EP0258482A1 - Cage de laminoir à cylindres déplaçables axialement - Google Patents

Cage de laminoir à cylindres déplaçables axialement Download PDF

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Publication number
EP0258482A1
EP0258482A1 EP86112269A EP86112269A EP0258482A1 EP 0258482 A1 EP0258482 A1 EP 0258482A1 EP 86112269 A EP86112269 A EP 86112269A EP 86112269 A EP86112269 A EP 86112269A EP 0258482 A1 EP0258482 A1 EP 0258482A1
Authority
EP
European Patent Office
Prior art keywords
roll
rolls
bale
contour
length
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.)
Granted
Application number
EP86112269A
Other languages
German (de)
English (en)
Other versions
EP0258482B1 (fr
Inventor
Tilmann Dr. Schultes
Gerd Beisemann
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 Siemag AG
Original Assignee
SMS Schloemann Siemag AG
Schloemann Siemag AG
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 Schloemann Siemag AG, Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to DE8686112269T priority Critical patent/DE3668121D1/de
Publication of EP0258482A1 publication Critical patent/EP0258482A1/fr
Application granted granted Critical
Publication of EP0258482B1 publication Critical patent/EP0258482B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • B21B13/142—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 by axially shifting the rolls, e.g. rolls with tapered ends or with a curved contour for continuously-variable crown CVC
    • 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
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/025—Quarto, four-high stands
    • 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
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/028—Sixto, six-high stands

Definitions

  • the invention relates to a roll stand with two work rolls, each of which is optionally supported directly or via an intermediate roll on a back-up roll, the rolls of a pair of rolls being axially displaceable in opposite directions and each of the displaceable rolls being axially parallel over at least part of the length of the roll bale Straight, deviating, curved contour that extends over the entire length of the roll barrel and the contours of the two rolls of the pair of rolls complement each other only in a certain axial position of the rolls.
  • a rolling stand of this type is already known from DE-PS 30 38 865. It has the essential advantage that the shape of the roll gap and thus the rolling strip cross-section influence practically exclusively by the axial displacement of the rollers provided with the curved contour and the rolling force distribution without effort can change. The shape of the roll gap and thus the cross-sectional shape of the rolled strip can be influenced even by small displacement paths of the rollers having the curved contour, without the need to directly adjust the position of the displaceable rollers to the width of the rolling stock. Not only roll stands with back-up and / or intermediate rolls make it possible to use the measures according to DE-PS 30 38 865, but these measures can also be easily implemented with duo roll stands.
  • the rolls of several pairs of rolls of a set of rolls have an adapted curved contour on their roll bales and are axially displaceable relative to one another.
  • the rolls of the pair of work rolls and the rolls of the support roll pair can also have a curved contour that extends over the entire length of the roll barrel.
  • Such an operating state of the roll stands can particularly easily lead to undesirable damage to the roll bales.
  • the present invention therefore aims to overcome these drawbacks. It is therefore based on the task of proposing measures by means of which a reduction in the line load peaks is achieved on those rollers which have the curved contour which extends over the entire length of their roller barrel.
  • the length half of the bale having the concavely curved contour has a slight reduction in diameter following the edge of the bale, preferably over a length range which corresponds to the intended one Displacement path is adapted for the roller in question. If a displacement path of approximately 100 mm is provided for this roller relative to the roller adjacent to it and coming into line contact with it, then the cylindrically tapering longitudinal section should also be at least 100 mm at the end of the lengthwise half of the roller bale having the concave contour.
  • the object can also be achieved according to the invention in that the rolls with the cylindrical roller bales are each provided with a slightly tapered contour towards the edge of the bale at that end of the bale which is assigned to the concavely curved contour section of a roller having a curved roller bale contour.
  • the conically tapered bale contour should extend over a length range of the roll bale which is at least equal to the axial displacement path between the adjacent rolls.
  • the taper of the tapered contour on the cylindrical roller bale can be designed so that it corresponds at least approximately to the course of the concave contour at the end of the roller adjacent to it and coming into contact with it.
  • roller sets of the four-roll mill stand according to FIG. 1 and the six-roll mill stands according to FIGS. 2 to 4 are shown in the drawing.
  • the four-roll stand 11 according to FIG. 1 works with a set of rolls which consists of the pair of backup rolls 12, 13 and the pair of work rolls 14, 15.
  • the pair of work rolls 14, 15 delimits a roll gap 16 for the rolled strip 17, the height of which is determined in the usual way by adjusting device (not shown) which act on the chocks of the support roll pair 12, 13.
  • the roller bales 12a and 13a of the support rollers 12 and 13 each have a curved contour when viewed in their longitudinal direction.
  • the contour of the roller barrel 12a is convexly curved in its left half, while it has a concave curvature in its right half.
  • the lower support roller 13 namely that the roller barrel 13a has a convexly curved contour in the right half of its length, while it is provided with a concave curved contour in its left half.
  • Both longitudinal sections of the roller bales 12a and 13a of the support rollers 12 and 13 are determined by the same curvature curves and it can also be seen from FIG. 1 that both support rollers 12 and 13 have an identical - here bottle-like - shape of the roller barrel 12a and 13a and in the roll stands of the roll stand 11 are accommodated relative to one another in an installed position turned through 180 °.
  • the curved contour of the roll bales 12a and 13a ends at the end of the lengthwise half having the concave contour towards the edge of the bale cylindrically over a certain length section 12b or 13b.
  • the roll barrel 12a or 13a has a constant diameter 12c or 13c over the length section 12b or 13b.
  • the two work rolls 14 and 15 of the work roll pair also have roll bales 14a and 15a with a contour which is curved over their length and which is designed to be complementary to the contour of the roll bale 12a and 13a of the adjacent support roll 12 and 13, respectively.
  • the roll barrel 14a of the upper work roll 14 has a concave contour curve over its left half and a convex contour curve over its right half, while vice versa
  • the roll barrel 15a of the lower work roll 15 has a convex curve over the left half and over that right half is concavely curved.
  • the two work rolls 14 and 15 have an identical - namely bottle-like - shape of their roll bales 14a and 15a, and they are also accommodated in the roll stands relative to one another in an installed position turned through 180 °.
  • the curved contour of the roll barrel 14a or 15a ends cylindrically at the end of the lengthwise half having the concave contour towards the edge of the bale over a certain length section 14b or 15b, i.e. there has a constant diameter 14c or 15c.
  • the roller gap 16 has a constant cross-sectional height over the entire length of the bale, as is shown in FIG. 1, although it has a slightly S-shaped curvature .
  • the rolled strip 57 is therefore rolled out over its entire width with a uniform thickness.
  • the height of the roll gap 16 between the two contoured bales 14a and 15a of the work rolls 14 and 15 depends on the one hand on the distance between the axes of the two work rolls 14 and 15 and on the respective radius the roll barrel contour around the relevant roll axes.
  • the roll gap 16 can have a considerable cross-sectional shape can be varied. Depending on the setting made, either the rolling pressure on the longitudinal edges of the rolled strip 17 can be increased or reduced. However, it is also possible to influence the pressure distribution between the roller bales 12a and 14a and 13a and 15a of the support roller set 12, 13 and work roller set 14, 15 in a very sensitive manner and thus further optimize the shape of the roll gap 16.
  • the cylindrically tapering end regions 12b, 13b and 14b, 15b of their roller balls 12a, 13a and 14a, 15a should also have at least one Have a length of 100 mm.
  • the six-roll stand 21 according to FIG. 2 has the same basic structure as the four-roll stand 11 according to FIG. 1. In addition to the two back-up rolls 22 and 23 and the two work rolls 24 and 25, this six-roll stand 21 still comprises two intermediate rolls 28 and 29. In this case, too, the two working rolls 24 and 25 of the roll gap 26 for the rolled strip 27 are limited in between.
  • the intermediate rolls 28 and 29 have roll rolls with a curved contour in their longitudinal direction, which are convex over one half of the length and is concavely curved over the other half of the length.
  • the backup rolls 22 and 23 have roll bales 22a and 23a
  • the work rolls 24 and 25 are provided with roll bales 24a and 25a
  • the intermediate rolls 28 and 29 have roll bales 28a and 29a.
  • the curved contours are matched to one another on the roller bales 22a, 28a, 24a and 23a, 29a, 25a, which are in contact with one another, in such a way that they are in the central axial position of all roller pairs 22, 23; 28, 29; Complement 24, 25 of the six-roll stand 21 according to FIG. 2 so that the roll gap 26 for the rolled strip 27 then has the same height over its entire length despite its slightly S-shaped cross-sectional shape.
  • the contour of the roller gap 26 can then be delicately influenced, specifically by the additional presence of the intermediate roller pair 28 and 29 even more sensitive than in the case of the four-roll stand 11 according to FIG. 1.
  • roller bales 22a, 23a; 28a, 29; 24a, 25a of all pairs of rollers 22, 23; 28, 29; 24, 25 in each case following the bale edge of that half of the length which has the concavely curved contour, over a certain length section 22b, 23b; 28b, 29b; 24b, 25b runs out cylindrically, as can be clearly seen in FIG. 2.
  • This cylindrical length section 22b, 23b or 28b, 29b or 24b, 25b of the roll bales 22a 23a or 28a, 29a or 24a, 25a has a diameter 22c, 23c or 28c, 29c or 24c, 25c, which is dimensioned at least slightly smaller than the diameter which the roll bale in question would have in the region of the bale edge with a normally curved contour.
  • the cylindrical longitudinal sections 22b, 23b; 28b, 29b; 24b, 25b of the roll bales 22a, 23a; 28a, 29a; 24a, 25a reliable, the emergence of line load peaks between the contacting bale surfaces at certain relative axial sliding positions between the adjacent rolls of the roll set and thereby avoid the occurrence of critical pressures.
  • support rolls 32 and 33 are used which have roll bores 32a and 33a which are cylindrically contoured over their entire length.
  • the work rolls 34 and 35 have roll balls 34a and 35a with a contour that is essentially curved over their entire length, as are the intermediate rolls 38 and 39 roll balls 38a and 39a, which have a contour that is curved over almost their entire length.
  • the curved contour in each case has a convex curve on one half of the length of the roll barrel and a correspondingly concave curve over the other half of the length.
  • the installation of the intermediate rolls 38 and 39 and the work rolls 34 and 35 in the roll stand 31 is carried out so that their bale contours complement each other with a medium axial setting and thereby determine a roll gap 36 for the rolled strip 37, which despite a slightly S-shaped curve has a constant height over its entire width.
  • the work rolls 34 and 35 and also the intermediate rolls 38 and 39 match the work rolls and the Intermediate rolls of the roll stand according to Fig. 2 completely match. That is, the diameter 34c, 35c and 38c, 39c of these longitudinal sections 34b, 35b and 38b, 39b is kept slightly smaller than the diameter that the roller bales 34a, 35a and 38a, 39a would have on the relevant bale edge if the concave arched bale contour would normally run out to this bale edge.
  • the six-roll mill stand 31 according to FIG. 3 differs from the six-roll mill stand 21 according to FIG. 2 not only in that its roll set has support rolls 32 and 33 with cylindrical roll balls 32a and 33a, but also in that these cylindrical roll balls 32a and 33a at the end which is adjacent to the concave bale contour of the intermediate rollers 38 and 39 each have a length section 32b or 33b which is provided with a contour which tapers slightly conically towards the bale edge.
  • This measure also contributes to the fact that, during the rolling operation, with certain axial relative positions of the intermediate rolls 38 and 39 to the support rolls 32 and 33, line load peaks and resulting critical pressures are avoided.
  • the work rolls 44 and 35 of the work roll pair 44, 45 roll bales 44a and 45a have a cylindrical shape over almost their entire length. Only at each end of the bale do the two work rolls 44 and 45 have short longitudinal sections 44b and 45b, respectively, which are provided with a contour which tapers slightly conically towards the edge of the bale. It can be seen in FIG. 4 that the longitudinal sections 44b and 45b which have the conically tapered contour are provided on the ends of the two work rolls 44 and 45 which are directed away from each other.
  • the roll balls 42a and 43a of the support rolls 42 and 43 as well as the roll balls 48a and 49a of the intermediate rolls 48 and 49 are, however, again provided with a curved contour almost over their entire length, this curved contour in each case having a convex curvature over its one half length and its other Half of the length has a concave curvature.
  • the concavely curved contour runs cylindrically towards the edge of the bale over a certain length section, as is the case in FIG. 4 for the support rollers 42 and 43 through the length sections 42b and 43b and for the support rollers 48 and 49 by the longitudinal sections 48b and 49b.
  • the diameter 42c, 43c or 48c, 49c of the cylindrically tapering longitudinal sections 42b, 43b or 48b, 49b is kept slightly smaller than the diameter which the roll bale 42a, 43a or 48a, 49a has on the relevant bale edge if the concavely curved contour would be carried out normally up to this edge of the bale.
  • the cylindrically tapered longitudinal sections 42b, 43b of the support rolls 42 and 43, the cylindrically tapered longitudinal sections 48b, 49b of the intermediate rolls 48 and 49 and the conically tapered longitudinal sections 44b, 45b of the work rolls 44 and 45 each have a length dimension that is at least matched to the maximum possible displacement path for the roller in question, the rolling line counteracts the occurrence of line load peaks at the points of contact between the roller balls, which could lead to pressures that are in the critical range.
  • the nip 46 for the rolling band 47 is influenced by the axially displaceable arrangement of the support rolls 42 and 43 and / or the intermediate rolls 48 and 49, while the work rolls 44 and 45 can be axially fixed in their chocks .
  • bale length corresponds to the latter is dimensioned twice the maximum possible displacement path than the bale length of the associated support roller.
  • the work rolls are each provided with a cylindrical outlet towards the edge of the bale, which lies at the end of the longitudinal half, which has the concavely curved bale contour, the length of which corresponds at least to the maximum possible displacement path of the work roll in question.
  • This cylindrical outlet on the curved bale contour of the work rolls breaks the otherwise occurring line load peak in rolling operation, provided the work rolls are axially displaced in the negative direction relative to the support rolls, i.e. the bale edge of the work roll adjacent to the cylindrical outlet protrudes axially from the corresponding bale edge of the associated backup roll.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Storage Of Harvested Produce (AREA)
EP86112269A 1985-04-16 1986-09-04 Cage de laminoir à cylindres déplaçables axialement Expired - Lifetime EP0258482B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE8686112269T DE3668121D1 (de) 1986-09-04 1986-09-04 Walzgeruest mit axial verschiebbaren walzen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3513554 1985-04-16
DE19863602698 DE3602698A1 (de) 1985-04-16 1986-01-30 Walzgeruest mit axial verschiebbaren walzen

Publications (2)

Publication Number Publication Date
EP0258482A1 true EP0258482A1 (fr) 1988-03-09
EP0258482B1 EP0258482B1 (fr) 1990-01-10

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EP86112269A Expired - Lifetime EP0258482B1 (fr) 1985-04-16 1986-09-04 Cage de laminoir à cylindres déplaçables axialement

Country Status (4)

Country Link
US (1) US4781051A (fr)
EP (1) EP0258482B1 (fr)
JP (1) JPH0755323B2 (fr)
DE (1) DE3602698A1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0543014A4 (fr) * 1991-05-16 1995-05-24 Kawasaki Steel Co
US5622073A (en) * 1991-05-16 1997-04-22 Kawasaki Steel Corporation Six high rolling mill
WO2002009896A1 (fr) * 2000-07-29 2002-02-07 Sms Demag Aktiengesellschaft Procede et dispositif pour la translation orientee sur les rives de bande des cylindres intermediaires dans une cage de laminoir a 6 cylindres
EP0451874B2 (fr) † 1990-04-13 2003-08-27 Hitachi, Ltd. Laminoir à quatre cylindres
WO2007144162A1 (fr) * 2006-06-14 2007-12-21 Siemens Vai Metals Technologies Gmbh & Co Cage de laminoir pour la fabrication de bande laminée ou de tôle
AT509107B1 (de) * 2009-12-10 2011-09-15 Siemens Vai Metals Tech Gmbh Walzgerüst zur herstellung von walzband
CN110983711A (zh) * 2019-12-09 2020-04-10 湖州菠萝蜜服饰有限公司 一种面料预缩设备给湿装置的转角传动辊

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JPH0763737B2 (ja) * 1988-05-11 1995-07-12 日新製鋼株式会社 ワークロールと接する中間ロール及びそれが組み込まれた多段圧延機
DE19719318C2 (de) * 1997-05-08 2003-06-12 Sms Demag Ag Verfahren zur Beeinflussung der Bandkontur im Kantenbereich eines Walzenbandes
DE19812263A1 (de) * 1998-03-20 1999-09-23 Schloemann Siemag Ag Walze für ein Walzgerüst
US6119500A (en) * 1999-05-20 2000-09-19 Danieli Corporation Inverse symmetrical variable crown roll and associated method
AT410765B (de) * 2001-09-12 2003-07-25 Voest Alpine Ind Anlagen Walzgerüst zur herstellung von walzband
JP2005052864A (ja) * 2003-08-04 2005-03-03 Ishikawajima Harima Heavy Ind Co Ltd 帯板製造設備
BRPI0402683B1 (pt) * 2003-08-04 2013-12-24 Ishikawajima Harima Heavy Ind Laminador de chapa
DE10359402A1 (de) * 2003-12-18 2005-07-14 Sms Demag Ag Optimierte Verschiebestrategien als Funktion der Bandbreite
CN100413608C (zh) * 2005-03-28 2008-08-27 宝山钢铁股份有限公司 一种用以支撑连续可变凸度轧机工作辊的支撑辊
JP4960009B2 (ja) * 2006-05-09 2012-06-27 スチールプランテック株式会社 圧延ロール、圧延機および圧延方法
US8607848B2 (en) * 2008-08-05 2013-12-17 Nucor Corporation Method for casting metal strip with dynamic crown control
US8607847B2 (en) * 2008-08-05 2013-12-17 Nucor Corporation Method for casting metal strip with dynamic crown control
US8063674B2 (en) * 2009-02-04 2011-11-22 Qualcomm Incorporated Multiple supply-voltage power-up/down detectors
US8505611B2 (en) 2011-06-10 2013-08-13 Castrip, Llc Twin roll continuous caster
US9120134B2 (en) 2011-10-26 2015-09-01 I2S, Llc Methods of shifting and bending rolls in a rolling mill
CN102921741A (zh) * 2012-10-25 2013-02-13 苏州有色金属研究院有限公司 用于轧机特殊辊形辊缝凸度计算的有限元模型的建模方法
EP3124130A1 (fr) * 2015-07-28 2017-02-01 Primetals Technologies Austria GmbH Meule de cylindre destinee a l'evitement cible de quarts d'onde
CN205659983U (zh) * 2016-06-15 2016-10-26 日照宝华新材料有限公司 一种esp生产线用长公里数轧制辊
CN117483424B (zh) * 2023-11-17 2024-06-04 燕山大学 一种改善镁合金板边裂的可轴向移动异形轧辊及轧制方法

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EP0091540A1 (fr) * 1982-04-10 1983-10-19 Sms Schloemann-Siemag Aktiengesellschaft Cage de laminoir à cylindres déplaçables axialement

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0451874B2 (fr) † 1990-04-13 2003-08-27 Hitachi, Ltd. Laminoir à quatre cylindres
US5622073A (en) * 1991-05-16 1997-04-22 Kawasaki Steel Corporation Six high rolling mill
EP0543014A4 (fr) * 1991-05-16 1995-05-24 Kawasaki Steel Co
KR100796255B1 (ko) * 2000-07-29 2008-01-21 에스엠에스 데마그 악티엔게젤샤프트 6단 롤 스탠드에서 중간 롤을 스트립 에지에 적합하게맞추어 변위시키는 방법 및 장치
WO2002009896A1 (fr) * 2000-07-29 2002-02-07 Sms Demag Aktiengesellschaft Procede et dispositif pour la translation orientee sur les rives de bande des cylindres intermediaires dans une cage de laminoir a 6 cylindres
US7181949B2 (en) 2000-07-29 2007-02-27 Sms Demag Aktiengesellschaft Strip-edge-based displacement of intermediate rolls in six-high rolling stand
CN101511498B (zh) * 2006-06-14 2011-06-15 西门子Vai金属技术两合公司 用来制造轧带或者板材的轧机机架
WO2007144161A1 (fr) * 2006-06-14 2007-12-21 Siemens Vai Metals Technologies Gmbh & Co Cage de laminoir pour la fabrication de bande laminée ou de tôle
WO2007144162A1 (fr) * 2006-06-14 2007-12-21 Siemens Vai Metals Technologies Gmbh & Co Cage de laminoir pour la fabrication de bande laminée ou de tôle
RU2428268C2 (ru) * 2006-06-14 2011-09-10 Сименс Фаи Металз Текнолоджиз Гмбх Прокатная клеть для изготовления катаной ленты или листа
RU2442669C2 (ru) * 2006-06-14 2012-02-20 Сименс Фаи Металз Текнолоджиз Гмбх Клеть прокатного стана для производства полосы или листа
US8413476B2 (en) 2006-06-14 2013-04-09 Siemens Vai Metals Technologies Gmbh Rolling mill stand for the production of rolled strip or sheet metal
US8881569B2 (en) 2006-06-14 2014-11-11 Siemens Vai Metals Technologies Gmbh Rolling mill stand for the production of rolled strip or sheet metal
AT509107B1 (de) * 2009-12-10 2011-09-15 Siemens Vai Metals Tech Gmbh Walzgerüst zur herstellung von walzband
US9789521B2 (en) 2009-12-10 2017-10-17 Primetals Technologies Austria GmbH Rolling stand for producing rolled strip
CN110983711A (zh) * 2019-12-09 2020-04-10 湖州菠萝蜜服饰有限公司 一种面料预缩设备给湿装置的转角传动辊

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JPS6384702A (ja) 1988-04-15
JPH0755323B2 (ja) 1995-06-14
US4781051A (en) 1988-11-01
DE3602698A1 (de) 1986-10-16
EP0258482B1 (fr) 1990-01-10

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