US3691810A - Individual eccentric control for mill screwdown - Google Patents

Individual eccentric control for mill screwdown Download PDF

Info

Publication number
US3691810A
US3691810A US3691810DA US3691810A US 3691810 A US3691810 A US 3691810A US 3691810D A US3691810D A US 3691810DA US 3691810 A US3691810 A US 3691810A
Authority
US
United States
Prior art keywords
eccentrics
casters
strip
screwdown
lever means
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
Other languages
English (en)
Inventor
Tadeusz Sendzimir
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.)
T Sendzimir Inc
Original Assignee
T Sendzimir Inc
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
Application filed by T Sendzimir Inc filed Critical T Sendzimir Inc
Application granted granted Critical
Publication of US3691810A publication Critical patent/US3691810A/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
    • B21B31/26—Adjusting eccentrically-mounted roll bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/147—Cluster mills, e.g. Sendzimir mills, Rohn mills, i.e. each work roll being supported by two rolls only arranged symmetrically with respect to the plane passing through the working rolls
    • 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
    • Y10T83/00—Cutting
    • Y10T83/465—Cutting motion of tool has component in direction of moving work
    • Y10T83/4766—Orbital motion of cutting blade
    • Y10T83/4795—Rotary tool
    • Y10T83/483—With cooperating rotary cutter or backup
    • Y10T83/4833—Cooperating tool axes adjustable relative to each other

Definitions

  • ABSTRACT In a beam-backed rolling mill wherein the working rolls are backed by casters mounted on eccentric shafts for screwdown purposes, there is disclosed an arrangement wherein a plurality of eccentrics are mounted at spaced intervals on a shaft, each of said eccentrics being individually operable by outside means, whereby the eccentrics may be made large enough so as not to be self-locking, and whereby the pressure exerted by each eccentric, through the adjacent caster, upon the work roll, may be controlled and the roll profile adjusted to a desired configuration.
  • each of the eccentrics is provided with an eccentric bushing, and the angular position of each of the bushings is controlled individually.
  • these spaced eccentrics are very smalljust enough to cover the screwdown range, and therefore screwdown actuating means must be provided at each end of the eccentric shafts to minimize torsional deflection. Since, however, small eccentrics are essentially self-locking, they cannot be used to control the roll pressure exerted on each eccentric, even through they control precisely the position of the roll.
  • the present invention provides means for precisely controlling the pressure exerted by each eccentric (through the adjacent casters) upon the roll; and these means control the roll pressure at spaced intervals across the entire width of the work piece.
  • each eccentric is connected to outside means for exerting torque upon it and/or for rotating it. In this way torsional deflection of the shaft is avoided and therefore the eccentrics may have much greater eccentricity.
  • the eccentrics are far removed from the self-locking range.
  • angular adjustment of these eccentrics results in a roll displacement (screwdown range) which is many times larger than is obtainable in mills heretofore known, so that the mill of the present invention is useful in certain fields which are out of reach of the small eccentric mills, as will be discussed in more detail hereinafter.
  • FIG. 1 is a fragmentary top plan view with parts in cross sections of one embodiment of the invention.
  • FIG. 2 is a vertical cross sectional view taken on the line 2-2 of FIG. 1.
  • FIG. 3 is a composite view similar to FIG. 1 showing a second embodiment in the left half and a third embodiment in the right half.
  • FIG. 4 is a vertical cross sectional view of FIG. 3 also showing the second and third embodiment.
  • FIG. 5 is a schematic elevational view of an application of the invention.
  • FIG. 6 is an enlargement of a central portion of FIG. 5 showing a modification.
  • the mill is provided with saddles I supported by the rigid beam 2 of the mill housing and spaced evenly across the width of the work piece.
  • Each saddle 1 has two openings to accommodate the eccentrics 3, 3' with their bearings such as the needie bearings 4, 4'.
  • the eccentrics 3, 3' in turn carry shafts 5, 5' which support casters 6, 6' which are mounted upon the shafts in the spaces between adjacent eccentrics 3, 3'.
  • the casters 6, 6' jointly support one component of roll pressure exerted by the working roll 7 along their common generant.
  • FIGS. 1 and 2 Further description of the invention of FIGS. 1 and 2 will be with respect to the elements 3', 4', 5 and 6', and it will be understood that the parts to be described hereinafter will be duplicated for the elements 3, 4, 5, and 6.
  • a shaft 11' carries pinions l0 keyed thereon and the pinions 10' are in mesh with the respective gear segments 8'.
  • the shaft 11' is located in a saddle or an extension 1" thereof by bearings 12' and the shaft 11' is coupled to actuating means such as the hydraulic actuator 13'.
  • each pinion 10' is adjustable. This may be accomplished by means of nuts 14' engaging threaded hubs of the pinions 10'. The outer peripheries of the nuts 14 are provided with worm gear teeth which engage worms 15' which can be rotated by means of gear motors I6 and the like.
  • the gear motors 16' may be controlled by signals from strip flatness verifying instruments of the automatically produced flat sheets, as will be described hereinafter.
  • a suitable relief valve (not shown) is preferably provided in the hydraulic system of the actuator so that in cast of a surge of roll pressure, as for example during a cobble, the actuators may actually turn in reverse, thereby preventing damage to mill components.
  • the actuator shaft ll of the present invention fulfills the same role, it is not subject to any limitation as to its diameter. it can be made so heavy, that even though the torque means (hydraulic actuator) is applied to one end only, the torsional deflection will be negligible.
  • crown control elements which are slender eccentric rings surrounding the screwdown eccentrics and having needle bearings inside and out to reduce friction. These elements are moreover subjected to the same roll pressure as the screwdown eccentrics and must, therefore, be made of heat-treated and ground alloy steel. This, of course, increases their cost.
  • crown control according to the present invention does not require separate elements since the screwdown elements serve both purposes. These parts are sturdy and can be made of ordinary machine steel and they are not subjected to roll pressure.
  • FIGS. 3 and 4 the left and right-hand portions of these Figures differ from each other only in the mode of attachment of actuating means to the eccentrics 3 and 3'.
  • the saddle 1 and eccentric 3 may be broadened and the segment 8 may be affixed to the eccentric 3 in a shallow slot 17 therein and the parts may be connected by dowels, screws, or the like as at 18.
  • the tooth segment 8 protrudes from the saddle 1 through a slot 20 provided therein and it protrudes to a position in which it meshes with a pinion as described above. This construction makes it possible to apply the tooth pressure in the plane of symmetry of the eccentric 3.
  • fluid may be admitted to or let out from all the cylinders 23 connected to the eccentrics 3' of a shaft 5 simultaneously.
  • a three-way valve 25 is provided for each cylinder 23 and this valve has connections to a pump or supply of fluid under pressure S to a sump W and to an individual pressure control device, such as the small accumulator 26 which is connected by a suitable valve 25' to both the supply S and the sump W.
  • the several valves 25 for the several cylinders 23 may be arranged in a single line and connected by a shaft 35 so that they may all be operated concurrently. In the third position mentioned above, pressure from each cylinder is controlled individually and independently of the other cylinders.
  • a typical application of such a skin-pass mill is in strip processing, for example in a continuous bright-annealing line.
  • a schematic view of such a mill is shown in FIG. 5 and it will be observed that the annealed and cooled strip 27 is passed in succession by two tensioning devices with the skin-pass, mill therebetween. While the strip 27 is passed through the line at a certain tension, the tension is considerably augmented for skinpassing and usually amounts to one-third of the elastic limit of the strip.
  • each tensioning device consists of a pulley 28, 28' around which the strip passes and two deflecting pulleys 29, 29', and in some cases pressure roll chains 30, 30 around each tension pulley, so that with high enough initial tension, the wrapping angle around the tension pulley and its coefficient of friction, a nonslip contact is assured.
  • the tension pulleys 28, 28' are preferably geared together and operated from a common drive, so that with the strip moving from left to right, the pull y 28 is driving and the pulley 28 is driven, while the difference in surface velocities of the two pulleys must be equal to the required percentual elongation of the strip 27.
  • Known compensation drives such as described in US. Pat. No. 2,l94,2 l 2 are usually used for adjustment of the percentage of elongation without jeopardizing the accuracy thereof.
  • roll pressure is a pressure where the tension of the strip 27 is of the desired magnitude (one-third of the elastic limit preferably). If the tension falls, this can be corrected by lowering roll pressure. If not corrected, it is difficult to produce a flat strip. Similarly, if the tension is too high, the strip 27 may stretch irregularly at places outside of the roll bite, producing so-called stretcher-strains" and making the strip unsuitable for many purposes.
  • tension indicating meters are provided at points across the strip corresponding to the positions of the eccentrics 3. These meters may be proximity gauges 31 mounted on a rigid beam 32 parallel with the width of the strip. The strip is then subjected to a light but uniform pressure, such as static air pressure. This pressure may be produced in a trough 33 extending all the way across the strip and closely spaced to the strip to restrict escape of air and air under pressure is supplied through the line 34 from a blower or the like.
  • the indications of the gauges 31 may be transmitted in the form of suitable signals to the pressure control device of each cylinder 23 to restore uniform tension across the strip 27. This insures that the flatness is correct and at the same time controls the total pressure to assure correct rolling conditions, including correct tension.
  • Another quite different benefit of the present invention when applied to skin-passing and processing lines, is the possibility of providing two pairs of work rolls rather than one. Only one of the pairs is in working contact with the strip, while the other is retracted and kept far enough from the strip to prevent contact, even on wavy spots in the strip.
  • the middle shaft 5" may also be actuated for the purpose.
  • the middle shaft 5" may have its eccentrics keyed onto it and a rotary actuator is coupled onto one of its ends to rotate it to one of two positions: to the left as shown in FIG. 6 to engage the roll 7 while disengaging the roll 7'; or to the right to disengage the roll 7 and engage the roll 7'.
  • the axis of the work roll 7, the casters and eccentrics all lie in the same plane.
  • These keyed eccentrics may be relatively large to obtain a large displacement of the rolls since in either of the two operating positions the roll pressure passes directly through the center of the eccentrics, so that the eccentrics and the shaft 5 are not subjected to any torque.
  • an actuator shaft is mounted parallel to said caster shaft beyond the periphery of said casters, and carries a plurality of pinions keyed thereon, said pinions being in mesh, respectively, with the teeth on said levers, whereby a change in the angular position of said actuator shaft results in simultaneous actuation of all the eccentrics to produce parallel movement of said casters.
  • linear actuators are fluid cylinders with actuating pistons.
  • a fluid circuit is provided for all said cylinders, said circuit including a source of fluid pressure, a sump and an individual pressure control for each cylinder, and a valve is provided for each cylinder, all said valves being connected together for simultaneous operation to (a) admit fluid from said source, (b) discharge fluid to sump, or (c) to close both said connections and open a connection to said individual pressure controls.
  • the structure of claim 1 in combination with means to deflect a tenioned exiting strip in a direction normal to its plane, and proximity measuring gauges disposed opposite each of said eccentrics to measure the deflection of the strip at that point, the signals from eccentric control means to said proximity gauges serving to actuate the individual IINITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3, 91,810 Dated September 19, 1972 Inventor) Tadeusz Sendzimir It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:
  • said caster shafts should read caster shafts carrying eccentrics, said eccentrics Signed and sealed this 19th day of March 19%..

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Control Of Metal Rolling (AREA)
  • Paper (AREA)
US3691810D 1971-05-25 1971-05-25 Individual eccentric control for mill screwdown Expired - Lifetime US3691810A (en)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
US14666171A 1971-05-25 1971-05-25
GB3054972A GB1379108A (en) 1971-05-25 1972-06-29 Improvements in or relating to rolling mills
FR7225012A FR2190535B1 (enrdf_load_html_response) 1971-05-25 1972-07-06
DE2238064A DE2238064A1 (de) 1971-05-25 1972-08-02 Durch exzenter betaetigte anstellvorrichtung fuer ein durch balken abgestuetztes walzwerk

Publications (1)

Publication Number Publication Date
US3691810A true US3691810A (en) 1972-09-19

Family

ID=34382054

Family Applications (1)

Application Number Title Priority Date Filing Date
US3691810D Expired - Lifetime US3691810A (en) 1971-05-25 1971-05-25 Individual eccentric control for mill screwdown

Country Status (4)

Country Link
US (1) US3691810A (enrdf_load_html_response)
DE (1) DE2238064A1 (enrdf_load_html_response)
FR (1) FR2190535B1 (enrdf_load_html_response)
GB (1) GB1379108A (enrdf_load_html_response)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4116261A (en) * 1975-12-17 1978-09-26 Vereinigte Osterreichische Eisen- Und Stahlwerke - Alpine Montan Aktiengesellschaft Continuous casting plant strand guiding means
US4130042A (en) * 1977-07-25 1978-12-19 Avery International Corporation Adjustable anvil roll for die-cutting labels
US4156359A (en) * 1977-10-19 1979-05-29 T. Sendzimir, Inc. Method of operation of crown adjustment system drives on cluster mills
US4289013A (en) * 1979-08-29 1981-09-15 Textron, Inc. Crown control for rolling mill
US4922778A (en) * 1987-10-16 1990-05-08 Sky Aluminum Co., Ltd. Apparatus for cutting metal sheet
US5048387A (en) * 1989-07-14 1991-09-17 Komori Corporation Horizontal perforation forming apparatus for rotary press
US5083488A (en) * 1991-04-12 1992-01-28 Melvin Stanley Radially adjustable anvil roll assembly for a rotary die cutting press
US5365814A (en) * 1992-06-24 1994-11-22 Japan Tobacco Inc. Shredding device for paper web used in the manufacture of cigarettes with filters
EP0712674A1 (en) * 1994-11-11 1996-05-22 GASPARINI S.p.A. Roll forming machine
US5855133A (en) * 1995-01-19 1999-01-05 Hayes Corporation Rollforming apparatus for forming profile shapes
US6032560A (en) * 1997-10-24 2000-03-07 Morgan Construction Company High speed trimming shear
EP0899068A3 (de) * 1997-08-23 2002-05-02 Kocher + Beck GmbH + Co. Rotationsstanztechnik KG Vorrichtung zum Stanzen von Etiketten o.dgl.
US6604397B2 (en) 2001-02-05 2003-08-12 Dietrich Industries, Inc. Rollforming machine
US6826941B2 (en) 2000-12-29 2004-12-07 Ronald L. Plesh, Sr. Roller apparatus with improved height adjustability
WO2005092530A1 (en) * 2004-03-29 2005-10-06 Pittini Impianti S.R.L. Cold rolling-mill for wire and rods with improved adjustment of the distance between centers of the rolls
US20070199358A1 (en) * 2006-02-24 2007-08-30 Kocks Technik Gmbh & Co., Kg Rolling stand, and method for determining the rolling force in a rolling stand
CN101439353B (zh) * 2008-12-30 2012-06-06 浙江精工科技股份有限公司 钢板成型机用轴间距调整机构
US20130025426A1 (en) * 2011-07-25 2013-01-31 Gallus Druckmaschinen Ag Die cutting device with adjustable cylinder distance
US20140238098A1 (en) * 2011-10-07 2014-08-28 Danieli & C. Officine Meccaniche Spa Rolling unit
CN113083907A (zh) * 2021-03-29 2021-07-09 广西北港不锈钢有限公司 一种不锈钢板材偏心轧制线计算方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU806176A1 (ru) * 1977-10-19 1981-02-23 Московский Ордена Трудового Красногознамени Институт Стали И Сплавов Рабоча клеть стана холоднойпРОКАТКи ТРуб
US5743126A (en) * 1995-07-06 1998-04-28 Morgan Construction Company Roll stand with separable roll parting adjustment module

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB831505A (en) * 1955-11-22 1960-03-30 Sandvikens Jernverks Aktiebolo Backed rolling mill
JPS4818868B1 (enrdf_load_html_response) * 1969-06-21 1973-06-08

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4116261A (en) * 1975-12-17 1978-09-26 Vereinigte Osterreichische Eisen- Und Stahlwerke - Alpine Montan Aktiengesellschaft Continuous casting plant strand guiding means
US4130042A (en) * 1977-07-25 1978-12-19 Avery International Corporation Adjustable anvil roll for die-cutting labels
US4156359A (en) * 1977-10-19 1979-05-29 T. Sendzimir, Inc. Method of operation of crown adjustment system drives on cluster mills
US4289013A (en) * 1979-08-29 1981-09-15 Textron, Inc. Crown control for rolling mill
US4922778A (en) * 1987-10-16 1990-05-08 Sky Aluminum Co., Ltd. Apparatus for cutting metal sheet
US5048387A (en) * 1989-07-14 1991-09-17 Komori Corporation Horizontal perforation forming apparatus for rotary press
US5083488A (en) * 1991-04-12 1992-01-28 Melvin Stanley Radially adjustable anvil roll assembly for a rotary die cutting press
US5365814A (en) * 1992-06-24 1994-11-22 Japan Tobacco Inc. Shredding device for paper web used in the manufacture of cigarettes with filters
EP0712674A1 (en) * 1994-11-11 1996-05-22 GASPARINI S.p.A. Roll forming machine
USRE42417E1 (en) 1995-01-19 2011-06-07 Hayes International Rollforming apparatus for forming profile shapes
US5855133A (en) * 1995-01-19 1999-01-05 Hayes Corporation Rollforming apparatus for forming profile shapes
EP0899068A3 (de) * 1997-08-23 2002-05-02 Kocher + Beck GmbH + Co. Rotationsstanztechnik KG Vorrichtung zum Stanzen von Etiketten o.dgl.
US6032560A (en) * 1997-10-24 2000-03-07 Morgan Construction Company High speed trimming shear
US6826941B2 (en) 2000-12-29 2004-12-07 Ronald L. Plesh, Sr. Roller apparatus with improved height adjustability
US6604397B2 (en) 2001-02-05 2003-08-12 Dietrich Industries, Inc. Rollforming machine
WO2005092530A1 (en) * 2004-03-29 2005-10-06 Pittini Impianti S.R.L. Cold rolling-mill for wire and rods with improved adjustment of the distance between centers of the rolls
US7497104B2 (en) * 2006-02-24 2009-03-03 Kocks Technik Gmbh & Co. Kg Rolling stand, and method for determining the rolling force in a rolling stand
CN101024231B (zh) * 2006-02-24 2011-01-05 科克斯技术有限及两合公司 用于确定轧机机座中轧制力的方法和轧机机座
US20070199358A1 (en) * 2006-02-24 2007-08-30 Kocks Technik Gmbh & Co., Kg Rolling stand, and method for determining the rolling force in a rolling stand
CN101439353B (zh) * 2008-12-30 2012-06-06 浙江精工科技股份有限公司 钢板成型机用轴间距调整机构
US20130025426A1 (en) * 2011-07-25 2013-01-31 Gallus Druckmaschinen Ag Die cutting device with adjustable cylinder distance
US8943939B2 (en) * 2011-07-25 2015-02-03 Gallus Druckmaschinen Ag Die cutting device with adjustable cylinder distance
US20140238098A1 (en) * 2011-10-07 2014-08-28 Danieli & C. Officine Meccaniche Spa Rolling unit
US10016797B2 (en) * 2011-10-07 2018-07-10 Danieli & C. Officine Meccaniche Spa Rolling unit
CN113083907A (zh) * 2021-03-29 2021-07-09 广西北港不锈钢有限公司 一种不锈钢板材偏心轧制线计算方法

Also Published As

Publication number Publication date
FR2190535A1 (enrdf_load_html_response) 1974-02-01
FR2190535B1 (enrdf_load_html_response) 1977-08-26
GB1379108A (en) 1975-01-02
DE2238064A1 (de) 1974-02-21

Similar Documents

Publication Publication Date Title
US3691810A (en) Individual eccentric control for mill screwdown
JP2967010B2 (ja) 圧延機及び圧延方法並びに圧延設備
US8127584B2 (en) Prestressed rolling mill housing assembly with improved operational features
EP0743107A1 (en) Improvements in or relating to a roll crossing and shifting system
US4691548A (en) Rolling mill stand for strip-shaped material
US3427848A (en) Devices for cold-rolling and planishing metal sheet
US4289013A (en) Crown control for rolling mill
US3138979A (en) Construction and control of planetary mills
KR100254474B1 (ko) 클러스터타입의 판재압연기의 형상제어
US3657913A (en) Crown control
US3595054A (en) Double three high planetary mill
US2573353A (en) Rolling mill
JPH07284821A (ja) 多数本のロールの支持構造物
US4603569A (en) Pressure controlled plate mill
US4676085A (en) Rolling mill for controlling the contour of a workpiece
JPS6232001B2 (enrdf_load_html_response)
JPS6057401B2 (ja) 多段圧延機構を有する圧延機
US3318131A (en) Multiple-roll rolling mill for exchangeable work rolls of substantially varying diameter
US3148565A (en) Rolling mill
SU1547900A1 (ru) Устройство дл регулировани планшетности и разнотолщинности прокатываемых полос
JPS62151203A (ja) 板材の圧延方法
JPS608883B2 (ja) 形状制御機能を有する多段圧延機
JPS642443B2 (enrdf_load_html_response)
JP3025370B2 (ja) 圧延機
JPS6235842B2 (enrdf_load_html_response)