EP0043869B1 - Walze für Walzwerk - Google Patents

Walze für Walzwerk Download PDF

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Publication number
EP0043869B1
EP0043869B1 EP80106377A EP80106377A EP0043869B1 EP 0043869 B1 EP0043869 B1 EP 0043869B1 EP 80106377 A EP80106377 A EP 80106377A EP 80106377 A EP80106377 A EP 80106377A EP 0043869 B1 EP0043869 B1 EP 0043869B1
Authority
EP
European Patent Office
Prior art keywords
roll
rolls
end portion
axial end
axial
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
Application number
EP80106377A
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English (en)
French (fr)
Other versions
EP0043869A3 (en
EP0043869B2 (de
EP0043869A2 (de
Inventor
Toshiyuki Kajiwara
Hidetoshi Nishi
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.)
Hitachi Ltd
Original Assignee
Hitachi 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
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Application filed by Hitachi Ltd filed Critical Hitachi Ltd
Priority to AT80106377T priority Critical patent/ATE14849T1/de
Publication of EP0043869A2 publication Critical patent/EP0043869A2/de
Publication of EP0043869A3 publication Critical patent/EP0043869A3/en
Publication of EP0043869B1 publication Critical patent/EP0043869B1/de
Application granted granted Critical
Publication of EP0043869B2 publication Critical patent/EP0043869B2/de
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
    • B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of 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
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/18—Adjusting or positioning rolls by moving rolls axially
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/42—Control of flatness or profile during rolling of strip, sheets or plates using a combination of roll bending and axial shifting of the rolls
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/021—Rolls for sheets or strips
    • B21B2027/022—Rolls having tapered ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/02—Roll bending; vertical bending of rolls
    • B21B2269/08—Back-up roll bending
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/12—Axial shifting the rolls
    • B21B2269/16—Intermediate rolls

Definitions

  • the present invention relates to a rolling mill comprising an upper and a lower work roll and at least one axially displaceable roll arranged at one side of the work rolls in such a manner that its axis substantially coincides with the plane of the axis of the work rolls, said displaceable roll being shiftable in the axial direction in accordance with the width of the rolled sheet and has one axial end portion of arcuate profile the diameter of which is gradually decreased toward the axial outer end.
  • this rolling mill In this rolling mill, the length of contact between cooperating rolls is changed by the axial displacement of the intermediate rolls to permit the control of the deflection of the work roll.
  • This rolling mill therefore, can remarkably improve the quality of control of the shape of the rolled product, thanks to the combination of the axial displacement of the intermediate rolls and the . operation of the work roll bender.
  • this rolling mill offers various additional advantages such as improvements in efficiency of the rolling equipment as a whole, rate of operation of the rolling mill and enhanced yield of the product, as well as saving of labour and energy.
  • rolls are arranged in an asymmetric manner with respect to the central axis of the rolling mill, so that an asymmetric axial load distribution is formed between the axially displaceable rolls and the cooperating rolls contacting the latter.
  • the greatest load is produced at each axial end portion of the axially displaceable rolls.
  • the axial end portions of the axially displaceable roll suffer double disadvantages in connection with the load as compared with the roll of the conventional rolling mill, resulting in a shortened life of the roll and/or generation of spalling.
  • the rolls of rolling mills are usually made of forged steel or cast steel. It is, therefore, extremely difficult to overcome the above-described problems by drastically enhancing the roll strength. The use of expensive hard materials, needless to say, uneconomically raises the cost of the roll.
  • the rolling mill of the kind described inherently has a superior shape controllability.
  • the present inventors have made proposals, on an assumption to provide the axial end portion of the axially displaceable roll with an arcuate profile, to represent the radius of curvature of the arcuate profile by a value of no dimension in relation to the roll diameter.
  • This proposal provides a solution to a problem concerning the determination of the starting point of the axial end portion of the roll, i.e. the junction between the cylindrical roll body portion and the arcuate axial end portion.
  • the rolling mill of the type described permits good rolling for varying rolling load and rolling width. In fact, the rolling can be satisfactorily performed even at such a high reduction ratio of about 50%. In the rolling operation at such a high reduction ratio, the amount of flattening deformation between the rolls is innegligibly large, and the above-mentioned problems cannot be obviated solely by adopting arcuate profile of the axial end portions of displaceable roll.
  • Fig. 6 to 8 a construction according to the preamble of claim 1, wherein the reduced radius portion in the form of parabolic or arcuate profile portion is formed in the barrel end portion of axially displaceable rolls which is installed as an intermediate roll of 6-high rolling mill.
  • the work roll diameter is less than 15% of the roll barrel length and thus it is insufficient in its rigidity as a work roll.
  • the parabolic profile portion of axially displaceable roll is merely disclosed as a technique for preventing the roll from being scored owing to the fact that the end portion of intermediate roll changes abruptly from a cylindrical portion to a tapered portion by means of regulating the profile of axially displaceable roll so as to correspond with the deflection amount of work roll.
  • a back-up or work roll for a 4-high-mill having end reliefs on both end portions, which reduce the roll end spalling and increase the range of roll contour control by bending.
  • the end reliefs of the roll comprise two symmetrically located smoothly curving exponential functions extending from the center line of the roll barrel to the two roll ends or from two locations intermediate tne ends of the roll and the roll barrel center line to the ends of the roll. All rolls of this rolling mill are fixed in the axial direction so that the problems discussed above do not occur.
  • the generation of surface flaw or score in the contacting roll should be eliminated, even when conventional less-expensive material such as forged steel, cast steel or the like is used as the material of the roll.
  • the solution of this object according to the invention is characterized in that the reduction Ye in radius of said axial end portion within the range x, of 100 mm as measured from the starting point S of said axial end portion toward said axial end is at least 0,3 mm and that the diameter of the work rolls is at least 15% of the roll barrel length.
  • the end portion of the displaceable roll is suitably located in relation to the widthwise end of the rolled material to perform a good shape control.
  • the boundary between the contacting region and non-contacting region of the displaceable roll with the adjacent roll is moved due to a Hertz flattening of the rolls when the rolling load is actually applied.
  • each displaceable roll has an axial end portion which is shaped in such a manner that a diameter gradually reduces toward the axial outer extremity and that the reduction in radius in each axial end portion within the axial region of 100 mm as measured from the starting point of the axial end portion is at least 0.3 mm.
  • Figs. 1 and 2 show a six high mill embodying the invention having axially displaceable rolls the axial end portions of which are shaped and sized in accordance with the invention. More specifically, Fig. 1 is a sectional view of the rolling mill, while Fig. 2 is a side elevational view.
  • Upper and lower work rolls 2, 3 for rolling the material 1 to be rolled in direct contact with the latter are supported by metal chocks 5, 6 held in the roll housing 4 at their both ends.
  • the metal chocks 5, 6 in turn are carried by the inside of the left and right projections 7, 8 provided on the roll housing 4 for free vertical adjustment.
  • the projections 7, 8 incorporate hydraulic rams 9, 10 for effecting bending of the upper and lower work rolls.
  • Upper and lower intermediate rolls 11, 12 arranged in pair and contacting the work rolls 2, 3, respectively, are disposed such that their axes are substantially in the same plane as those of the upper and lower work rolls 2, 3, and are supported at their both ends by metal chocks 13, 14.
  • Each intermediate roll has an axial end portion having an arcuate profile and of a diameter gradually decreasing toward the axial outer extremity. More specifically, the intermediate rolls are arranged such that their arcuate axial end portions are located at opposite sides of the rolling mill. In other words, the arcuate axial end portion of one intermediate roll is located at left side of the path of the rolled material, while the arcuate axial end portion of the other intermediate roll is located at the right side of the same.
  • Upper and lower backup rolls 15, 16 are arranged in a pair, in contact with the upper side of the upper intermediate roll 11 and the lower side of the lower intermediate roll 12, respectively, such that the axes of these backup rolls are in the same plane as the axes of the intermediate and work rolls.
  • These backup rolls 15, 16 are supported at their both ends by metal chocks 17, 18 provided in the roll housing 4.
  • a hydraulic ram 19 for effecting the roll reduction is connected to the lower side of the metal chock 18 and is received by a cylinder 20.
  • the metal chocks 13, 14 for the intermediate rolls are received by recesses 21, 22 of the metal chocks 17, 18 for backup rolls, so as to permit the intermediate rolls 11, 12 to be displaced in the upward and downward direction, as well as in the axial direction.
  • the intermediate rolls 11, 12 are coupled, through shafts 23, 24 connected to their one ends, with means (not shown) for axially displacing the intermediate rolls in opposite axial directions.
  • the work rolls 2, 3 are drivingly coupled with driving means (not shown) through respective universal joints 25, 26 and drive shafts 27, 28.
  • each intermediate roll is axially adjusted in accordance with the width of the sheet being rolled in such a manner that, for example, the starting point of the axial end portion of decreasing diameter is located to a position corresponding to the widthwise end of the rolled sheet or its vicinity.
  • the undesirable deflection of the work roll due to the load imposed by the backup roll contacting therewith, is avoided to prevent excessive rolling of the rolled sheet at both axial ends of the work roll.
  • the roll bending effect is well performed by the hydraulic ram for bending, because each work roll is freed at its one axial end from contact with the backup roll.
  • Fig. 3 is an enlarged view of the axial end portion of the intermediate roll, in which x,, R and Ye represent, respectively, the axial length, radius of curvature and radius reduction (relief) of the axial end portion of the intermediate roll. Also, the diameter of the cylindrical body portion and the point at which the axial end portion starts are designated with D and S, respectively.
  • the direction of roll axis is represented by x-axis, while the upward and downward direction as viewed in this Figure is represented by y-axis, with the crossing point of the vertical line passing the starting point S and the horizontal plane containing the intermediate roll surface constituting the origin of the coordinate.
  • Figs. 4A to 4C show the positional relationship of rolls. More specifically, Fig. 4A shows the state in which no rolling load is imposed, Fig. 4B shows the state in which the roll end portion is in contact with the cooperating roll over the entire axial length thereof due to a rolling load imposed thereon and Fig. 4C shows the state in which the rolling load is imposed but the axial end portion makes contact with the cooperating roll only at a part of axial length thereof.
  • Fig. 5 shows the theoretically obtained relationship between the amount 6 of Hertz flattening generated between two rolls 29, 30 and the line load p (load per unit axial length of roll) imposed on the roll. This relationship is theoretically defined by the following equation. and where,
  • the Hertz flattening amount can be expressed by the following equation, if the sum (d 1 +d 2 ) of diameters of two rolls 29, 30 fall within the practical range.
  • the roll line load adopted in actual rolling mills usually falls within the following ranges:
  • the amount of Hertz flattening 6 is calculated to be 0.06 to 0.15 mm and 0.24 to 0.3 mm for the rolling mills belonging to the categories (a) and (b). Therefore, in order to ensure that the contact between the axial end portion of the displaceable roll and the cooperating roll takes place only over a portion of the axial end portion of the displaceable roll by providing the relief amount y e in only one of these rolls, the relief amount Ve should be at least 0.3 mm.
  • Another factor which influences the roll relief amount Ye is an increase in the length of contact region between the rolls owing to the deflection of rolls.
  • Fig. 7 shows a relationship between the rolled sheet width and the minimum diameter of work roll as obtained through a theoretical calculation on an assumption that the diameters of the backup roll and the intermediate roll are 1400 mm and 650 mm, respectively, and that the roll barrel length of the intermediate roll is 1420 mm. It is necessary that the work roll diameter D' has to be determined in relation to the rolled sheet width B to satisfy the relationship expressed by D'?0.2B. This condition is generally met by practical sizes of rolls. This relationship expresses the limit for avoiding the so-called composite elongation of the rolled material. In other words, this relation determines the threshold value for avoiding an abrupt deflection of the cooperating roll at a portion of the latter where the support by the displaceable roll is lost due to the axial displacement of the latter.
  • the rolls having roll barrel length 100 to 150 mm greater than the rolled sheet width are employed.
  • the minimum required diameter of the work roll is 160 mm and the roll barrel length is selected to be 900 to 950 mm.
  • the ratio of work roll diameter to the roll barrel length is 17 to 18%. Since the invention is applied to the rolling mill having work roll of a high flexural rigidity and the ratio of diameter to roll barrel length of work roll exceeding at least 15%, each work roll can be supported by only one roll which is, in the arrangement shown in Fig. 1, the intermediate roll which is disposed at each of upper and lower sides of the pair of work rolls.
  • the diameter of the cooperating roll is selected to be greater than the above-mentioned minimum limit or threshold value, it is not necessary to take into consideration the expansion of the contact region attributable to the abrupt deflection of the cooperating roll.
  • the amount of relief at the axial extremity or edge of the axially displaceable roll is at least 0.3 mm in radius.
  • the axial end portion has an arcuate profile of a radius of curvature of at least 200 mm, more preferably between 300 and 4000 mm to gradually decrease the roll diameter at such an axial end portion.
  • the axial displacement of the boundary between the contacting region and non-contacting region is preferably smaller than 10 mm.
  • a discussion will be made hereinunder as to the condition for maintaining the axial displacement within the range below the above-specified limit value.
  • the axial displacement X is 94.7 mm.
  • it is required to provide a relief amount Ye in axial end portion of at least 0.3 mm in radius within the region of 100 mm as measured from the starting point of the axial end portion toward the axial extremity or edge of the displaceable roll.
  • the boundary between the contacting and non-contacting regions exist between the starting point S of the axial end portion and the axial extremity or edge of the displaceable roll. The roll line load is decreased as such boundary is shifted toward the axial extremity.
  • the axial outer part of the axial end portion have a radius R of curvature smaller than that at the starting point of the axial end portion or to form such an axial outer part by a straight line of a large gradient. By so doing, it is possible to obtain the smaller length between the starting point S of the axial end portion and the point at which the radius reduction of 0.3 mm is achieved.
  • the arcuate axial end portion of the displaceable roll has a radius of curvature between 300 and 4000 mm.
  • the length between the starting point S of the axial end portion of the displaceable roll and the point at which the radius reduction of 0.3 mm or greater is reached is selected to be smaller than 100 mm.
  • Figs. 8 and 9 show different forms of the axial end portion of the displaceable roll. More specifically, in the arrangement shown in Fig. 8, the part of the axial end portion between the starting point and the point at which the relief amount of 0.5 mm is achieved has a radius of curvature of 5000 mmR and the part of the axial end portion beyond the above-mentioned point is formed with a radius of curvature of 500 mmR, the parts of 500 mmR and 5000 mmR being connected smoothly.
  • Fig. 9 shows the form of the axial end portion in which the axial outer part of the axial end portion is relieved by a straight line.
  • the forms of roll end portion as shown in Figs. 8 and 9 offer an advantage that the axial length between the starting point of the axial end portion and the axial extremity or edge of the displaceable roll is diminished to shorten the time required for grinding the axial end portion of the displaceable roll, which is usually troublesome and time consuming.
  • it is possible to obtain the large relief amount in radius with a small axial length of the axial end portion e.g. an amount of Hertz flattening of 1 mm or so generated in the worst case such as a rolling accident.
  • the invention has been described specifically through a six high mill having two intermediate rolls displaceable in opposite axial directions and disposed between the upper work roll and upper backup roll and between the lower work roll and lower backup roll, this is not exclusive and the invention is applicable to a four high mill as shown in Fig. 11 in which backup rolls are axially displaceable, a multi-stage mill as shown in Fig. 12 having two intermediate rolls axially displaceable in opposite directions and disposed between the upper work roll and upper backup roll and various other types of rolling mill.
  • the invention can be applied also to a rolling mill incorporating rolls having a crown over their entire axial length.
  • the point at which the curvature of the crown or the taper is abruptly changed is considered as being the starting point of the axial end portion of roll.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)
  • Metal Rolling (AREA)

Claims (7)

1. Walzgerüst mit einer oberen und einer unteren Arbeitswalze (2, 3) sowie wenigstens einer axialverschiebbaren Walze (11; 12), die auf einer Seite der Arbeitswalzen (2, 3) derart angeordnet ist, daß ihre Achse im wesentlichen mit der Ebene der Achse der Arbeitswalzen (2, 3) zusammenfällt, wobei die verschiebbare Walze in Axialrichtung nach Maßgabe der Breite des Walzblechs verschiebbar ist und einen axialen Endabschnitt mit gekrümmtem Profil aufweist, dessen Durchmesser zum axial äußeren Ende hin allmählich abnimmt, dadurch gekennzeichnet, daß die Radiusverkleinerung Ye des axialen Endabschnitts innerhalb des Bereichs x. von 100 mm, gemessen vom Ausgangspunkt S des axialen Endabschnitts zum axialen Ende hin, wenigstens 0,3 mm beträgt und daß der Durchmesser der Arbeitswalzen wenigstens 15% der Walzenballenlänge beträgt.
2. Walzgerüst nach Anspruch 1, dadurch gekennzeichnet, daß die allmähliche Radiusverkleinerung des axialen Endabschnitts an dem Ausgangspunkt S mit einem Krümmungsradius R von 200 mm oder mehr beginnt.
3. Walzgerüst nach Anspruch 2, dadurch gekennzeichnet, daß der Krümmungsradius R zwischen 300 mm und 4000 mm liegt.
4. Walzgerüst nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß ein Paar Zwischenwalzen (11, 12), die an der Ober- und der Unterseite des Arbeitswalzenpaars (2, 3) in Kontakt mit diesen angeordnet sind, in Axialrichtungen nach Maßgabe der Breite des Walzblechs (1) verschiebbar sind und jede den Endabschnitt mit verkleinertem Durchmesser an einem Ende aufweist, daß an der Ober- und der Unterseite der Zwischenwalzen (11, 12) Stützwalzen (15, 16) in Kontakt mit den Zwischenwalzen angeordnet sind, und daß Biegeeinrichtungen (9, 10) eine Biegekraft auf die Arbeitswalzen (2, 3) ausüben.
5. Walzgerüst nach einem der Ansprüche 1-3, dadurch gekennzeichnet, daß ein Paar Stützwalzen (15, 16), die an der Ober- und der Unterseite der Arbeitswalzen (2, 3) angeordnet sind, in Axialrichtung nach Maßgabe der Breite des Walzblechs (1) verschiebbar sind, wobei jede Stützwalze einen axialen Entabschnitt mit allmählich abnehmendem Durchmesser aufweist, und daß Einrichtungen (9, 10) vorgesehen sind, die die Arbeitswalzen (2, 3) mit einer Walzenbiegekraft beaufschlagen.
6. Walzgerüst nach einem der Ansprüche 1-5, dadurch gekennzeichnet, daß der Endabschnitt der verschiebbaren Walzen (11, 12) mehrere Krümmungsprofile aufweist, deren jedes einen Krümmungsradius von mehr als 200 mm hat.
7. Walzgerüst nach einem der Ansprüche 1-5, dadurch gekennzeichnet, daß das Profil des Endabschnitts der verschiebbaren Walze (11, 12) eine Kombination aus einem an der Ausgangslinie S beginnenden Profilabschnitt mit einem Krümmungsradius von mehr als 200 mm und einem konischen Profilabschnitt ist.
EP80106377A 1980-07-07 1980-10-20 Walze für Walzwerk Expired - Lifetime EP0043869B2 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80106377T ATE14849T1 (de) 1980-07-07 1980-10-20 Walze fuer walzwerk.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP55093195A JPS6018243B2 (ja) 1980-07-07 1980-07-07 圧延ロ−ル
JP93195/80 1980-07-07

Publications (4)

Publication Number Publication Date
EP0043869A2 EP0043869A2 (de) 1982-01-20
EP0043869A3 EP0043869A3 (en) 1982-04-28
EP0043869B1 true EP0043869B1 (de) 1985-08-14
EP0043869B2 EP0043869B2 (de) 1990-11-07

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ID=14075792

Family Applications (1)

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EP80106377A Expired - Lifetime EP0043869B2 (de) 1980-07-07 1980-10-20 Walze für Walzwerk

Country Status (7)

Country Link
EP (1) EP0043869B2 (de)
JP (1) JPS6018243B2 (de)
AT (1) ATE14849T1 (de)
AU (1) AU526637B2 (de)
CA (1) CA1153586A (de)
DE (1) DE3070984D1 (de)
DK (1) DK159593C (de)

Families Citing this family (14)

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Publication number Priority date Publication date Assignee Title
JPS5956905A (ja) * 1982-09-28 1984-04-02 Kawasaki Steel Corp 調質圧延用６段圧延機
JPS60158062U (ja) * 1983-11-28 1985-10-21 三菱重工業株式会社 耐熱材料でコ−テイングしたピストンリング
JPS60146508U (ja) * 1984-03-13 1985-09-28 石川島播磨重工業株式会社 圧延機のロ−ル研削装置
JPS60188853U (ja) * 1984-05-28 1985-12-14 株式会社　リケン ピストンリング
JPS619109U (ja) * 1984-06-22 1986-01-20 川崎製鉄株式会社 多段圧延装置
JPS61144202A (ja) * 1984-12-19 1986-07-01 Kawasaki Steel Corp 板材の形状制御圧延方法および圧延機
DE3624241C2 (de) * 1986-07-18 1996-07-11 Schloemann Siemag Ag Verfahren zum Betrieb eines Walzwerkes zur Herstellung eines Walzbandes
JPH0396465U (de) * 1990-01-22 1991-10-02
US5174144A (en) * 1990-04-13 1992-12-29 Hitachi, Ltd. 4-high rolling mill
CA2087156C (en) * 1991-05-16 2000-12-26 Toshiki Hiruta Six high rolling mill
US5319430A (en) * 1993-01-04 1994-06-07 Xerox Corporation Fuser mechanism having crowned rolls
DE10037004B4 (de) * 2000-07-29 2004-01-15 Sms Demag Ag Walzgerüst für bandkantenorientiertes Verschieben der Zwischenwalzen in einem 6-Walzen-Gerüst
JP7331874B2 (ja) * 2021-01-29 2023-08-23 Ｊｆｅスチール株式会社 調質圧延機のバックアップロール、調質圧延機および調質圧延方法
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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Publication number Priority date Publication date Assignee Title
GB1351074A (en) * 1971-02-15 1974-04-24 Hitachi Ltd Rolling mills
US3733878A (en) * 1971-10-20 1973-05-22 Aluminum Co Of America Roll end relief for rolling mills
JPS517635B2 (de) * 1971-12-10 1976-03-09
DE2322046C3 (de) * 1973-05-02 1979-11-22 Hoechst Ag, 6000 Frankfurt Verfahren zum Herstellen von Druckformen
JPS5316784A (en) * 1976-07-31 1978-02-16 Matsushita Electric Works Ltd Preparation of thermosetting resin decorative laminates
IN150120B (de) * 1978-05-19 1982-07-24 Sendzimir Inc T
JPS5522420A (en) * 1978-08-03 1980-02-18 Nippon Steel Corp Six-stage roll
DE2835514C2 (de) * 1978-08-12 1982-12-02 Sundwiger Eisenhütte Maschinenfabrik Grah & Co, 5870 Hemer Vorrichtung zum axialen Verschieben von konischen Zwischenwalzen in einem Mehrrollen-Walzgerüst

Also Published As

Publication number Publication date
JPS6018243B2 (ja) 1985-05-09
AU526637B2 (en) 1983-01-20
CA1153586A (en) 1983-09-13
JPS5717309A (en) 1982-01-29
DE3070984D1 (en) 1985-09-19
DK159593B (da) 1990-11-05
EP0043869A3 (en) 1982-04-28
DK460680A (da) 1982-01-08
DK159593C (da) 1991-04-15
EP0043869B2 (de) 1990-11-07
ATE14849T1 (de) 1985-08-15
EP0043869A2 (de) 1982-01-20
AU6384580A (en) 1982-01-14

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