US3197986A - Control system for rolling mills - Google Patents

Control system for rolling mills Download PDF

Info

Publication number
US3197986A
US3197986A US150738A US15073861A US3197986A US 3197986 A US3197986 A US 3197986A US 150738 A US150738 A US 150738A US 15073861 A US15073861 A US 15073861A US 3197986 A US3197986 A US 3197986A
Authority
US
United States
Prior art keywords
thickness
force
wedge
rolls
gauge
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.)
Expired - Lifetime
Application number
US150738A
Other languages
English (en)
Inventor
Robert P Freedman
Peter J Barnikel
James H Torrance
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.)
General Dynamics Corp
Original Assignee
General Dynamics Corp
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
Priority to BE624523D priority Critical patent/BE624523A/xx
Application filed by General Dynamics Corp filed Critical General Dynamics Corp
Priority to US150738A priority patent/US3197986A/en
Priority to FR914600A priority patent/FR1345182A/fr
Priority to GB42113/62A priority patent/GB968778A/en
Application granted granted Critical
Publication of US3197986A publication Critical patent/US3197986A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • B21B31/30—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis mechanically, e.g. by thrust blocks, inserts for removal by wedges or their equivalent
    • 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
    • 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
    • B21B31/32—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis by liquid pressure, e.g. hydromechanical adjusting
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable
    • Y10T74/2105—Memory devices

Definitions

  • CONVERTER 1 SHIFT REGISTER 4fl DIGITAL TO ANALOG 4/ CONVERTER LINEAR HYDRAULIC ACTUATOR INVENTORS ROBERTS F. FR DMAN PETER J. BARN a BY JAMES H. TORRANOE THE/12 ATTORNEYS Aug. 3, 1965 R. P. FREEDMAN ET AL 3,197,986
  • I MULTIPLY I I I I SQUARE ROOT I I FUNCTION I (GENERATOR) I I u I I MULTIPLY I UL I I I DIVIDE I I LL I I I I FUNCTION I GENERATOR I uL I T (uL) I I I I I I I I e I I I I I I (s-sn I I MULTIPLY I I I I L E w I I MULTIPLY I P .J
  • An additional object of the invention is to provide an adjusting device for a rolling stand which is capable of much faster response than has been possible heretofore.
  • a further object of the invention is to provide a new and improved control system for rolling operations capable of predicting accurately the force which must be applied a to produce material having a desired thickness and making any necessary changes in the force rapidly.
  • a rolling stand having a pair of adjacent compressing or Working rolls supported in a frame
  • fluid-actuated rapid response adjusting means interposed between the frame of the stand and one of the rolls adapted to vary the distance between that roll and the frame of the stand so as to vary the pressure applied to a material passing between the rolls, and means for determining in advance the pressure necessary to accomplish a desired reduction in the thickness of the material and controlling the adjusting means to produce a force on the roll corresponding to the necessary pressure.
  • the system includes 3,197,986 Patented Aug.
  • the system preferably includes a gauge for detecting the force applied between the frame and the rolls and a device for comparing the applied force with the desired force and varying the condition of the adjusting means to eliminate any difference between them.
  • the adjusting means comprises wedge means located between the stand frame and one of the working-rolls and linear fluid actuating means such as a hydraulic ram connected to drive the Wedge and thereby adjust the pressure.
  • the wedge means includes a permanent layer of antifriction material such as Teflon fabric while, in another embodiment, rollers are held captive in wedge tracks or races having inclined surfaces in two adjacent members, one of which is movable relative to the other.
  • FIG. 1 is a schematic diagram illustrating the arrangement of a typical control system according to the invention
  • FIG. 2 is a block diagram showing one form of delay device suitable for use in the system shown in FIG. 1;
  • FIG. 3 is a partial sectional view illustrating a preferred form of adjusting device for use in the system of FIG. 1;
  • FIG. 4 is a sectional view illustrating another form of rapid response adjusting device
  • FIG. 5 is a sectional view taken along the line 55 of FIG. 4 and looking in the direction of the arrows;
  • FIG. 6 is a partial sectional view showing another form.
  • FIG. 7 is a schematic block diagram illustrating the arrangement and mode of operation of the force computer.
  • a generally conventional steel mill rolling stand 16 shown partly in section, includes a pair of working rolls 11 and 12 and corresponding backup rolls 13 and 14, the lower support roll 14 being mounted in a fixed location in the frame 10a of the stand and the upper support roll 13 being capable of vertical motion in the stand frame.
  • a strip or sheet 15 of steel or the like which is to be rolled passes between the working rolls 11 and 12 and an adjustable screw-down device 16 is provided to force the upper backup roll 13 and working roll 11 toward the lower rolls so that the nominal separation between the working rolls can be set before rolling.
  • the stand 10 also includes a fluid-actuated rapid response adjusting de vice 17, which is described in detail hereinafter for varying the pressure applied by the rolls promptly in accordance with a force control signal supplied through a line 27a.
  • a fluid-actuated rapid response adjusting de vice 17 which is described in detail hereinafter for varying the pressure applied by the rolls promptly in accordance with a force control signal supplied through a line 27a.
  • the control system includes a force computer and a reset unit 21 Which make the necessary computations in the manner described below based on information received from a temperature gauge 19, two conventional tension gauges 22 and 23 which measure the tension of the strip entering and leaving the stand, respectively, and two thickness gauges 24 and positioned to measure the thickness of the incoming and outgoing portions of the strip, respectively, each of the latter being, for example, a beta or X-ray gauge of any well-known type. Also a tachometer Z6 is connected to one of the rolls or strip 15 to detect the velocity of the strip 15 passing through the stand.
  • the force computer 20, illustrated schematically in FIG. 7, is arranged in any well-known manner to calculate the amount of force which must be applied between the Working rolls 11 and 12 to produce a pressure on the strip which will reduce the strip thickness from that entering the stand to the desired thickness. These calculations are based on the following equations:
  • Equation 1 has been taken from the article Theory of Rolling by Ford in Metallurgic Reviews, vol. 2, No. 1, p. l (1957) while Equation 2 is derived by Stone in the article The Rolling of Thin Strip in the Iron and Steel Engineer Yearbook, 1953, p. 115. Part II of the latter article appears at page 981 of the 1956 Iron and Steel Engineer Yearbook. By solving these two equations simultaneously, the iteration process, which would be necessary if Equation 2 were used by itself, is avoided. Relation 3 and the manner of determining the function f of Relation 4 for a particular set of conditions also appear in the 1953 Stone article at page 118.
  • the strip temperature is transmitted from the gauge 19 through the line 19a to determine S the two tension gauges 22 and 23 provide tension data to determine S; to the computer through two corresponding lines 22a and 23a, and the incoming thickness gauge 24 and the tachometer 26 transmit information to a delay device 38 through lines 24a and 26a, the delay devicebeing connected to the computer by the line 38a.
  • a temperature gauge 19 may be omitted since 'S will then be constant for the particular material being rolled.
  • the output signal from the computer representing the force necessary to produce a desired reduction in thickness is transmitted to a difference amplifier 27 through a line 27a for comparison with the actual force applied between the stand and the working roll which is detected by a conventional force gauge 28 and represented by asignalon a line 28a.
  • a conventional force gauge 28 is the ASEA Presductor force transducer.
  • the closed loop control thus provided assures that the actual pressing force in the stand is at all times equal to the necessaryy force as determined by the computer despite the existence of uncontrollable factors which may affect the force, such as eccentricity of the backup and working rolls, for example.
  • five input terminals 29, 3t), 31, 32,, and 33 are connected to the computer so that an operator can enter those factors which do not change during the rolling operation.
  • One of these input terminals indicated by the numeral 29, receives a signal corresponding to the desired strip thickness after rolling (t while the signals applied to the other terminals correspond to the work roll radius (R), the strip width (W), the constrained yield stress (S of the material being rolled at a given temperature, and the nominal thickness of the incoming strip (t
  • the'yield stress is a function of the material being rolled and its temperature, for non-ferrous as well as ferrous metals.
  • FIGURE 9.21 shows the variation of yield stress, or resistance to deformation as a function of temperature.
  • the value of (S is determined by taking the average of the outgoing and incoming tensions, as indicated by the gauges 23 and 22, and it should be readily apparent that if the stand 10 is the first of the series and a strip with no tension is supplied to the stand, the gauge 22 can be omitted since the tension of the outgoing strip is then equal to (28,).
  • the computer may be of either the analog or the digital type and the specific arrangement of the computer will be readily apparent to those skilled in the art from a consideration of the following calculations which are to be made, a description of the structure and operation of a specific computer is unnecessary and it will be suflicient to describe the mathematical steps to be performed which are illustrated'in the diagram of FIG. 7.
  • the flattened radius R of the work roll is calculated from Equation 1, the constant 0 being built into the computer and having a value dependent on the material of which the working rolls are made. Then, from the equation L (t t )R, the length of contact L of the roll with the strip can be determined.
  • the next step is to form E t and then calculate the value of Q e t 1 uL This expression is multiplied by the difference between the constrained yield stress S and the average tension S,
  • the computer output signal representing the necessary force is transmitted by a line 27a to the difference amplifier 27 for comparison, with the actual force, as measured by the gauge 28. Any deviation of the actual force from the computed force detected in this manner actuates the rapid response adjusting device 17 to equalize the actual force with the desired force, thereby assuring that the proper pressure is applied to the strip of material at all times without any delay in response to variations in the actual incoming and outgoing thickness and tension.
  • the computer also includes a conventional device (not shown) for comparing the actual incomingstrip thicknesses measured by the gauge 24 with the nominal thickness represented by the signal at the input terminal 29 and making an appropriate correction for any difference between them in the output signal representing the required force. It will be apparent that, if desired, the computer 20 may be set to overcompensate for. relatively large indicated thickness reductions, thus reducing the tendency of variations in thickness to grow back in subsequent rolling stands because of the increased hardness of the material caused by the larger reduction in thickness.
  • the delay device 38 In order to control the application of force in the stand into the strip 15 at exactly the right time to correct a thickness variation measured by the gauge 24, the delay device 38 must be highly accurate.
  • One form of suitable delay device is shown inFIG. 2 wherein the thickness information from the line 24a is converted from analog to digital form by an analog to digital converter 39. Digital information from this unit is carriedthrough a shift register 40 comprising a plurality of information storage units, the number of which correspond to the distance between the gauge 24 and the line between the centers of the working rolls 11 and 12.
  • the rate of transfer of the information through the shift register is controlled according to the velocity of the rolls 11 and 12, as measured by the tachometer and indicated on the line 26a, the response time of the system being taken into account, and the delayed information is then reconverted to analog form, if necessary, by a converter 41 for transmission to the computer on the line 38a.
  • the output thickness is supplied through a line a to a difference amplifier 35 in the reset unit 21 where it is compared with the desired output thickness, as represented at the terminal 29, and an error signal is transmitted to the computer on a line 35a to correct the computation of the required force.
  • the reset unit error signal is effective to compensate for any and all types of inaccuracies in the computer, the tension gauges, the incoming thickness gauge, the tachometer, and the force gauge, as well as any inaccuracies in the signals applied to the terminals -33.
  • a filter 36 is included in the line a to smooth out rapid changes in the error signals so that the reset unit provides relatively long term correction of the force signal.
  • the computer determines the force required to reduce the thickness of the strip to the desired value in the manner described above and transmits a signal representing this force to the difference amplifier 27.
  • the actual force in the stand is, as previously mentioned, detected by the gauge 28 and compared with the desired force and a control signal on the line 18 is transmitted to the adjusting device 17. Also, the actual outgoing strip thickness is detected by the gauge 25 and compared with the desired output thickness in the reset unit 21 to produce an error signal which revises the force calculation in the computer 20..
  • a tapered wedge 42 is interposed between the frame 10a of the stand and a support block 43 for the upper backup roll.
  • This wedge is connected to a linear hydraulic actuator 44 which may comprise, for example, a hydraulic ram receiving hydraulic fluid under pressure from two conduits 4-5 and 46 through a conventional electrohydraulic servo control valve 47 arranged to regulate the position of the linear hydraulic actuator 44 in accordance with the control signal received from the line 18.
  • a permanent layer 49- of antifriction material is mounted on each of the working surfaces of the Wedge.
  • the best material presently known for this purpose is a fabric made of fibers of Teflon interwoven with fibers of cotton or glass or other bondable material.
  • This fabric is preferably made so that only the Teflon fibers appear at the outer surfaces and the cotton fibers are adjacent to the body of the Wedge and are bonded thereto by a conventional adhesive such as a phenolformaldehyde resin, thereby holding the fabric in place on the wedge surface.
  • a conventional adhesive such as a phenolformaldehyde resin
  • the Wedge can be accelerated rapidly in either direction without requiring excessive hydraulic flow rates even when the strip 15 is under extremely high pressure.
  • a total load force of two million pounds acting on a bearing area of about two hundred square inches so as to produce a compressive stress on the wedge of about 10,000 psi a wedge having a taper of 0.060 inch per inch can be accelerated at a rate of about five inches per second per second by a ram supplied with hydraulic fluid at a pressure of 3,300 p.s.i.
  • the thickness control system of the present invention can respond promptly to correct substantially all variations in the thickness of the incoming strip 15 including discontinuities such as welds, whereas the slow response of conventional screw-down devices prevents correction of many of these variations even if the thickness of the incoming strip is measured in advance, resulting in a considerable proportion of off-gauge material in the rolled strip.
  • the frequency response of this adjusting device is very high, approximately one cycle per second, thereby permitting variations in the working roll separation rapid O enough to correct for eccentricities in the working roll which, otherwise would produce a wavy pattern in the rolled material.
  • adjusting device utilizes the Teflon surfaced wedge shown in FIG. 3 because it provides the most rapid response for a given set of hydraulic ram requirements
  • other forms of rapid response adjusting devices may also be used with the control system of the invention if a hydraulic actuator of increased capacity is provided.
  • FIGS. 4 and 5 In the embodiments shown in FIGS. 4 and 5,
  • a wedge system comprising a series of rolling members movable on adjacent inclined planes.
  • a plurality of hardened rollers 51 is held captive in a corresponding plurality of races 52 formed in two adjacent relatively rotatable cage members 53 and 54, the bearing surfaces 55 and 56 of the races being inclined with respect to the plane of relative motion of the members.
  • the upper cage member 53 is rotatably connected to the frame a of the stand, preferably through a bearing 57, and is linked to the linear hydraulic actuator 44 through a peripheral pivotable attachment 58, while the lower case member 54 is affixed to a support block 60 for the upper backup roll 13.
  • this wedge arrangement may be enclosed in a housing 61 which is filled with a liquid lubricant to further reduce the frictional resistance of the system.
  • FIG. 6 A different form of adjusting device which does not include any wedge arrangement is shown in FIG. 6 wherein a piston 61, aflixed to the stand frame 10a, is slidably received in a cylinder 62 mounted on the support member 60 for the upper back-up roll. Hydraulic fluid from the control valve 47 is supplied to or withdrawn from a chamber 64 located between the piston and cylinder through a conduit 63, in response to signals on the line 18 calling for a change in the working roll separation. If desired, a separate bleed line may be provided in the cylinder 62. to withdraw hydraulic fluid from the chamber 64.
  • control system of the present invention responds with greater rapidity to correct thickness variations than has same time producing at high speed a strip having a closely regulated thickness.
  • control system it is possible by utilizing the present control system to maintain the thickness of'a rolled strip within the range of accuracy of presently available measuring devices.
  • Control apparatus for a rolling mill wherein a piece of material is passed between a pair of working rolls supported in a frame to reduce its thickness to a desired value
  • fluid-actuated rapid response adjusting means interposed between the frame and one of. the working rolls to vary the separation of the'rolls in response to a control signal, and means operatively positioned in advance of the pair of Working rolls for determining the force necessary to accomplish a desired reduction in'the thickness of the piece and transmitting to the adjusting means a control signal to actuate the adjusting means to produce the necessary force at the time the piece passes between the working rolls.
  • Control apparatus including force gauge means interposed between the frame and the working rolls for detecting the force applied to the working rolls, comparing means responsive to the force gauge means and the means for determining the necessary force for comparing the detected force with the necessary force and modifying the control signal in accordance with any difference between them.
  • Control apparatus comprising thickness gauge means fordetecting the thickness of the piece of material as it enters the stand, tension gauge means fordetecting the tension in the piece of material, and computer means responsive to the thick ness and tension gauges to solve a function of thenecessary force in terms of the thickness and tension of the piece.
  • Control apparatus wherein the means for determining the force necessary to accomplish a desired reduction in thickness includes tachometer means for measuring the velocity of the piece through the stand, and delay means responsive to the thickness gauge means and the teachometer means for delaying the transmission of thickness information to the computer means so that the resulting actuation of the adjusting means takes place at the time the detected thickness of the piece of material passes between the working rolls.
  • Control apparatus including output thickness-gauge means for measuring the actual thickness of the piece of material after rolling and reset means for comparing the actual thickness with a desired thickness and transmitting an errorsignal to the computer means.
  • Control appaartus according to claim 5 including filter means in the reset means to smooth out rapid variations in the error signal so that the corrections made by the computer as a result of the error signal are relatively long term corrections.
  • Control apparatus according to claim 3 wherein the computer means includes means for solving simultaneously two different functions of the necessary force in terms of the thickness of the piece of material.
  • control apparatus comprises wedge means interposed between the frame and the working roll and hydraulic drive means for driving'the wedge means to vary the distance between the frame and the roll in response to a control signal.
  • control apparatus comprises a wedge-shaped member and including means forming surfaces cooperating with the surf-aces of the wedge means and a permanent layer of antifriction material. aifixed to at least one of the cooperating surfaces.
  • control apparatus according to claim 9 wherein the antifriction material comprises Teflon fabric.
  • control apparatus comprising a pair of relatively rotatable adjacent members formed with a plurality of races having inclined surfaces, and rolling means positioned within each of the races.
  • Control apparatus comprising hydraulic piston and cylinder means interposed between the frame and one of the working rolls and control valve means connected to a source of hydraulic fluid under pressure and responsive to the control signal to supply hydraulic fluid under pressure to the piston and, cylinder means.
  • control apparatus for a rolling mill wherein a piece of material is passed between a pair of working rolls supported in a frame to reduce its thickness to a desired value-in accordance with a force applied between the frame and the working rolls, rapid response adjusting means for varying the force comprising wedge means interposed between the frame and one of the rolls, fluid actuated linear drive means for driving the wedge means, and control valve means for controlling the application of fluid to the linear drive means in response to a control signal representing a desired force.
  • the Wedge means comprises a Wedge-shaped member having relatively inclined surfaces interposed between the frame and one of the working rolls, means forming corresponding surfaces for cooperation with the Wedge means for varying the force applied to the rolls in response to motion of the wedge-shaped member, and a permanent layer of antifriction material affixed to at least one of the surfaces.
  • Control apparatus wherein the antifriction material is a fabric made of Teflon fibers.
  • the wedge means comprises a pair of relatively rotatable adjacent members formed with a plurality of races having inclined surfaces, and rolling means positioned within each of the races.
  • Control apparatus for a rolling stand wherein a piece of material is passed between a pair of working rolls supported in a frame to reduce its thickness to a desired value
  • a Wedge-shaped member having relatively inclined surfaces supported for sliding motion between the stand frame and one of the working rolls, means forming corresponding surfaces for cooperation with the wedge means to vary the separation of the rolls in response to motion of the wedge-shaped member, a permanent coating of antifri-ct'ion material on at least one of the surfaces, hydraulic ram means connected to a Wedge-shaped member to drive it in response to a control signal, gauge means in the stand for detecting the force 16.
  • Control apparatus wherein applied to the working rolls, comparing means for comparing the detected force with a desired force and modifying the control signal in accordance with any difference between them, thickness gauge means for measuring the thickness of the piece before rolling, computer means responsive to the thickness gauge means for determining the force required to produce a desired reduction in the thickness of the piece to the stand and providing a control signal to the comparing means, a control valve means for the hydraulic ram means responsive to a control signal from the comparing means for controlling the ram means to drive the wedge-shaped member in the direction to reduce the difference between the detected force and the desired force, output thickness gauge means for measuring the thickness of the piece after rolling, and reset means for comparing the rolled thickness with the desired thickness and transmitting an error signal to the computer means.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Control Of Metal Rolling (AREA)
US150738A 1961-11-07 1961-11-07 Control system for rolling mills Expired - Lifetime US3197986A (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
BE624523D BE624523A (nl) 1961-11-07
US150738A US3197986A (en) 1961-11-07 1961-11-07 Control system for rolling mills
FR914600A FR1345182A (fr) 1961-11-07 1962-11-07 Système de commande pour le laminage de matériaux tels que tôles métalliques, bandes ou tubes
GB42113/62A GB968778A (en) 1961-11-07 1962-11-07 Improvements relating to rolling mill stands

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US150738A US3197986A (en) 1961-11-07 1961-11-07 Control system for rolling mills

Publications (1)

Publication Number Publication Date
US3197986A true US3197986A (en) 1965-08-03

Family

ID=22535797

Family Applications (1)

Application Number Title Priority Date Filing Date
US150738A Expired - Lifetime US3197986A (en) 1961-11-07 1961-11-07 Control system for rolling mills

Country Status (3)

Country Link
US (1) US3197986A (nl)
BE (1) BE624523A (nl)
GB (1) GB968778A (nl)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3342047A (en) * 1963-09-17 1967-09-19 British Iron Steel Research Rolling mills
US3391557A (en) * 1964-11-12 1968-07-09 Fox Ind Inc Gauge control rolling mills and methods of rolling
US3470722A (en) * 1965-12-11 1969-10-07 Gkn Machinery Ltd Rolling of rod stock
US3479854A (en) * 1966-05-16 1969-11-25 Davy & United Eng Co Ltd Rolling mills
US3517531A (en) * 1967-11-03 1970-06-30 Gulf & Western Ind Prod Co Rolling mill gage control actuator system
US3596490A (en) * 1967-09-13 1971-08-03 Schloemann Ag Roll stand, with means for the fine adjustment of the rolls under rolling pressure
US3624369A (en) * 1969-08-04 1971-11-30 Ruloff F Kip Jr Thickness reduction control systems
US3744287A (en) * 1971-09-14 1973-07-10 Westinghouse Electric Corp Hydraulic interstand tension regulating and automatic gauge control system for multi-stand rolling mills
US4450728A (en) * 1981-10-06 1984-05-29 Horiba Instruments Incorporated Vehicle force measurement system
US5351516A (en) * 1991-08-14 1994-10-04 Otis Elevator Company Rail repair device
EP0815963A1 (en) * 1996-06-24 1998-01-07 DANIELI & C. OFFICINE MECCANICHE S.p.A. Device for the crossed displacement of rolling rolls
CN105414202A (zh) * 2015-12-30 2016-03-23 邢台海裕锂能电池设备有限公司 在线调隙轧机、在线调隙轧制系统

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113441558B (zh) * 2021-06-29 2022-07-12 杭州电子科技大学 基于前滑法的轧机轧制界面摩擦系数测量装置

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE508186A (nl) * 1952-01-30
US1092084A (en) * 1912-04-29 1914-03-31 Heinrich Stueting Feed mechanism for tube-rolling mills.
US2040755A (en) * 1934-05-08 1936-05-12 Meyer Eduard Regulating means for rolling mechanisms
US2525687A (en) * 1946-04-10 1950-10-10 Nat Tube Co Separation device for rolling mills
US2575590A (en) * 1949-08-31 1951-11-20 Wingfoot Corp Calender roll pressure control apparatus
US2998397A (en) * 1955-05-18 1961-08-29 Gen Motors Corp Bearing element comprising thermoplastic resin and sintered teflon particles
US3015974A (en) * 1958-09-18 1962-01-09 Gen Electric Automatic control system for rolling mills and adjustable dies

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1092084A (en) * 1912-04-29 1914-03-31 Heinrich Stueting Feed mechanism for tube-rolling mills.
US2040755A (en) * 1934-05-08 1936-05-12 Meyer Eduard Regulating means for rolling mechanisms
US2525687A (en) * 1946-04-10 1950-10-10 Nat Tube Co Separation device for rolling mills
US2575590A (en) * 1949-08-31 1951-11-20 Wingfoot Corp Calender roll pressure control apparatus
BE508186A (nl) * 1952-01-30
US2998397A (en) * 1955-05-18 1961-08-29 Gen Motors Corp Bearing element comprising thermoplastic resin and sintered teflon particles
US3015974A (en) * 1958-09-18 1962-01-09 Gen Electric Automatic control system for rolling mills and adjustable dies

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3342047A (en) * 1963-09-17 1967-09-19 British Iron Steel Research Rolling mills
US3391557A (en) * 1964-11-12 1968-07-09 Fox Ind Inc Gauge control rolling mills and methods of rolling
US3470722A (en) * 1965-12-11 1969-10-07 Gkn Machinery Ltd Rolling of rod stock
US3479854A (en) * 1966-05-16 1969-11-25 Davy & United Eng Co Ltd Rolling mills
US3596490A (en) * 1967-09-13 1971-08-03 Schloemann Ag Roll stand, with means for the fine adjustment of the rolls under rolling pressure
US3517531A (en) * 1967-11-03 1970-06-30 Gulf & Western Ind Prod Co Rolling mill gage control actuator system
US3624369A (en) * 1969-08-04 1971-11-30 Ruloff F Kip Jr Thickness reduction control systems
US3744287A (en) * 1971-09-14 1973-07-10 Westinghouse Electric Corp Hydraulic interstand tension regulating and automatic gauge control system for multi-stand rolling mills
US4450728A (en) * 1981-10-06 1984-05-29 Horiba Instruments Incorporated Vehicle force measurement system
US5351516A (en) * 1991-08-14 1994-10-04 Otis Elevator Company Rail repair device
EP0815963A1 (en) * 1996-06-24 1998-01-07 DANIELI & C. OFFICINE MECCANICHE S.p.A. Device for the crossed displacement of rolling rolls
US5870916A (en) * 1996-06-24 1999-02-16 Danieli & C. Officine Meccaniche Spa Device for the crossed displacement of rolling rolls
CN105414202A (zh) * 2015-12-30 2016-03-23 邢台海裕锂能电池设备有限公司 在线调隙轧机、在线调隙轧制系统

Also Published As

Publication number Publication date
GB968778A (en) 1964-09-02
BE624523A (nl)

Similar Documents

Publication Publication Date Title
US3197986A (en) Control system for rolling mills
US4222255A (en) Rolling device having at least one controlled deflection roll
US3327508A (en) Rolling mills
GB982232A (en) Improvements in or relating to automatic strip gauge control for a rolling mill
US2659154A (en) Apparatus for measuring strip thickness
US3416341A (en) Rolling mill control system
US5086399A (en) Method and apparatus for setting-up rolling mill roll gaps
US3475935A (en) Control apparatus and system for strip rolling
KR830007156A (ko) 금속의 압연 방법
US3650135A (en) Control for rolling means having successine rolling stands
US3517531A (en) Rolling mill gage control actuator system
Hessenberg et al. Principles of continuous gauge control in sheet and strip rolling
GB1307823A (en) Rolling of strip or plate material
US3312092A (en) Control arrangement for level rolling metal plates and sheets in reversible rolling mills
US3620058A (en) Hot or cold rolling of strip or plate
US3436943A (en) Rolling mill taper control system
US3534571A (en) Rolling mill control
US3550413A (en) Gage control for rolling mills
US3124020A (en) Methods of and apparatus for controlling rolling mills
GB1270788A (en) Improvements in or relating to cold rolling stands
US3875775A (en) Device for automatic adjustment of strip thickness in rolling
US3024680A (en) Process measurement and control
US2332272A (en) Sheet thickness gauge for continuous rolling mills
GB1243806A (en) Apparatus for controlling a rolling mill
US3398559A (en) Control of prestressed rolling mills