EP2736660B1 - Roll-holder cartridge for a rolling mill - Google Patents

Roll-holder cartridge for a rolling mill Download PDF

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Publication number
EP2736660B1
EP2736660B1 EP12759203.8A EP12759203A EP2736660B1 EP 2736660 B1 EP2736660 B1 EP 2736660B1 EP 12759203 A EP12759203 A EP 12759203A EP 2736660 B1 EP2736660 B1 EP 2736660B1
Authority
EP
European Patent Office
Prior art keywords
cartridge
roll
pin
rolling
adjusting
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.)
Active
Application number
EP12759203.8A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2736660A2 (en
Inventor
Paolo Marin
Marcello Pacher
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.)
SMS Group SpA
Original Assignee
SMS Innse SpA
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 SMS Innse SpA filed Critical SMS Innse SpA
Publication of EP2736660A2 publication Critical patent/EP2736660A2/en
Application granted granted Critical
Publication of EP2736660B1 publication Critical patent/EP2736660B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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
    • 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
    • B21B13/08—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with differently-directed roll axes, e.g. for the so-called "universal" rolling process
    • B21B13/10—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with differently-directed roll axes, e.g. for the so-called "universal" rolling process all axes being arranged in one plane
    • B21B13/103—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with differently-directed roll axes, e.g. for the so-called "universal" rolling process all axes being arranged in one plane for rolling bars, rods or wire
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B17/00—Tube-rolling by rollers of which the axes are arranged essentially perpendicular to the axis of the work, e.g. "axial" tube-rolling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B28/00—Maintaining rolls or rolling equipment in effective condition
    • B21B28/02—Maintaining rolls in effective condition, e.g. reconditioning

Definitions

  • the present invention relates to a roll-holder cartridge for a continuous rolling mill, in particular for a continuous rolling mill suitable for the production of long semi-finished articles.
  • the invention also relates to a stand and a rolling mill comprising such a cartridge.
  • specific reference will be made, by way of a non-limiting example, to the rolling of seamless tubes, but it is understood that the same inventive ideas may be applied to the rolling of other long articles such as bars, rods, round bars and the like.
  • the three pairs of arms are coplanar with each other, have a radial direction and are arranged at a distance of 120° from each other around the rolling axis.
  • the set of connected profiles of the grooves of the three rolls defines the external circumference of the tube leaving the rolling station.
  • the roll-support levers are mounted on a cartridge so as to be able to pivot about an axis parallel to the rolling axis.
  • An actuator for example of the hydraulic type, acts on each of the rolls and pushes the roll in the radial direction relative to the rolling axis. The actuators thus produce the force required to deform plastically the tube.
  • the rolls are rotated by proper motors so as to provide, by means of friction, the feeding movement to the tube being processed.
  • the subsequent stations together with, if required, an internal mandrel, gradually convert the semi-finished article into a tube with the desired configuration in terms of outer diameter, inner diameter, wall thickness and length.
  • the rolling rolls are subject to wear and, following given working cycles, must be reconditioned by means of turning. In this way it is possible to eliminate the deformation and wear marks and restore the groove profile of the roll. It is in fact necessary to ensure an optimum profile of the groove of each roll so that the individual station may provide the tube being processed with an optimum profile.
  • Turning may be performed, in a manner known per se, by disassembling each roll from the respective position and transporting it to a suitable conventional turning station.
  • a suitable conventional turning station in a manner equally well known per se, it is possible, for each stand, to remove the entire cartridge, while keeping the three rolls mounted therein, and perform the turning operation with a special tool arranged in the centre of the cartridge in place of the tube.
  • Each turning operation necessarily reduces the diameter of the individual roll. For this reason, it is known to provide on each stand means for keeping the rolls parallel to each other before and after each turning operation.
  • the roll could be brought into contact with the tube by means of simple pivoting of the lever about its axis.
  • This configuration of the roll would be asymmetrical with respect to the radial direction and the contact would not be optimal.
  • the set of profiles of the grooves of the three rolls would no longer define a circumference; instead they would define a three-lobed figure composed of circle arcs which are not connected together.
  • the first solution consists in compensating for the reduction in diameter of the roll by means of an identical lengthening of the respective arms. In this way, the movement of the roll between the initial position and the position following turning is a purely translatory movement in the radial direction passing through the groove plane. The roll therefore remains parallel to itself.
  • the second solution consists in compensating for the reduction in diameter of the roll by means of an identical displacement of the pin about which the roll-support lever rotates, this displacement being obtained by means of a series of eccentrics nested inside each other.
  • each rolling station requires three complete series of shims; each series must contain a number of shims equal to the number of turning operations which can be performed on the rolls from the time when they are new to when they are completely worn.
  • WO 2010/082174 A1 is regarded as being the prior art closest to the subject-matter of claim 1, and discloses a roll-holding cartridge for rolling an elongated article having an axis X, comprising two side walls, a plurality of roll-lever units, and an adjusting actuator, wherein:
  • the object of the present invention is therefore to overcome at least partly the drawbacks mentioned above with reference to the prior art.
  • a task of the present invention is to provide a rolling station for a continuous rolling mill which allows compensating for, in a simple and rapid manner, the reduction in the diameter of the roll following reconditioning by means of turning.
  • Each stand 22 comprises, in a manner known per se, a plurality of actuators 21, a plurality of motor-reducer-spindle units 23, and a roll-holder cartridge 24.
  • the roll-holder cartridge 24 comprises two side walls 26, a plurality of roll-lever units 30, two adjusting rings 28 and an adjusting actuator 32.
  • Each side wall of the cartridge comprises a plurality of first seats 260; each adjusting ring 28 comprises a plurality of second seats 280; and each of the roll-lever units 30 is mounted on the cartridge 24 so as to be able to pivot about a pin 300, each end of each pin being housed in the axial direction inside a first seat 260 and a second seat 280, respectively.
  • first seats allow a displacement of the respective pins 300 in a purely tangential direction t
  • second seats 280 allow a displacement of the respective pins 300 in a purely radial direction r
  • the two adjusting rings 28 may be rotated about the axis X by means of the adjusting actuator 32.
  • axial is understood as meaning the direction of any straight line a parallel to the rolling axis X.
  • radial is understood as meaning the direction of any straight half-line r which has its origin on the rolling axis X and is perpendicular thereto.
  • circumferential is understood as meaning the direction of any circumference c centred on the rolling axis X and lying in a plane perpendicular thereto.
  • tangential is understood as meaning the direction of any straight line t tangential to a circumference c .
  • the side walls 26 are fixed to the cartridge 24, while the adjusting rings 28 are movable with respect thereto, and in particular they may rotate about the axis X .
  • the cartridge 24 is fixed to the rolling stand 22 during rolling of the tube 18 and, potentially, during some of the slight movements of the pins 300 which will be described below. It is however true that, in some embodiments of the rolling mill 20, the cartridge 24 may be extracted from the rolling stand 22, for example for the operations of reconditioning of the rolls 304 and of the consequent displacement of the pins 300.
  • the cartridge 24 comprises two side walls 26 and two adjusting rings 28.
  • the detailed description which follows, as well as Figures 10 to 14 refers to only one of the two walls 26, to the respective ring 28 and to the seats 260 and 280 formed therein. Obviously the figures and the description are applicable also to the other wall 26 which is substantially symmetrical with respect to the wall considered here.
  • a roll 304 is mounted on the cartridge 24 by means of a roll-support lever 302 (or simply lever 302).
  • the lever 302 is mounted on the cartridge 24 so as to be able to pivot about the pin 300.
  • the pin 300 has an axis a parallel to the rolling axis X.
  • the lever 302 supports the roll 304 by means of two arms 306.
  • Each roll 304 comprises, moreover, an actuator 21 (visible in Figure 1 ) suitable for applying to the roll 304 a force in a radial direction r with respect to the axis X.
  • the force applied by the actuator 21, indicated by the bold arrow F in Figures 2 to 4 is the one which produces the plastic deformation of the tube 18 being processed.
  • the composition of the three forces F produced by the three actuators 21 of a stand 22 results in a radial reduction in the thickness of the tube 18 and in an axial lengthening of the tube itself.
  • the actuator 21 comprises a hydraulic jack which acts on a thrusting surface 302 integral with the lever 302.
  • the station also comprises motor-reducer-spindle units 23 suitable for causing the rotation of each roll 304.
  • the rotation of the roll 304 performed by these units 23 is the one which provides the feeding movement displacing, by means of friction, the tube 18 along the axis X.
  • Each roll 304 defines an axis of rotation I .
  • the roll 304 is formed symmetrically with respect to the axis I and has, formed on its periphery, a groove which is able to reproduce an arc of the outer profile of the tube 18.
  • each rolling stand 22 comprises three rolls 304, each of them must act on a nominal arc of 120°.
  • each roll 304 it is also possible to define a groove plane which intersects, perpendicularly with respect to the axis I , the roll 304 along its smaller section.
  • the rolls 304 must be periodically reconditioned in order to be able to ensure an optimum profile of the groove. Reconditioning is performed by means of turning of the roll 304, with the consequent gradual reduction of its diameter.
  • FIG. 2 to 4 shows a roll 304 at the beginning, halfway through and at the end of its working life respectively. As can be seen in Figure 2 , the roll 304 starts its working life with a maximum diameter.
  • the displacement of the pin 300 of the lever 302 is obtained by means of reconfiguration of a series of eccentrics nested inside each other.
  • This reconfiguration operation is particularly laborious because it must be completed singly for each of the pins 300.
  • the side walls 26 of the cartridge 26 and the adjusting rings 28 are shown with conventional forms different from each other.
  • the adjusting rings 28 are shown as circular rims with a radial lug 284 (see Figures 8 , 11 and 12 ) or as circular rim segments (see Figures 13 to 15 ).
  • the side walls 26 of the cartridge 24 are shown as polygonal rims (see Figures 8 , 10 and 12 ) or as polygonal rim segments (see Figures 13 to 15 ).
  • each of the first seats 260 formed in the side walls 26 and therefore integral with the cartridge 24, allows displacement of the pin 300 housed therein in a purely tangential direction t.
  • each of the second seats 280 which are formed in the adjusting ring 28 and therefore rotatable about the axis X, allows displacement of the pin 300 housed therein in a purely radial direction r.
  • each of the first seats 260 comprises a recess 261 and a slider block 262 sliding inside the recess 261.
  • a hole 263 formed in the slider block 262 is intended to receive a first portion 360 of the end of the pin 300.
  • first seat 260 is such that the slider block 262 is able to slide inside the recess 261 only in the tangential direction t.
  • each of the second seats 280 comprises a recess 281 and a slider block 282 sliding inside the recess 281.
  • a hole 283 formed in the slider block 282 is intended to receive a second portion 380 of the end of the pin 300.
  • the form of the second seat 280 is such that the slider block 282 is able to slide inside the recess 281 only in the radial direction r.
  • Each axial end of each pin 300 is therefore housed simultaneously inside a first seat 260 and inside a second seat 280.
  • Each lever 302 by means of a pin 300, is rotatable about an axis a.
  • the three axes a of each cartridge 24 are located on a circumference centred on the axis X and are spaced from each other by 120°.
  • the pins 300 are movable, and the axes a are movable with them, it is convenient to define a nominal position for them in relation to which the movements of the pins 300 and therefore the axes a may be more easily described.
  • the nominal position is that shown schematically in Figure 14 , where the slider block 262 is situated at the centre of its working stroke inside the recess 261 and the slider block 282 is situated at the centre of its working stroke inside the recess 281. It is therefore possible to define the nominal radial direction r 0 , i.e. the one which passes through the axis a when the latter is in its nominal position. Similarly it is also possible to define the nominal tangential direction t 0 , i.e. the one which passes through the axis a when the latter is in its nominal position.
  • the nominal radial direction r 0 is perpendicular to the contact surfaces of the recess 261 with the slider block 262 of the first seat 260. Moreover, the nominal radial direction r 0 is parallel to the contact surfaces of the recess 281 with the slider block 282 of the second seat 280. Similarly, as can be seen in Figure 14 , the nominal tangential direction t 0 is perpendicular to the contact surfaces of the recess 281 with the slider block 282 of the second seat 280. Moreover, the nominal tangential direction t 0 is parallel to the contact surfaces of the recess 261 with the slider block 262 of the first seat 260.
  • the first seat 260 allows displacement of the respective pin 300 in a tangential direction t and since the first seat 260 is fixed with respect to the cartridge 24, consequently the tangential direction t along which the pin 300 may be displaced is always the same (relative to the cartridge 24) and coincides with the nominal tangential direction t 0 .
  • the second seat 280 allows displacement of the respective pin 300 in a radial direction r and since the second seat 280 is rotatable about the axis X together with the ring 28, consequently the radial direction r along which the pin 300 may be displaced varies continuously about the nominal radial direction r 0 .
  • the adjusting ring 28 may be rotated about the axis X by means of operation of the adjusting actuator 32 which acts, for example, on the radial lug 284 integral with the adjusting ring 28.
  • the adjusting ring 28 assumes exactly the form which is shown in the accompanying figures. It could for example not form a complete circle, provided that it accommodates all the second seats 280 of all the pins 300 and provided that it ensures a sufficient rigidity to ensure the same movements for all the seats 280.
  • the rotation of the adjusting ring 28 results in a movement of the second seats 280 which takes place generally in a purely circumferential direction c.
  • This feature is illustrated schematically in Figure 8 where the angular movements have been amplified for greater clarity.
  • the respective axis a (indicated by x in Figures 14 and 15 ) would describe an arc of a circumference c. Since, however, the pin 300 is housed simultaneously inside the first seat 260 and the second seat 280, its movement is determined by the combination of the constraints imposed by the two seats 260 and 280.
  • the movement of the adjusting ring 28 imparts a thrust in the circumferential direction c to the slider block 282.
  • the surface of contact between the recess 281 and the slider block 282 is in fact perpendicular to the thrust and therefore does not involve in any way the only (radial) degree of freedom permitted by the particular form of the second seat 280.
  • the movement of the slider block 282 causes the movement also of the pin 300 since it is partially housed inside the hole 283.
  • the pin 300 itself, since it is partially housed inside the hole 263, therefore transmits a thrust in the circumferential direction c to the slider block 262 of the first seat 260 which, it is recalled, is fixed with respect to the cartridge 24 and therefore, potentially, with the entire plant 20.
  • the particular form of the first seat 260 allows the slider block 262 a single degree of freedom, i.e. that of being able to slide inside the recess 261 in the nominal tangential direction t 0 .
  • the circumferential trajectory c and the nominal tangential trajectory t 0 diverge increasingly the one from the other moving away from the nominal position. In Figure 15 it can therefore be seen how the final position of the axis a (indicated by x) moves away from the circumferential trajectory c.
  • the pin 300 in order to compensate for the reduction in diameter b of the roll 304 following reconditioning by means of turning, the pin 300 (and the axis a together with it) must be displaced by an identical length d along the nominal tangent t 0 .
  • This displacement may be performed owing to the geometric composition of the degrees of freedom permitted by the first seats 260 and by the second seats 280.
  • the displacement of the axis a along the nominal tangent t 0 may be obtained in theoretical terms by the combination of a rotation along the direction c (imparted by rotation of the adjusting ring 28) with a displacement along the radial direction r performed at the end of rotation (imposed by the geometric constraints).
  • the total working stroke d of the pin 300 along the nominal tangent to is such as to be able to compensate for the overall reduction in diameter b affecting the roll 304 from the start to the end of its working life.
  • the total working stroke of the pin 300 along the nominal tangent t 0 is between about 20 mm and about 30 mm and is preferably about 25 mm. This stroke d is substantially equal to the total working stroke of the slider block 262 inside the respective recess 261.
  • the total working stroke of the pin 300 is composed of a half stroke of about 12.5 mm to the right of the nominal position and a half stroke of about 12.5 mm to the left of the nominal position.
  • the pin 300 is positioned at a first end point along its working stroke ( Figure 2 ).
  • the halfway point of the working stroke of the pin regarded above as being the nominal position, is reached halfway through the working life of the roll 304 ( Figure 3 ).
  • the cartridge 24 comprises an adjusting actuator 32 suitable for imparting to the adjusting rings 28 a rotation about the axis X.
  • This adjusting actuator 32 may assume different forms, such as that of a mechanical screw jack, a mechanical worm screw and rack jack, a hydraulic jack, etc.
  • the adjusting actuator 32 comprises a jack 320, for example a hydraulic jack, which is connected to a movable member 321.
  • the jack 320 is mounted on the cartridge 24 so as to impart to the movable member 321 a displacement along a radial direction r relative to the axis X.
  • the movable member 321 in turn comprises an inclined guide 322 inside which a slide 323 is slidable seated.
  • the slide 323 comprises a hole 324 which receives a pin 325 integral with both the lugs 284 of the adjusting rings 28.
  • This kinematic configuration has the effect that, following a purely radial displacement of the movable element 321, the inclination of the guide 322 causes a displacement of the slide 323 which has a radial component e r and a circumferential component e c (see Figure 17 ). It should be noted that, for the sole purposes of description of the adjusting actuator 32, it is no longer necessary to distinguish the circumferential direction c from the tangential direction t. Since the slide 323 houses the pin 325, the radial displacement of the movable member 321 causes a circumferential displacement of the pin 325 and therefore a rotation about the axis X of the lugs 284 of the adjusting rings 28. In accordance with certain embodiments, the inclination of the slide 323 with respect to the radial direction ranges between 10° and 20°, preferably between 12° and 18°.
  • the inclination of the slide 323 with respect to the radial direction is about 15°.
  • This geometric configuration involves a ratio of about 1:0.267 between the radial component e r and the circumferential component e c of the displacement of the slide 323.
  • This embodiment of the adjusting actuator 32 is particularly advantageous compared to other embodiments where the (for example hydraulic) jack may be oriented so as to act directly in the tangential direction.
  • the main advantage arising from the arrangement of the inclined guide 322 in the kinematic chain is that, on the one hand, it allows transmission of the force from the actuator 32 to the single pins 300 via the adjusting rings 28, but at the same time substantially prevents transmission of the forces in the reverse direction, i.e. from the pins 300 to the actuator 32.
  • the forces F generated by the actuators 21 and the consequent reactions generated by the tube 18 and by the mandrel contained inside it result in the generation of notable constraint reactions on the pins 300.
  • the pins 300 are fixed with respect to the stand 22 and the constraint reactions are therefore transmitted to the cartridge 24.
  • the cartridge 24 allows the pins 300 a certain mobility with respect to the stand 22. In other words, while the radial components of the constraint reactions of the pins 300 are still transmitted to the cartridge 24, the tangential and/or circumferential components are transmitted via the adjusting rings 28 to the adjusting actuator 32.
  • the overall rigidity of the system would depend precisely on the rigidity of the jack itself. In the case of a hydraulic jack, the rigidity of the system would therefore not be satisfactory owing to the compressibility of the oil column. On the contrary, the radial orientation of the jack and the presence of the inclined guide 322 result in a drastic reduction in the forces which are transmitted to the jack and which must be opposed by it.
  • a significant advantage arising from the use of a cartridge 24 according to the invention in a rolling plant 20 is that of allowing rapid, simple and precise adjustment of the position of the pins 300 following reconditioning by means of turning of the rolls 304.
  • the operation of displacement of the pins 300 involves merely operation of the adjusting actuator 32.
  • the consequent rotation of the adjusting rings 28 causes simultaneous (purely tangential) displacement d of all the pins 300 of the cartridge 24, thus allowing precise and rapid compensation of the reduction in diameter b of the rolls 304.
  • This operation which must necessarily be performed after reconditioning of the rolls 304, is preferably performed with the cartridge 24 removed from the rolling mill 20.
  • the outer profile of the tube 18 will continue to be a three-lobed figure composed of arcs of a circle which are not connected together, but will have a more regular form and a more uniform thickness compared to those which may be obtained by means of a cartridge of the known type.
  • the invention also relates to a stand 22 and a rolling mill 20 for performing the rolling of long semi-finished articles, typically seamless tubes 20.
  • the rolling stand 22 according to the invention comprises a plurality of actuators 21, a plurality of motor-reducer-spindle units 23, and a cartridge 24 in accordance with that described above.
  • the rolling mill 20 according to the invention comprises a plurality of rolling stations and associated stands 22 in accordance with that described above.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Metal Rolling (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Control Of Metal Rolling (AREA)
  • Crushing And Grinding (AREA)
EP12759203.8A 2011-07-26 2012-07-16 Roll-holder cartridge for a rolling mill Active EP2736660B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
IT001391A ITMI20111391A1 (it) 2011-07-26 2011-07-26 Cartuccia portarulli per un laminatoio
PCT/IB2012/053629 WO2013014572A2 (en) 2011-07-26 2012-07-16 Roll-holder cartridge for a rolling mill

Publications (2)

Publication Number Publication Date
EP2736660A2 EP2736660A2 (en) 2014-06-04
EP2736660B1 true EP2736660B1 (en) 2015-09-16

Family

ID=44511261

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12759203.8A Active EP2736660B1 (en) 2011-07-26 2012-07-16 Roll-holder cartridge for a rolling mill

Country Status (8)

Country Link
US (1) US20140182346A1 (ru)
EP (1) EP2736660B1 (ru)
JP (1) JP6130832B2 (ru)
CN (1) CN103781564B (ru)
AR (1) AR088745A1 (ru)
EA (1) EA025048B1 (ru)
IT (1) ITMI20111391A1 (ru)
WO (1) WO2013014572A2 (ru)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020202107B4 (de) 2020-02-19 2022-08-11 Kocks Technik Gmbh & Co Kg Vorrichtung zum Belasten von Walzen und Innenteilen eines Walzgerüsts während der Justierung einzelner Walzenkaliber
IT202000023752A1 (it) * 2020-10-08 2022-04-08 Sms Group S P A Laminatoio per manufatti allungati pieni

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE917963C (de) * 1950-04-25 1954-09-16 Schloemann Ag Einrichtung zum Anstellen der Walzen von Rohrwalzwerken
CN2085265U (zh) * 1990-11-06 1991-09-25 冶金工业部北京冶金设备研究所 Y型轧机三辊同步调整装置
IT1254864B (it) * 1992-04-15 1995-10-11 Filippo Cattaneo Laminatoio continuo per tubi senza saldatura del tipo a mandrino e conunita' di laminazione a tre o piu' rulli comandati e regolabili
JP2983126B2 (ja) * 1993-06-28 1999-11-29 住友重機械工業株式会社 ロールミル
IT1271808B (it) * 1994-12-28 1997-06-09 Innocenti Eng Spa Unita' di laminazione per corpi tubolari o astiformi in genere
IT1298750B1 (it) * 1998-03-18 2000-02-02 Demag Italimpianti Spa Laminatoio a bracci oscillanti,destinato in particolare ma non esclusivamente alla laminazione di tubi senza saldatura
CN1270086A (zh) * 1999-01-17 2000-10-18 张少渊 一种单传动输入轴可调式三辊(120°y型)轧机
JP4238744B2 (ja) * 2004-03-03 2009-03-18 住友金属工業株式会社 ３ロール式管圧延機におけるインナーハウジングの装着方法及び密着状態検知方法並びに３ロール式管圧延機
ITMI20051480A1 (it) * 2005-07-29 2007-01-30 Danieli & C Ohg Sp A Laminatoio con gabbie a tre rulli regolabili
BRPI0621813A2 (pt) * 2006-06-12 2011-12-20 Sms Demag Innse S P A laminador de mandril retido para tubos sem costura
IT1392679B1 (it) * 2009-01-19 2012-03-16 Sms Demag Innse S P A Ora Sms Innse S P A Rullo per un laminatoio

Also Published As

Publication number Publication date
WO2013014572A2 (en) 2013-01-31
AR088745A1 (es) 2014-07-02
CN103781564A (zh) 2014-05-07
EA201490341A1 (ru) 2014-05-30
JP6130832B2 (ja) 2017-05-17
EP2736660A2 (en) 2014-06-04
EA025048B1 (ru) 2016-11-30
CN103781564B (zh) 2015-11-25
JP2014523814A (ja) 2014-09-18
US20140182346A1 (en) 2014-07-03
ITMI20111391A1 (it) 2013-01-27
WO2013014572A3 (en) 2013-03-21

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