EP1281449A2 - Druckmittelzylinder und Walzwerk - Google Patents

Druckmittelzylinder und Walzwerk Download PDF

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Publication number
EP1281449A2
EP1281449A2 EP02015572A EP02015572A EP1281449A2 EP 1281449 A2 EP1281449 A2 EP 1281449A2 EP 02015572 A EP02015572 A EP 02015572A EP 02015572 A EP02015572 A EP 02015572A EP 1281449 A2 EP1281449 A2 EP 1281449A2
Authority
EP
European Patent Office
Prior art keywords
thin plunger
cylinder
liner
plunger
housing
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.)
Withdrawn
Application number
EP02015572A
Other languages
English (en)
French (fr)
Inventor
Mikio Mitsubishi Heavy Indust. Ltd Yamamoto
Susumu Mitsubishi Heavy Indust. Ltd Oota
Osamu Mitsubishi Heavy Indust. Ltd Yoshihara
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP1281449A2 publication Critical patent/EP1281449A2/de
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks

Definitions

  • This invention relates to a fluid pressure cylinder to be actuated by the supply of an oil pressure or the like, and a rolling mill having the fluid pressure cylinder and adapted to roll a strip material or the like, which passes between upper and lower rolling rolls, to a predetermined thickness.
  • upper and lower work rolls are rotatably supported inside a housing via work roll chocks, and the upper and lower work rolls are opposed to each other.
  • Upper and lower backup rolls are also rotatably supported inside the housing via backup roll chocks, and the upper and lower backup rolls are opposed to the upper and lower work rolls.
  • a screw down device for imposing a rolling load on the upper work roll via the upper backup roll is provided in an upper portion of the housing.
  • a strip is fed from an entry side of the housing, and passed between the lower work roll and the upper work roll given a predetermined load by the screw down device via the backup roll, whereby the strip is rolled to a predetermined thickness.
  • the rolled strip is delivered from a delivery side of the housing and supplied to a subsequent step.
  • mill vibrations If rolling is performed with a high rolling force and a high percentage reduction in the thickness of the strip while the horizontal dynamic stiffness of the rolling mill is low, great vibrations probably attributed to, for example, friction between the strip being rolled and the work rolls (hereinafter referred to as mill vibrations) occur in the housing or the work rolls, thereby impeding high efficiency rolling. Since the rolls are not stably supported, moreover, rolling becomes unstable, particularly when the strip is engaged between the rolls.
  • the applicant of the present application filed Japanese Patent Application No. 2000-187163 (Japanese Unexamined Patent Publication No. 2001-113308) as a solution to the above-described problems.
  • the invention of this application has upper and lower work rolls as a pair and upper and lower backup rolls as a pair rotatably supported in a housing via roll chocks; a screw down device provided in an upper portion of the housing for imposing a predetermined pressure on the upper work roll; and hydraulic cylinder mechanisms provided on an entry side and a delivery side of the housing, the hydraulic cylinder mechanisms being capable of thrusting the roll chocks in a horizontal direction.
  • the hydraulic cylinder mechanisms are actuated during rolling to eliminate the gaps between the roll chocks and the housing, thereby improving the horizontal dynamic stiffness. As a result, mill vibrations are suppressed, permitting high efficiency rolling.
  • the hydraulic cylinder mechanisms for thrusting the roll chocks in the horizontal direction require a huge thrusting force. Further, the hydraulic cylinder mechanisms undergo fluctuating loads, and their working strokes are small. Thus, when the hydraulic cylinder mechanisms are operated, their plungers do not properly move, but tend to stick, in the cylinders. Because of this faulty operation of the hydraulic cylinder mechanisms, mill vibrations cannot be suppressed reliably.
  • the present invention has been accomplished to solve the above problems. Its object is to provide a fluid pressure cylinder improved in operability, and a rolling mill which uses this fluid pressure cylinder to prevent mill vibrations and enable high efficiency rolling, and which, because of the fluid pressure cylinder, stably supports rolls to achieve a stable rolling state.
  • a fluid pressure cylinder comprising:
  • the thin plunger is supported by the cylinder so as to be movable by the guide means fitted to the thin plunger because of a convex-concave structure.
  • the thin plunger is excellent in straight line stability, and properly working without sticking, so that its operability can be improved.
  • a rolling mill comprising:
  • the thin plunger is movably supported in the cylinder by the guide means fitted to the thin plunger because of a convex-concave configuration.
  • the thin plunger is excellent in straight line stability. Even if an axial load or a fluctuating load is imposed by the roll chock during rolling, the thin plunger does not stick, but properly works, and prevents mill vibrations occurring in the housing or rolling rolls. Consequently, the passage of the strip is improved to achieve high efficiency rolling. Since the rolls are stably supported, moreover, a stable rolling state can be realized.
  • the thin plunger may be movably supported in the housing, and a liner capable of contacting and thrusting the roll chock may be connected to a front end portion of the thin plunger. Since the roll chocks can be directly thrust by the liner, the structure of the rolling mill can be simplified.
  • the rolling mill may further include greasing means for greasing a surface of the liner.
  • greasing means for greasing a surface of the liner.
  • the thin plunger may be provided in a liner portion contacting the roll chock, may be movably supported by the liner, and may have a front end portion capable of thrusting the roll chock.
  • the thin plunger can be easily incorporated by replacing the liner, so that the general-purpose properties of the rolling mill can be improved.
  • the rolling mill may further include greasing means for greasing a front end surface of the thin plunger.
  • greasing means for greasing a front end surface of the thin plunger.
  • the guide means may include a center guide of a cylindrical shape provided at a center of the cylinder, and a concave portion provided in the thin plunger and fitted over the center guide.
  • the thin plunger may be movably fitted on an inner peripheral surface of the cylinder via a liner, a ring-shaped cover may be fixed to the cylinder in correspondence with an outer peripheral portion of the thin plunger, an oil pressure supply chamber may be provided between the cylinder and the thin plunger, and a pullback mechanism may be provided between the cover and the thin plunger.
  • upper and lower work roll chocks 12 and 13 as a pair are supported in a housing 11. Shaft portions of upper and lower work rolls 14 and 15 as a pair are rotatably supported by the upper and lower work roll chocks 12 and 13, respectively, and the upper work roll 14 and the lower work roll 15 are opposed to each other. Upper and lower backup roll chocks 16 and 17 as a pair are supported above and below the upper and lower work roll chocks 12 and 13. Shaft portions of upper and lower backup rolls 18 and 19 as a pair are rotatably supported by the upper and lower backup roll chocks 16 and 17, respectively.
  • the upper backup roll 18 and the upper work roll 14 are opposed to each other, while the lower backup roll 19 and the lower work roll 15 are opposed to each other.
  • a screw down device 20 for imposing a rolling load on the upper work roll 14 via the upper backup roll 18 is provided in an upper portion of the housing 11.
  • Hydraulic cylinders (fluid pressure cylinders) 21 and 22 are mounted on an entry side and a delivery side of the housing 11 so as to be opposed to the upper work roll chock 12.
  • the hydraulic cylinders 21 and 22 can be pressed against the housing 11 by thrusting the upper work roll chock 12 from upstream and downstream sides along a transport direction.
  • Hydraulic cylinders (fluid pressure cylinders) 23 and 24 are mounted on the entry side and the delivery side of the housing 11 so as to be opposed to the lower work roll chock 13.
  • the hydraulic cylinders 23 and 24 can be pressed against the housing 11 by thrusting the lower work roll chock 13 from upstream and downstream sides along the transport direction.
  • Hydraulic cylinders (fluid pressure cylinders) 25 and 26 are mounted on the entry side and the delivery side of the housing 11 so as to be opposed to the upper backup roll chock 16.
  • the hydraulic cylinders 25 and 26 can be pressed against the housing 11 by thrusting the upper backup roll chock 16 from upstream and downstream sides along the transport direction.
  • Hydraulic cylinders (fluid pressure cylinders) 27 and 28 are mounted on the entry side and the delivery side of the housing 11 so as to be opposed to the lower backup roll chock 17.
  • the hydraulic cylinders 27 and 28 can be pressed against the housing 11 by thrusting the lower backup roll chock 17 from upstream and downstream sides along the transport direction.
  • the hydraulic cylinders 21 to 28 are mounted within the housing 11, and have practically the same configuration. Therefore, only the hydraulic cylinder 21 will be described in detail.
  • the housing 11 has a mounting concave portion 31 formed at a predetermined position opposed to the upper work roll chock 12.
  • a cylinder 32 of a cylindrical shape is fitted into the mounting concave portion 31, and is fixed by bolts (not shown).
  • a ring-shaped liner 33 is fitted on the inner peripheral surface of the cylinder 32 via an O ring 34.
  • the liner 33 takes a tapered shape by having an inclined surface 35 formed in its front end outer peripheral portion along the circumferential direction.
  • a curved surface portion 36 is formed along the circumferential direction in order to prevent stress concentration.
  • many oil holes 37 piercing therethrough in the diametrical direction are formed.
  • a center guide 38 of a cylindrical shape is fixed at the center of the cylinder 32 by bolts 39.
  • a thin plunger 40 takes a cylindrical shape, and is fitted on the inner wall surface of the liner 33 of the cylinder 32 via a slipper seal 41.
  • a concave portion 42 formed in a base end portion of the thin plunger 40 is fitted over the center guide 38 via an O ring 43 and a slipper seal 44.
  • guide means of the present invention is composed of the center guide 38 and the concave portion 42.
  • a ring-shaped cover 45 is disposed on an outer peripheral portion of the thin plunger 40, and fixed to the cylinder 32 by bolts 46 to fix the liner 33 and define the amount of movement of the thin plunger 40.
  • An oil pressure supply chamber 47 is provided between the base end surface of the thin plunger 40 and the cylinder 32 by a stepped portion.
  • An oil feed passage 48 communicating with the oil pressure supply chamber 47 is formed.
  • a helical compression spring 49, as a pullback mechanism, is interposed between the thin plunger 40 and the cover 45.
  • the thin plunger 40 is normally located at a position of contact with the cylinder 32 by the urging force of the helical compression spring 49 (i.e., the position indicated by solid lines in FIG. 1).
  • an oil is fed from an oil pressure source (not shown) to the oil pressure supply chamber 47 via the oil feed passage 48, the thin plunger 40 can move rightward in FIG. 1 over a predetermined stroke S in opposition to the urging force of the helical compression spring 49.
  • oil supply to the oil pressure supply chamber 47 is stopped, the thin plunger 40 moves leftward in FIG. 1 by the stroke S under the urging force of the helical compression spring 49, and the oil is discharged from the oil pressure supply chamber 47.
  • the inner wall surface of the liner 33 and the outer wall surface of the thin plunger 40 which are slidable over each other, the outer wall surface of the center guide 38 and the inner wall surface of the concave portion 42 which are slidable over each other, and the outer wall surface of the replaceable liner 33 and the inner wall surface of the cylinder 32 which are slidable over each other are surface treated in consideration of durability, abrasion resistance and impact resistance.
  • the liner 33 can be replaced.
  • the thin plunger 40 has a front end portion to which a flange portion 51 of a support shaft 50 is attached by a support bracket 53 via a compression spring 52.
  • a liner 54 as an output portion, is connected to a front end portion of the support shaft 50 by a connecting member 55, and a cover 56 is attached to the liner 54.
  • the liner 54 has a curved back surface consistent with the front end surface of the thin plunger 40, and is pivotable in an amount corresponding to the gap between the liner 54 and the support shaft 50.
  • a ring-shaped greasing groove 57 is formed in the surface of the liner 54 for increased slidability.
  • the greasing groove 57 can be greased from a greasing source (not shown) through greasing passages 58, 59, 60, 61 formed in the cylinder 32, center guide 38, thin plunger 40 and liner 54.
  • a strip is fed from the entry side of the housing 11, and passed between the lower work roll 15 and the upper work roll 14 given a predetermined load by the screw down device 20 via the backup roll 18.
  • the strip is rolled to a predetermined thickness, delivered from the delivery side, and fed to a subsequent step.
  • an inward narrowing deformation amount occurs in the housing 11 in response to a screw down load.
  • a thrusting force is exerted on the housing 11 by actuating the hydraulic cylinders 21 to 28, whereby the deformation amount of the housing 11 is decreased.
  • the oil is supplied from the oil pressure source to the oil pressure supply chamber 47 via the oil feed passage 48.
  • the thin plunger 40 moves over the predetermined stroke S under a predetermined oil feed pressure in opposition to the urging force of the helical compression spring 49, thereby thrusting the upper work roll chock 12 via the liner 54.
  • the thin plunger 40 moves, with its outer peripheral surface being supported by the liner 33, and with the concave portion 42 at its based end portion being supported by the center guide 38.
  • its straight line stability is fully ensured, and the thin plunger 40 can move properly without sticking.
  • the liner 54 pivots following the upper work roll chock 12, or a reaction force against rolling acts on the thin plunger 40 via the upper work roll chock 12.
  • the thin plunger 40 has the concave portion 42 supported by the center guide 38.
  • the thin plunger 40 can reliably accept this reaction force and properly move.
  • the hydraulic cylinders 21 to 28 are mounted on the entry side and delivery side of the housing 11 so as to be opposed to the roll chocks 12, 13, 16, 17.
  • These hydraulic cylinders 21 to 28 are constituted in the following manner:
  • the thin plunger 40 is movably fitted into the cylinder 32 fixed to the housing 11 via the liner 33.
  • the concave portion 42 of the thin plunger 40 is movably fitted over the center guide 38 of the cylinder 32 to serve as guide means.
  • the liner 54 for thrusting each of the roll chocks 12, 13, 16, 17 is connected to the front end portion of the thin plunger 40.
  • the thin plunger 40 has the outer peripheral portion and the central portion movably supported by the cylinder 32 in the above manner.
  • the thin plunger 40 is excellent in straight line stability. Even if an axial load or a fluctuating load is imposed by the roll chocks 12, 13, 16, 17 during rolling, the thin plunger 40 does not stick, but properly works, and prevents mill vibrations occurring in the housing 11 or work rolls 14, 15. Consequently, the passage of the strip is improved to achieve high efficiency rolling, and a stable rolling state can be realized.
  • FIGS. 4 and 5 show sections of hydraulic cylinders mounted on rolling mills according to other embodiments of the present invention. Members having the same functions as described in the aforementioned embodiment are assigned the same numerals, and duplicate explanations are omitted.
  • a thin plunger 40 is fitted on the inner wall surface of a liner 33 of a cylinder 32 via a slipper seal 41.
  • a concave portion 42 of the thin plunger 40 is fitted over a center guide 38 via an O ring 43 and a slipper seal 44.
  • the thin plunger 40 is movable in the axial direction.
  • An oil pressure supply chamber 47 is provided between the base end surface of the thin plunger 40 and the cylinder 32, and an oil feed passage 48 communicates with the oil pressure supply chamber 47.
  • An oil pressure supply chamber 65 as a pullback mechanism, is provided among the thin plunger 40, a cover 45 and the liner 33, and an oil feed passage 66 communicates with the oil pressure supply chamber 65.
  • the oil feed passages 48, 66 are connected to an oil pressure source via selector valves (not shown).
  • the selector valves are operated to supply an oil from the oil pressure source to the oil pressure supply chamber 47 via the oil feed passage 48, and discharge the oil from the oil pressure supply chamber 65 via the oil feed passage 66.
  • the thin plunger 40 is moved rightward in FIG. 4, whereby a liner 54 can thrust the roll chock.
  • the selector valves are switched to supply the oil from the oil pressure source to the oil pressure supply chamber 65 via the oil feed passage 66, and discharge the oil from the oil pressure supply chamber 47 via the oil feed passage 48.
  • the thin plunger 40 is moved leftward in FIG. 4, whereby the liner 54 can be stopped from thrusting the roll chock.
  • the movement of the plunger 40 is performed only by the supply and discharge of the oil pressure.
  • the action of the plunger 40 namely, its action of thrusting the roll chock, can be carried out reliably.
  • a liner 72 is supported on a curved surface 71 of a housing 11 so as to be opposed to a roll chock 12 and be pivotable by a pivot mechanism (not shown).
  • a hydraulic cylinder 73 is mounted on the liner 72.
  • the cylinder 73 is formed at a predetermined position of the liner 72, and a concave portion 74 of a cylindrical shape is formed at the center of the cylinder 73.
  • a thin plunger 75 is disc-shaped, and is fitted on the inner wall surface of the cylinder 73 via a slipper seal 76.
  • a center guide 77 formed in a base end portion of the thin plunger 75 is fitted into the concave portion 74 via a slipper seal 78.
  • guide means of the present invention is composed of the concave portion 74 and the center guide 77.
  • a cover 79 is disposed on an outer peripheral portion of the thin plunger 75, and fixed to the liner 72 by a bolt 80 to define the stroke S of the thin plunger 75.
  • An oil pressure supply chamber 81 is provided between the base end surface of the thin plunger 75 and the liner 72, and an oil feed passage 82 communicates with the oil pressure supply chamber 81.
  • a helical compression spring 83 as a pullback mechanism, is interposed between the thin plunger 75 and the cover 79.
  • the thin plunger 75 has a front end portion to which a front end liner 84, as an output portion, is fixed by a bolt 85.
  • the thin plunger 75 can thrust the roll chock via the front end liner 84.
  • a greasing groove 86 of a cross shape is formed in the surface of the front end liner 84 for increased slidability.
  • the greasing groove 86 can be greased from a greasing source (not shown) through greasing passages 87, 88 formed in the thin plunger 75, front end liner 84, etc.
  • the thin plunger 75 moves over a predetermined stroke S under a predetermined oil feed pressure in opposition to the urging force of the helical compression spring 83, thereby thrusting the roll chock via the front end liner 84.
  • the thin plunger 75 moves, with its outer peripheral surface being supported by the cylinder 73, and with the center guide 77 being supported by the concave portion 74.
  • the liner 72 is pivotably supported by the housing 11, the cylinder 73 is formed in the liner 72, and the thin plunger 75 is movably fitted into the cylinder 73.
  • the center guide 77 of the thin plunger 75 is movably fitted into the concave portion 74 of the cylinder 73 to serve as guide means.
  • the front end liner 84 for thrusting the roll chock is fixed to the front end portion of the thin plunger 75.
  • the center guide 38 is formed as a separate member, and fixed to the cylinder 32 by the bolts 39.
  • the center guide 77 is formed integrally with the thin plunger 75.
  • the center guide may be a separate member or an integral member, which may be selected, as desired, according to the production cost or ease of assembly.
  • the position of formation of the center guide and the concave portion may be in the thin plunger or in the cylinder.
  • the guide means is the center guide and the concave portion.
  • a plurality of convex portions may be provided at positions other than the central position.
  • the rolling mill of the present invention is preferably used not only for rolling mills of ordinary shapes, but also for cross rolling mills and shift rolling mills.
  • the fluid pressure cylinder of the present invention is applied as the hydraulic cylinders 21 to 28 for thrusting the roll chocks in various rolling mills .
  • the fluid pressure cylinder may be provided at any place where its working force is great and its working stroke is short.
EP02015572A 2001-08-02 2002-07-12 Druckmittelzylinder und Walzwerk Withdrawn EP1281449A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001234661A JP2003048006A (ja) 2001-08-02 2001-08-02 流体圧シリンダ及び圧延機
JP2001234661 2001-08-02

Publications (1)

Publication Number Publication Date
EP1281449A2 true EP1281449A2 (de) 2003-02-05

Family

ID=19066229

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02015572A Withdrawn EP1281449A2 (de) 2001-08-02 2002-07-12 Druckmittelzylinder und Walzwerk

Country Status (8)

Country Link
US (1) US20030024292A1 (de)
EP (1) EP1281449A2 (de)
JP (1) JP2003048006A (de)
KR (1) KR20030013291A (de)
CN (1) CN1401444A (de)
BR (1) BR0202853A (de)
CA (1) CA2392101A1 (de)
TW (1) TW565476B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2510298C2 (ru) * 2012-04-20 2014-03-27 Общество С Ограниченной Ответственностью "Надежность Тяжелых Машин" Станина клети прокатного стана

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4310733B2 (ja) 2003-09-08 2009-08-12 株式会社ダイフク 摩擦駆動の台車式搬送装置
US7225657B2 (en) * 2004-05-05 2007-06-05 United States Steel Corporation Elimination of rolling mill chatter
DE102005042168A1 (de) * 2005-06-08 2006-12-14 Sms Demag Ag Vorrichtung zur Beaufschlagung der Führungsflächen von in den Ständerfenstern von Walzgerüsten geführten Lagereinbaustücken
DE102006046311A1 (de) 2006-09-29 2008-04-03 Xella Baustoffe Gmbh Verfahren und Bewehrungsmittel zur Herstellung bewehrter Poren- oder Schaumbetonkörper und Bewehrungshalterahmen zur Verwendung für ein derartiges Verfahren
US8091817B2 (en) * 2009-12-11 2012-01-10 Flsmidth A/S Milling device
CN102847717A (zh) * 2012-09-08 2013-01-02 中色科技股份有限公司 一种提高轧机辊系稳定运行的装置及其方法
KR101990994B1 (ko) * 2017-11-08 2019-06-20 주식회사 포스코 압연설비
CN112958629B (zh) * 2021-01-29 2023-01-13 嘉兴学院 一种有色金属压延成型设备

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3906767A (en) * 1974-05-31 1975-09-23 Mitsubishi Heavy Ind Ltd Hydraulic roll-gap control system
GB1559571A (en) * 1976-09-24 1980-01-23 Avon Ind Polymers Piston means for piston cylinder arrangements
DE3019947A1 (de) * 1980-05-24 1981-12-03 Fried. Krupp Gmbh, 4300 Essen Walzenanstellvorrichtung
JPS5987904A (ja) * 1982-11-12 1984-05-21 Mitsubishi Heavy Ind Ltd ワ−クロ−ルベンデイングシリンダ装置
FR2616089B1 (fr) * 1987-06-04 1994-04-29 Clecim Sa Dispositif de maintien axial d'un cylindre a enveloppe tournante
FI891868A (fi) * 1988-04-30 1989-10-31 Voith Gmbh J M Cylinder-kolv-enhet foer att foerskjuta en vals tvaers oever dess laengdaxell.
DE3827018A1 (de) * 1988-08-05 1990-02-08 Mannesmann Ag Vorrichtung zur axialfuehrung der walzen von walgeruesten zur herstellung von profilstahl
DE4010662C3 (de) * 1990-04-03 2001-07-05 Bwg Bergwerk Walzwerk Anstellvorrichtung zum Einstellen des Walzenabstandes in Walzgerüsten, insbesondere in Bandwalzgerüsten für Warm- oder Kaltwalzung
DE4033638C1 (de) * 1990-10-23 1992-02-13 Eduard Kuesters Maschinenfabrik Gmbh & Co Kg, 4150 Krefeld, De
US5299489A (en) * 1991-05-17 1994-04-05 Reo Hydraulic Pierce & Form Pressure cylinder with low tolerance fit capable of supporting large transverse loads
JP2920466B2 (ja) * 1993-12-28 1999-07-19 新日本製鐵株式会社 位置制御用油圧シリンダの検出器支持機構
JP4402264B2 (ja) * 1999-08-11 2010-01-20 三菱重工業株式会社 圧延機

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2510298C2 (ru) * 2012-04-20 2014-03-27 Общество С Ограниченной Ответственностью "Надежность Тяжелых Машин" Станина клети прокатного стана

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US20030024292A1 (en) 2003-02-06
JP2003048006A (ja) 2003-02-18
BR0202853A (pt) 2003-05-20
CA2392101A1 (en) 2003-02-02
CN1401444A (zh) 2003-03-12
TW565476B (en) 2003-12-11
KR20030013291A (ko) 2003-02-14

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