
  • the digital computer system is associated with well known predetermined input systems, typically including a conventional contact closure input system which scans contact or other signals representing the sensed status of various process conditions, a conventional analog input system which scans and converts process analog signals, and operator controlled and other information input devices and systems such as paper tape, teletypewriter and dial input systems.
  • Various kinds of information can be entered into the computer system through the input devices including, for example, desired strip delivery gauge and temperature, strip entry gauge and width and temperature (by entry detectors if desired), grade of steel being rolled, plasticity tables, hardware oriented programs and control programs for programming system, and so forth.
  • the contact closure input systems and the analog input systems interface the computer system with the process through the medium of measured or detected variables, which include the following:
  • controlled devices are operated directly by means of output system contact closures or by means of analog signals derived from output system contact closures through a digital to analog converter.
  • the principal control action outputs from the gauge control system 12 includes a roll opening positioning command signal applied to roll opening position control 40in operating the screwdown motor 26 for desired screw movement, and a speed control signal applied to the drive motor 24 to cause a change in drive speed to compensate the force on the workpiece strip for a change in thickness being made by a screwdown movement.
  • Display and printout systems such as numeral display, tape punch, and teletypewriter systems can be also associated with the outputs of the digital computer system in order to keep the mill operator generally informed about the mill operation and in order to signal the operator regarding an event or alarm condition which may require some action on his part.
  • the gauge control system 12 uses Hookes law to determine the total amount of screwdown movement required at the roll force controlled stand 10 at the calculating point in time for roll force and gauge error correction, i.e. for loaded roll opening and stand delivery gauge correction to the desired value. The calculation defines the total change in the unloaded roll opening required to correct for determined back-up roll eccentricity or other roll force and gauge error causing conditions.
  • a mill spring curve 62 defines the separation between a pair of mill stand work rolls as a function of roll separating force and as a function of screwdown position.
  • the slope of the mill spring curve 62 is the well known mill spring constant K.
  • the indicated theoretical face intersect represents theoretical roll facing and it is for this theoretical condition that the screwdown position is assigned to a zero value.
  • roll facing actually occurs when the screwdown position is at a slightly negative value because of the non-linearity of the lower part of the mill spring curve.
  • a definition of the screwdown calibration as being correct for the indicated theoretical conditions is, however, convenient and appropriate for mill operation.
  • the stand workpiece delivery gauge equals the unloaded roll opening as defined by the screwdown position SD plus the mill stretch caused by the workpiece. If the screwdown calibration is incorrect, i.e. if the number assigned to the theoretical roll facing screwdown position is something other than zero because of roll crown wear or other causes, the stand workpiece delivery gauge equals the unloaded roll opening plus the mill stretch plus or minusthe calibration drift.
  • the amount of mill stretch depends on the characteristic reduction curve for the workpiece.
  • a reduction curve 64 for a workpiece strip of predetermined width represents the amount of force required to reduce the workpiece from a stand entry thickness (height) of H
  • the workpiece plasticity P is the slope of the curve 64, and in this case the curve 64 Desired workpiece deliver gauge H is the initial con 1 ASRF i (6) dition IC produced in this case since the amount of force required to reduce the workpiece from H to H is equal to the amount of roll separating force required to stretch the rolls to a loaded roll opening H i.e. the intersection of the mill spring curve at an initial screwdown opening SD indicated by mill spring curve 62 and the workpiece reduction curve 64 lies at the desired gauge value.
  • the stand delivery gauge increases by a gauge error amount GE to I-I during a workpiece pass to produce a present condition PC, in this instance because the workpiece plasticity decreases and because the workpiece entry thickness increases to H as represented by the reduction curve 66, the stand screwdowns must be closed to a value which causes a future correct gauge condition FC.
  • the intersection of the mill spring curve and the new reduction curve 66 lies at the desired gauge H as provided by a spring curve location indicated by the reference character 68.
  • corrective screwdown closing causes the unloaded screw opening to be reduced by an amount AS to a new value which adds with the new mill stretch to equal the desired gauge H
  • desired screwdown correction AS is calculated to enable roll force gauge control operation in, accordance with the following programmed relationship algorithm:
  • each stand spring constant K is relatively accurately known. It is the first determined by the conventional work roll screwdown test, and it can be recalculated prior to each workpiece pass on the basis of the workpiece width and the backup roll diameter. Each resultant spring curve is stored for on line gauge control use.
  • the operative value of the workpiece plasticity P at each stand is also relatively accurately determined.
  • P tables can be stored in the storage memory of the digital computer system associated with the gauge control system 12 shown in FIG. 1 to identify the various values of P which apply to the mill stand 10 for various grade class and gauge class workpieces under various operating conditions and at various operating times during the rolling of the workpiece strip 14.
  • a main advantage of using the roll force gauge control system is the ability to detect error changes in strip gauge the instant they take place as the product is being rolled in the roll stand.
  • a shift in strip delivery gauge or thickness can be caused by a change in entry thickness, or a change in hardness as usually caused by a change in temperature. This change in delivery gauge can be immediately detected by feedback information monitoring of the roll separating force on the roll stand.
  • the screwdown correction AS can be determined by the relationship:
  • X is the amount of roll opening change and hence GE- P* AF (8) i. l y
  • the eccentricity measurement is accomplished by facing the work rolls 20 and 22 shown in FIG. 1 to a 60 predetermined force and rotating them at a typical operating speed.
  • the rotary transducers 34 and 36 will respectively indicate the exact positionof each back-up roll as it rotates, and the load cell 32 will indicate the force fluctuations caused by the eccentricity of the.
  • 0 is the angle of rotation of a selected back-up roll
  • A is the maximum force component caused by the eccentricity of the top back-up roll
  • B is the maximum force component caused by the eccentricity of the bottom back-up roll.
  • C is the angular offset between the top and bottom back-up roll eccentric axes.
  • the second step is to allow the back-up rolls to rotate until the slight difference in rotational frequency has caused the bottom roll to be 180 offset from its initial relationship to the top roll.
  • the equation for this condition would be:
  • the control system 12 now has enough information to permit the determination of the eccentricity of the top and bottom back-up rolls.
  • the eccentricity of the bottom roll is determined as follows:
  • the eccentricity of the top roll is determined as follows:
  • the signals supplied to the control system are the roll force signal from the load cell and the pulse signals from the pulse generator coupled to the upper back-up roll to indicate the rotational position of the upper roll and the pulse signals from the pulse generator coupled to the lower back-up roll to ingauge control system is programmed to sample the force signal over one complete rotation of the upper and lower back-up rolls; for theoretical purposes only one complete rotation is needed but in actual practice for mechanical purposes the force signal for four or five rotations of the back-up rolls is sampled to provide statistical averages.
  • the control system is programmed to sample the force signal and save a predetermined number such as 360 samples in memory, with one sample being made for each degree of rotation of the upper back-up roll, and in this way obtain roll force samples in memory for the rotation angle of the top back-up roll going from 0 to 360, with no workpiece positioned between the work rolls and with a predetermined roll force such as 1000 metric tons being provided for the roll stand under consideration.
  • the second step of measuring the back-up roll eccentricity is to separate the work rolls and rotate one of the back-up rolls, for example the bottom back-up roll, until the pulse generator operative with the bottom back-up roll indicates that the bottom back-up roll is now rotated substantially 180 from its relationship to the top back-up roll to in effect provide a 180 phase shift of the bottom back-up roll, and then again sample the roll force signal for each degree of rotation of a complete 360 rotation of the top back-up roll and save in memory the resulting 360 roll force signal samples. It is readily apparent that a fewer number of samples, such as 72 samples will give an approximation of the back-up roll eccentricity in this regard. These roll force signal measurements are all made with respect to the top back-up roll rotational position as a reference.
  • the back-up roll caused error in the measured roll force signal for a given rolling mill roll stand can be in the order ofi of the desired delivery gauge, particularly in relation to the last roll stand of a rolling mill.
  • the speed of response is fast enough to actually remove the eccentricity impressions by changing the roll opening in phase with the eccentricity as required to correct the gauge error resulting from the eccentricity of either one or both of the back-up rolls.
  • FIG. 3 there is illustrated the eccentricity correction to be applied to the roll opening of the mill stand in relation to the angular rotation position of a particular back-up roll.
  • the roll force error caused by the back-up roll eccentricity is shown by the curve. 1
  • FIG. 4 there is shown a flow chart to illustrate the eccentricity measurement program operation for the back-up roll eccentricity determination in accordance with the present invention.
  • the roll stand force is read and checked in relation to predetermined limits, such as high limit of 1500 metric tons and a low limit of 800 metric tons, and if the force reading is outside of those limits at step 77 an alarm is provided for the operator and the program ends.
  • predetermined limits such as high limit of 1500 metric tons and a low limit of 800 metric tons
  • the roll stand speed is read and checked in relation to predetermined limits, such as a high limit of 100 RPM and a low limit of 50 RPM, and if the speed is outside of those limits at step 81 an alarm is provided for the operator and the program ends.
  • step 83 the eccentricity index is initialized and a program loop is begun at step 85 where the stand roll force is read as the work rolls are rotating.
  • the program operation is such that 90 force sample readings will be taken during one back-up roll rotation.
  • step 87 the angular position of the top back-up roll is read from the rotary transducer 34, and 90 such readings will be taken or one reading every 4 of rotation.
  • step 89 the angular position of the bottom back-up rollis read from the rotary transducer 36, and 90 such readings will be taken.
  • the position readings are stored in memory and a delay of about one-tenth second is.
  • step 95 a check is made to see if 90 sample readings have been taken, and if not the program loops back to step 85 and if so the program goes to step 97 for a delay of 5 seconds to wait 1 until the bottom back-up roll has rotated 180 in relation to the top back-up roll.
  • step 99 a check is made to see if the bottom back-:up roll is 180 out of phase in relation to the top back-up roll, and if not the program loops back to step 97 for another time delay of 5 secondsand then anotherc home is made at step 99 until. the 180 degrees out of phase condition has occurred.
  • step 101 the program goes to step 101 to initialize the 180 out of phase eccentricity index.
  • step 103 the stand roll force is read as the work rolls are rotating. Again, 90 force sample readings are taken during one back-up roll rotation.
  • step 105 the position of the top back-up roll is read from the rotary transducer 34, and 90 such readings will be taken or one reading every 4 of rotation.
  • step 107 the position of the bottom back-up roll is read from the rotary transducer 36, and ninety such readings will be taken.
  • step 109 the position readings are stored in memory and a delay of about one-tenth second is provided.
  • step 111 the index is incremented such that the next force and position sample readings are taken the next time through this loop.
  • a check is made to see if 90 sample readings have been taken, and if not the program loops backto step 103 and if so the program goes to step 115 to calculate the average stand roll force by summing up all force readings taken during the first 90 samples and dividing by the number of such samples.
  • the top back-up roll eccentricity E is calculated in accordance with the relationship of above equation (25), at step 119 the bottom back-up roll eccentricity E, is calculated in accordance with above equation (18), and then the program ends.
  • FIG. 5 there is shown a flow chart to illustrate the eccentricity implementation program operation of the gauge control system 12 shown in FIG. 1.
  • the position of the top back-up roll 16 is read from the rotary transducer 34.
  • the eccentricity E value is obtained from the look up table provided by the FIG. 4 program.
  • the position of the bottom back-up roll 18 is read from the rotary transducer 36.
  • the eccentricity 15,, value is obtained from the look up table provided by the FIG. 4 program.
  • the eccentricity correction is obtained by adding together the individualeccentricity values, in accordance with the relationship indicated by above equation (26), which is used to calculate the gauge error at step 141.
  • the roll opening correction is calculatedin accordance with above equation (12), and
  • this roll opening correction is output to the roll opening position control 40 shown in FIG. 1.
  • FIG. 6 there is functionally illustrated the eccentricity determination and the control of workpiece delivery gauge in relation to a roll stand 150.
  • the average stand roll force F is determined.
  • the force reading F is established for in the order of every four degrees of rotation of the top backup roll 16 in accordance with above equation (I3).
  • the force reading F is established in accordance with above equation (14).
  • the eccentricity E of the bottom back-up roll 18 is established in accordance with above equation (18)
  • the eccentricity E of the top back-up roll 16 is established in accordance with above equation (25).
  • the gauge error including eccentricity is established in accordance with above equation (26), and at block 164 the roll opening correction is established in accordance with above equation (12).
  • MM In VAR SPEED MPH 11 1N ARR F1 WDMZ IN ARR F2 MISC I VAR TDPANGLE M166 IN VAR BOTANGLE @0187 IN ARR m M88 IN ARR HOT! 112 I ARR m 2 mac I ARR 801'2 MICE I ARR ET 9 22 nowadays I ARR EB @2713 I VAR K ⁇ AZIM IN VAR ISPEED WW3 'I 0P VAR LUSPEED GMCM IN DP VAR HIFORCE WW1 I DP VAR OFORCE WW2 IN DP VAR AVG-FORCE WW5 IN DP VAR DELTM MIN?

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Measurement Of Length, Angles, Or The Like Using Electric Or Magnetic Means (AREA)
  • Length Measuring Devices With Unspecified Measuring Means (AREA)
US448869A 1974-03-07 1974-03-07 Roll eccentricity correction system and method Expired - Lifetime US3882705A (en)

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US448869A US3882705A (en) 1974-03-07 1974-03-07 Roll eccentricity correction system and method
FR7507305A FR2272759B1 (fr) 1974-03-07 1975-03-07
JP50027259A JPS50122453A (fr) 1974-03-07 1975-03-07
BE154106A BE826408A (fr) 1974-03-07 1975-03-07 Dispositif et methode de correction de l'excentricite dans les laminoirs

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Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4038848A (en) * 1974-05-31 1977-08-02 Hitachi, Ltd. Method and apparatus for controlling eccentricity of rolls in rolling mill
US4126027A (en) * 1977-06-03 1978-11-21 Westinghouse Electric Corp. Method and apparatus for eccentricity correction in a 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
EP0219844A1 (fr) * 1985-10-21 1987-04-29 Nippon Steel Corporation Méthode de commande de profil d'une tôle pendant le laminage
US4685063A (en) * 1984-07-05 1987-08-04 Siemens Aktiengesellschaft Process and device for compensation of the effect of roll eccentricities
GB2253719A (en) * 1991-03-15 1992-09-16 China Steel Corp Ltd Compensating roll eccentricity of a rolling mill

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS51138468A (en) * 1975-05-27 1976-11-30 Ishikawajima Harima Heavy Ind Co Ltd Method of measuring eccentric state of rolls

Citations (5)

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US3194035A (en) * 1961-05-08 1965-07-13 Davy And United Instr Ltd System for eliminating cyclic variations in rolling mill gauge errors
US3460365A (en) * 1966-02-21 1969-08-12 Davy & United Eng Co Ltd Rolling mills
US3543549A (en) * 1967-11-21 1970-12-01 Davy & United Eng Co Ltd Rolling mill control for compensating for the eccentricity of the rolls
US3683653A (en) * 1971-02-22 1972-08-15 Gen Electric Motor drive system for rolling mill
US3709009A (en) * 1970-03-20 1973-01-09 Ishikawajima Harima Heavy Ind Method for detecting eccentricity and phase angle of working or backing roll in rolling mill

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JPS538304A (en) * 1976-07-13 1978-01-25 Toyota Motor Corp Marking method of sintered product

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
US3194035A (en) * 1961-05-08 1965-07-13 Davy And United Instr Ltd System for eliminating cyclic variations in rolling mill gauge errors
US3460365A (en) * 1966-02-21 1969-08-12 Davy & United Eng Co Ltd Rolling mills
US3543549A (en) * 1967-11-21 1970-12-01 Davy & United Eng Co Ltd Rolling mill control for compensating for the eccentricity of the rolls
US3709009A (en) * 1970-03-20 1973-01-09 Ishikawajima Harima Heavy Ind Method for detecting eccentricity and phase angle of working or backing roll in rolling mill
US3683653A (en) * 1971-02-22 1972-08-15 Gen Electric Motor drive system for rolling mill

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4038848A (en) * 1974-05-31 1977-08-02 Hitachi, Ltd. Method and apparatus for controlling eccentricity of rolls in rolling mill
US4126027A (en) * 1977-06-03 1978-11-21 Westinghouse Electric Corp. Method and apparatus for eccentricity correction in a rolling mill
FR2392737A1 (fr) * 1977-06-03 1978-12-29 Westinghouse Electric Corp Procede et installation pour corriger l'excentricite d'un laminoir
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
US4685063A (en) * 1984-07-05 1987-08-04 Siemens Aktiengesellschaft Process and device for compensation of the effect of roll eccentricities
EP0219844A1 (fr) * 1985-10-21 1987-04-29 Nippon Steel Corporation Méthode de commande de profil d'une tôle pendant le laminage
US4776192A (en) * 1985-10-21 1988-10-11 Nippon Steel Corporation Controlling the profile of sheet during rolling thereof
GB2253719A (en) * 1991-03-15 1992-09-16 China Steel Corp Ltd Compensating roll eccentricity of a rolling mill
US5181408A (en) * 1991-03-15 1993-01-26 China Steel Corp., Ltd. Method of measuring and compensating roll eccentricity of a rolling mill

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JPS50122453A (fr) 1975-09-26
FR2272759A1 (fr) 1975-12-26
BE826408A (fr) 1975-09-08
FR2272759B1 (fr) 1978-11-03

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