EP2554282B1 - Walzmaschine und walzverfahren für metallplatten - Google Patents

Walzmaschine und walzverfahren für metallplatten Download PDF

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Publication number
EP2554282B1
EP2554282B1 EP11762310.8A EP11762310A EP2554282B1 EP 2554282 B1 EP2554282 B1 EP 2554282B1 EP 11762310 A EP11762310 A EP 11762310A EP 2554282 B1 EP2554282 B1 EP 2554282B1
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EP
European Patent Office
Prior art keywords
rolling
roll
force
work roll
bending force
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.)
Not-in-force
Application number
EP11762310.8A
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English (en)
French (fr)
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EP2554282A4 (de
EP2554282A1 (de
Inventor
Shigeru Ogawa
Tsuyoshi Higo
Takashi Hisatsune
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Nippon Steel Corp
Original Assignee
Nippon Steel and Sumitomo Metal Corp
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Publication date
Application filed by Nippon Steel and Sumitomo Metal Corp filed Critical Nippon Steel and Sumitomo Metal Corp
Publication of EP2554282A1 publication Critical patent/EP2554282A1/de
Publication of EP2554282A4 publication Critical patent/EP2554282A4/de
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Publication of EP2554282B1 publication Critical patent/EP2554282B1/de
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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
    • 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
    • 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
    • B21B37/38—Control of flatness or profile during rolling of strip, sheets or plates using roll bending
    • 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

Definitions

  • the present invention relates to a rolling mill of a metal flat-rolled product which has a high response and can impart a powerful roll bending force.
  • a rolling mill which is suitable for a plate rolling mill or rough rolling mill for sheet hot rolling, can obtain the maximum gap between the upper and lower work rolls, and can impart a powerful roll bending force.
  • the present invention relates to a rolling method, which uses the above rolling mill, which has a high response and can provide a powerful crown/shape control function.
  • crown and the shape of the rolled plate become important indicators of quality.
  • Numerous art relating to crown/shape control have been disclosed.
  • the gap between the upper and lower work rolls has to be made larger than the thickness of the rolling material. For this reason, restrictions are imposed on the crown/shape control devices in the design of rolling mill facilities.
  • PLT 1 discloses a rolling method in plate rolling which rolls plate to a predetermined thickness by several passes wherein the method uses shape control devices constituted by work roll bending devices and uses the values of rolling results in a previous pass as the basis to control the roll bending force.
  • the type of the rolling mill which is disclosed in PLT 1 is a four-high rolling mill.
  • This rolling mill type is the structure which is shown in FIG. 14 .
  • the rolling mill of FIG. 14 to which decrease bending devices are arranged becomes the rolling mill which is shown in FIG. 10 .
  • the two rolling mills are basically the same in structure. That is, this is a type in which an upper work roll chock 3-1 is held by arm parts which are connected to an upper backup roll chock 4-1.
  • the arm parts have increase bending devices 6-1 and 6-2 of the upper work roll 1-1 built into them. By employing such a type, a large roll gap can be obtained.
  • the increase bending devices 6-3 and 6-4 of the lower work roll 1-2 are built into project blocks which connect to the rolling mill housing 9.
  • FIG. 11 there are rolling mills in which at both the upper and lower backup roll chocks 4-1 and 4-2 hold the work roll chocks 3-1 and 3-2.
  • an “increase bending device” means a hydraulic device which imparts a force to a work roll chock in a direction enlarging the roll gap.
  • An “increase bending device” is the general term for a device including an actuator comprised of a hydraulic cylinder.
  • an “increase bending device” unless otherwise stated, will indicate that actuator comprised of a hydraulic cylinder.
  • the force which is applied by the increase bending device to the work roll will be called the "increase bending force”.
  • a hydraulic device which gives a force to a work roll chock in a direction reducing the roll gap will be called a “decrease bending device” and the force which is applied to the work roll due to this will be referred to as the "decrease bending force”.
  • a “decrease bending device” is the general name for a device including the actuator comprised of a hydraulic cylinder.
  • a “decrease bending device” unless otherwise stated, will indicate that actuator comprised of a hydraulic cylinder.
  • PLT 2 discloses a rolling mill in which the increase bending devices 6-1 and 6-2 of the work rolls are built into the work roll chocks 3-1 and 3-2.
  • PLT 3 discloses a roll cross type of rolling mill. This rolling mill also, as shown in FIG. 12 , has the increase bending devices 6-1 and 6-2 built into the work roll chocks 3-1 and 3-2.
  • PLT 4 discloses a rolling mill which has a work roll shift function.
  • This rolling mill has increase bending devices 6-1 and 6-2 built into project blocks 5-1 and 5-2 which are formed integrally with the rolling mill housing. Note that, in the rolling mill which is disclosed in PLT 4, a plurality of hydraulic cylinders of the increase bending devices are arranged in the roll axial direction so that no biased load is applied at the time of shifting the work rolls.
  • FIG. 10 , FIG. 11 , FIG. 12 , and FIG. 13 show the case where there are decrease bending devices.
  • DE 36 01 239 A discloses a bending device for the axially displaceable working rolls of a four-high stand, in which a constructionally simple bending device for the axially displaceable working rolls of a four-high stand is seated in the blocks which are fixedly provided on both sides in the window of each roll housing and intended for the vertical and horizontal guide of the chocks (inserts) for the working rolls.
  • Patent Literatures cited above are:
  • the typical plate rolling mill such as disclosed in PLT 1 (rolling mill which is shown in FIG. 10 and FIG. 11 ) is designed having the ability to obtain a large roll gap as its highest priority. That is, arm parts which are connected to the upper backup roll chock 4-1 which is set and controlled in upper and lower positions by a reduction device 11 holds the upper work roll chock 3-1 in structure. Further, the arm parts, which are structurally restricted in size, have the increase bending devices 6-1 and 6-2 built into them, so building in large capacity hydraulic cylinders is difficult. For this reason, a powerful roll bending force cannot be imparted.
  • the roll deflection which is an indicator of the effect of roll bending, is inversely proportional to the cross-sectional secondary moment of the roll if the bending moment which is applied is the same. Therefore, the rolling bending effect of a work roll diameter of 1000 mm becomes as much as 60% inferior compared with a final rolling mill of a hot strip mill with a work roll diameter of 800 mm.
  • the rolling mill which is disclosed in each of PLT's 2 and 4 has the increase bending devices 6-1 and 6-2 built into the project blocks 5-1 and 5-2 which are connected to the rolling mill housing 9.
  • the hydraulic piping of the increase bending devices does not have to be detached and reattached at each roll changing operation. Therefore, this rolling mill can be provided with high response roll bending devices. For this reason, it is frequently used for final rolling mills of hot strip mills.
  • this rolling mill supports the offset force component which acts on the upper work roll 1-1 and other rolling direction forces by the contact surfaces of the work roll chock 3-1 and project block 5-2. For this reason, if operating a reduction device 11 to increase the roll gap, the center of rotation of the work roll will become outside of the contact surfaces and the work roll chock 3-1 will become unstable in posture. As a result, a large roll gap cannot be obtained. For this reason, this rolling mill is hardly ever employed in a plate rolling mill where a large roll gap is required.
  • the problem to be solved by the present invention is to provide a rolling mill which can obtain a large gap between upper and lower work rolls and which can impart a high response and powerful roll bending force.
  • the rolling mill according to the present invention supports the rolling direction force which is applied to the barrel of the upper work roll 1-1 by the contact surfaces between the upper work roll chock 3-1 and the housing window above the project block 5-2 in structure. For this reason, a large roll gap can be obtained and a powerful roll bending force can also be obtained.
  • FIG. 1 is a side view which shows one example of the structure of the rolling mill according to the present invention.
  • the rolling mill according to the present invention is a rolling mill which is provided with a pair of upper and lower work rolls 1-1 and 1-2 and a pair of upper and lower backup rolls 2-1 and 2-2 which support the same.
  • the rolling mill according to the present invention is a rolling mill which arranges upper increase bending devices 6-1 and 6-2 which apply increase bending force to the upper work roll 1-1 and lower increase bending devices 6-3 and 6-4 which apply increase bending force to the lower work roll 1-2 at project blocks 5-1 and 5-2 which project to the inside of the housing 9.
  • the rolling mill according to the present invention fundamentally reevaluates this to solve the problem in the conventional rolling mill which is shown in FIG. 13 . That is, it changes the positions of the project blocks 5-1 and 5-2, the shape of the upper work roll chock 3-1, etc. from the viewpoint of the structural design of the rolling mill, in particular from the viewpoint of obtaining a large roll gap.
  • the rolling mill according to the present invention solves the above problem.
  • the rolling mill according to the present invention arranges the project blocks 5-1 and 5-2 which project from the housing 9 in the inside direction at positions shifted to below the pass line. That is, unlike in the conventional rolling mill which is shown in FIG. 13 , the project blocks 5-1 and 5-2 are arranged vertically asymmetrically with respect to the pass line. Furthermore, the upper work roll chock 3-1 does not contact the project block 5-2 to support the rolling force, but contacts the housing window to support the rolling force.
  • the contact surfaces of the upper work roll chock 3-1 and the housing window 12 above the project block 5-2 are used to support the offset force component and other rolling direction force which acts on the upper work roll 1-1, that is, the rolling direction force which is applied from the rolled material 10, the upper backup roll 2-1, etc. to the barrel of the upper work roll 1-1.
  • the upper work roll chock 3-1 is constantly held stably in posture regardless of the roll gap.
  • a rolling mill which has upper and lower increase bending devices arranged at the project blocks is known.
  • the rolling mill according to the present invention fundamentally reevaluates the positions of the project blocks 5-1 and 5-2 and the shape of the upper work roll chock 3-1 so as to support the rolling direction force which is applied to the barrel of the upper work roll 1-1 by the contact surfaces between the upper work roll chock 3-1 and the housing window 12 above the project block 5-2 in structure, so a large roll gap can be obtained.
  • upper increase bending devices 6-1 and 6-2 which apply increase bending force to the upper work roll 1-1 and lower increase bending devices 6-3 and 6-4 which apply increase bending force to the lower work roll 1-2 are arranged at the project blocks 5-1 and 5-2 which project to the inside of the housing 9. For this reason, there is no need to detach and reattach the hydraulic piping of the increase bending devices with each work roll changing operation and high response increase bending devices can be employed. This is because it is possible to connect them through fixed hydraulic piping to respective hydraulic control valves, and servo valves for high response hydraulic control can be employed.
  • the rolling mill according to the present invention the rolling direction force which is applied to the barrel of the lower work roll 1-2 is supported by the contact surfaces between the lower work roll chock 3-2 and the project block 5-2.
  • the rolling mill according to the present invention which is shown in FIG. 1 increases the height of the part of the lower work roll chock 3-2 which is sandwiched between the project blocks 5-1 and 5-2.
  • the roll gap is mainly adjusted by making the upper work roll chock move up and down, so there is little up and down movement of the lower work roll chock. For this reason, there is no destabilization of the posture of the lower work roll as the roll gap becomes larger.
  • FIG. 2 is a cross-sectional plan view which shows an example of the arrangement of the upper and lower increase bending devices. That is, it is a cross-sectional view of the pass line heights of the project blocks 5-1 and 5-2.
  • the upper and lower increase bending devices are preferably arranged offset from each other in the cross-sectional plan view of the project blocks.
  • the upper increase bending devices 6-1 and 6-2 and the lower increase bending devices 6-3 and 6-4 are preferably arranged to a positional relationship where they are shifted in the axial direction of the work roll 1-2. By doing this, the upper and lower increase bending devices will not interfere with each other. It is possible to increase the strokes of the upper increase bending devices 6-1 and 6-2 and obtain a further larger roll gap.
  • the lower increase bending devices 6-3 and 6-4 are respectively comprised of two hydraulic cylinders at the entry side and the exit side.
  • similar effects can be obtained by using single hydraulic cylinders and arranging them at different positions in the axial direction of the work roll 1-2 so as not to interfere with the upper increase bending devices 6-1 and 6-2.
  • FIG. 3 is a cross-sectional plan view which shows an example of the arrangement of the upper and lower increase bending devices. That is, it is a cross-sectional view of the pass line height of the project blocks 5-1 and 5-2.
  • the upper increase bending devices 6-1 and 6-2a and the lower increase bending devices 6-3 and 6-4 may be arranged in a positional relationship shifted in the rolling direction. With this arrangement as well, the upper and lower increase bending devices do not interfere with each other. It is possible to increase the strokes of the upper increase bending devices 6-1 and 6-2 to obtain a further larger roll gap.
  • the structure of the rolling mill according to the present invention has been explained mainly from the viewpoint of one of the problems to be solved, that is, obtaining a large roll gap.
  • another problem that is, imparting a powerful roll bending force, can also be easily solved.
  • FIG. 10 and FIG. 11 are both rolling mills according to the prior art. Each rolling mill enables a large roll gap to be obtained.
  • project blocks 5-1 and 5-2 which project from the housing 9 of the rolling mill in the inside direction, are provided with large capacity/large stroke upper increase bending devices 6-1 and 6-2.
  • the rolling mill according to the present invention does not provide the upper backup roll chock 4-1 with arm parts like the rolling mills which are shown in FIG. 10 and FIG. 11 .
  • large capacity upper decrease bending devices 7-1 and 7-2 can be provided at positions of the upper backup roll chock 4-1 which do not interfere with the bearings of the upper backup roll. Due to this, the upper work roll 1-1 can be given a large decrease bending force.
  • the rolling mill according to the present invention which fundamentally reevaluates the positions of the project blocks 5-1 and 5-2 and the shape of the upper work roll chock 3-1 and is structured to support the rolling direction force which is applied to the barrel of the upper work roll 1-1 by the contact surfaces of the upper work roll chock 3-1 and the housing window 12, a large roll gap can be obtained and a powerful roll bending force can be imparted. Further, there is no need to detach and reattach hydraulic piping of the increase bending devices with each work roll changing operation. For this reason, it is possible to connect hydraulic control valves to the increase bending devices 6-1 to 6-4 through fixed hydraulic piping and possible to employ servo valves for high response hydraulic control. Therefore, it is possible to provide high response increase bending devices.
  • FIG. 4 is a side view which shows another example of the rolling mill according to the present invention.
  • the rolling mill which is shown in FIG. 4 has an upper roll system configured the same as in FIG. 1 , but has a lower roll system configured differently.
  • the rolling mill which is shown in FIG. 1 is provided at the lower backup roll chock 4-2 with lower decrease bending devices 7-3 and 7-4 which apply decrease bending force to the lower work roll.
  • the rolling mill which is shown in FIG. 4 provides the lower decrease bending devices 7-3 and 7-4 at the special project blocks 5-3 and 5-4 which are positioned below the project blocks 5-1 and 5-2.
  • the decrease bending force cannot be applied at the time of idling when no rolling load is being applied. For this reason, when applying a decrease bending force, it is necessary to quickly set the decrease bending force in the interval from the idling state where a roll balance is obtained to the start of rolling and further to quickly return to the roll balance state at the time of rolling end. Therefore, if changing the roll bending force by control by inferior response decrease bending devices, there is a possibility that the predetermined decrease bending force will not be applied at the tip and tail ends of the rolled material and the parts with defective shapes will become longer.
  • the rolling method according to present invention solves the above problem. That is, this is a rolling method which uses a rolling mill according to the present invention which arranges upper decrease bending devices 7-1 and 7-2 at the upper backup roll chock 4-1 and solves the above problems which can occur in that rolling mill.
  • the project blocks 5-1 and 5-2 which project from the housing 9 to the inside direction are provided with upper increase bending devices 6-1 and 6-2 in structure, so these can be made large capacity/large stroke upper increase bending devices 6-1 and 6-2. Further, it is not necessary to detach and reattach the hydraulic piping of the increase bending devices with each roll changing operation, so it is possible to employ fixed hydraulic piping and servo valves. Due to this, it is possible to provide high response increase bending devices.
  • the rolling method according to present invention changes the roll bending forces at the time of rolling start and at the time of rolling end by using the high response increase bending devices and compensates for the response of the decrease bending devices when making the decrease bending force act on the work rolls for the purpose of crown/shape control.
  • FIG. 5 is a view which shows one example of the flow of operation of the rolling method according to present invention. That is, it is a view which shows the flow of operation of a high response increase bending device and a somewhat lower response decrease bending device.
  • FIG. 6 shows the changes along with time in the roll bending force etc. for a single rolled material in this rolling method.
  • FIG. 6 shows, from the top, the changes along with time in the rolling load, output of an increase bending device, output of a decrease bending device, and the composite force of the same, that is, the work roll bending force. Below, this will be explained based on FIGS. 5 and 6 .
  • the set value F R of the rolling work roll bending force corresponding to the rolled material to be next rolled is calculated and output.
  • F R is calculated as a negative value, that is, a decrease bending force.
  • an increase bending force force in increase direction (direction opening up rolls)
  • a decrease bending force for in decrease direction (direction pressing upper and lower work rolls against each other)
  • both the increase bending force and decrease bending force are made to act and the composite force constituted by the increase side roll bending force corresponding to the roll balance force (F B ) acts on the work roll chock.
  • the increase bending device output is made I B (>0)
  • the decrease bending device output is made D B ( ⁇ 0)
  • I B +D B acts as the roll balance force F B (>0).
  • the roll balance force F B is determined as the force by which the work roll which is driven by the electric motor and the backup roll which is driven by that roll do not slip even at the time of the idling state. At this time, D B should be set by the minimum hydraulic pressure of an extent where the actuator of the decrease bending device does not end up separating from the work roll chock.
  • the decrease bending force is held at a constant value while the increase bending force is lowered and the composite force constituted by the predetermined in-rolling work roll bending force F R acts on the work roll chock.
  • the increase bending device output is changed from Is to I R .
  • the slow response decrease bending device output is left as D S while the fast response increase bending device can be controlled to quickly switch the composite force constituted by the work roll bending force from the roll balance force (F B (>0)) to the in-rolling work roll bending force (F R ( ⁇ 0)).
  • the time of rolling start (b) indicates the point of time of start of rolling. This may be detected for example by the method of finding the time when the load which is detected by a load cell for measurement of the rolling load of a rolling mill exceeds 30% of a predicted rolling load.
  • the roll bending force is returned to the state before the start of rolling by making a roll bending force which corresponds to the composite force constituted by the roll balance force (F B ) act on the work roll chock and ending the rolling.
  • the decrease bending device output is left as D S while the fast response increase bending device output is made to change from I R to I S .
  • the composite force constituted by the work roll bending force can be quickly switched from the in-rolling work roll bending force (F R ( ⁇ 0)) to the roll balance force (F B (>0)).
  • the time of rolling end (c) indicates the point of time of ending the rolling end. This may be detected for example by the method of finding the time when the load which is detected by a load cell for measurement of the rolling load of a rolling mill falls under 50% of an average value of measured rolling load.
  • the point of time after the elapse of for example 1 to 3 seconds from the time of rolling end (c) is made the timing of work completion (point d on time axis).
  • the increase bending device output is changed to I B and the decrease bending device output is changed to D B .
  • the composite force constituted by the work roll bending force is maintained at substantially the roll balance force (F B ).
  • the roll bending force is changed by using high response increase bending devices. For this reason, even if relatively low response decrease bending devices have to be provided, they are compensated for by the high response increase bending devices, so a high response and powerful crown/shape control function can be imparted.
  • control should be performed to make the in-rolling work roll bending force change, for example, in accordance with the measured value of the rolling load.
  • the rolling method according to present invention even when the rolled material entry side thickness or the rolled material temperature or other parameters fluctuate during rolling, a good crown/shape can be built in despite these external disturbances. Due to this, the product quality and yield can be greatly improved.
  • FIG. 7 is a view which shows the changes along with time in the rolling bending force etc. in the case of a low response of the decrease bending device (in particular, in the case of having hydraulic pressure characteristics whereby if the reaction force is withdrawn, the pressure ends up falling).
  • this shows the changes along with time in the roll bending force etc. which accompany a rolling operation on a single rolled material in accordance with the flow of operation of the increase bending device and the decrease bending device which is shown in FIG. 5 . That is, compared with the case of FIGS. 5 and 6 , the example of a case of a slow speed of response of the decrease bending device is shown.
  • FIG. 8 is a view which shows the flow of operation in the case where there is a fast response increase bending device and a slow response decrease bending device. Below, this will be explained based on the drawing.
  • a load cell which is set at the decrease bending device is used to constantly measure the decrease bending force or the hydraulic pressure inside of the hydraulic piping which leads to that device. This measured value is used as the basis to control the increase bending device. That is, the output of the increase bending device is controlled in accordance with the decrease bending force or hydraulic pressure of the decrease bending device so that the work roll bending force becomes the roll balance force F B before and after rolling and the work roll bending force becomes F R during rolling. Note that the rest of the control is similar to the rolling method which is shown in FIG. 5 .
  • the present invention can be utilized for rolling of steel plate, in particular for reverse rolling mills which require particularly large gaps etc.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)

Claims (6)

  1. Walzgerüst für ein Flachwalz-Metallerzeugnis (10), das ein Paar aus einer oberen und einer unteren Arbeitswalze (1-1, 1-2) und ein Paar aus einer oberen und einer unteren Stützwalze (2-1, 2-2) hat, die diese stützen, wobei das Walzgerüst für ein Flachwalz-Metallerzeugnis Hydraulikzylinder (6-1, 6-2, 6-3, 6-4) aufweist, die Biegungszunahmekraft auf die obere und untere Arbeitswalze ausüben und an Lagerblöcken (5-1, 5-2) angeordnet sind, die zum Inneren eines Walzgerüstständers (9) vorstehen,
    dadurch gekennzeichnet, dass
    die Lagerblöcke (5-1, 5-2) nach unterhalb einer Walzlinie verschoben und im Hinblick auf die Walzlinie vertikal asymmetrisch platziert sind,
    Kontaktflächen eines Lagerblocks und des unteren Arbeitswalzeneinbaustücks (3-2) so konfiguriert sind, dass sie Walzrichtungskraft abstützen, die auf einen unteren Arbeitswalzenballen ausgeübt wird, und
    Kontaktflächen eines Walzgerüst-Ständerfensters (12), das über den Lagerblöcken (5-1, 5-2) positioniert ist, und des oberen Arbeitswalzeneinbaustücks (3-1) so konfiguriert sind, dass sie Walzrichtungskraft abstützen, die auf einen oberen Arbeitswalzenballen ausgeübt wird.
  2. Walzgerüst für ein Flachwalz-Metallerzeugnis nach Anspruch 1, dadurch gekennzeichnet, dass ein Hydraulikzylinder, der Biegungszunahmekraft auf die obere Arbeitswalze ausübt, und ein Hydraulikzylinder, der Biegungszunahmekraft auf die untere Arbeitswalze ausübt, an unterschiedlichen Positionen in den Lagerblöcken mit Blick in Draufsicht angeordnet sind.
  3. Walzgerüst für ein Flachwalz-Metallerzeugnis nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass ein Hydraulikzylinder, der Biegungsabnahmekraft auf die obere Arbeitswalze ausübt, an einem oberen Stützwalzeneinbaustück der oberen Stützwalze angeordnet ist.
  4. Walzgerüst für ein Flachwalz-Metallerzeugnis nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass ein Hydraulikzylinder, der Biegungsabnahmekraft auf die untere Arbeitswalze ausübt, am unteren Stützwalzeneinbaustück oder an zweiten Lagerblöcken angeordnet ist, die unter den Lagerblöcken positioniert sind.
  5. Walzverfahren für ein Flachwalz-Metallerzeugnis, das ein Walzgerüst für ein Flachwalz-Metallerzeugnis nach Anspruch 3 verwendet, wobei das Walzverfahren für ein Flachwalz-Metallerzeugnis gekennzeichnet ist durch:
    vor Walzanfang erfolgendes Veranlassen, dass sowohl eine Biegungszunahmekraft als auch eine Biegungsabnahmekraft wirken, sowie Veranlassen, dass als zusammengesetzte Kraft eine Walzenbiegekraft in Entsprechung zu einer Walzenausbalancierkraft auf Arbeitswalzeneinbaustücke wirkt;
    anschließend bei Walzbeginn erfolgendes Fortsetzen von Regelung zum Halten der Biegungsabnahmekraft auf der vorbestimmten Biegungsabnahmekraft beim Walzen, während bewirkt wird, dass sich die Biegungszunahmekraft ändert, und bewirkt wird, dass die vorbestimmte Arbeitswalzenbiegekraft beim Walzen auf die Arbeitswalzeneinbaustücke als die zusammengesetzte Kraft wirkt;
    während des Walzens erfolgendes Durchführen des Walzens, so dass die vorbestimmte Arbeitswalzenbiegekraft beim Walzen beibehalten wird; und
    danach bei Walzende erfolgendes Bewirken, dass sich die Biegungszunahmekraft ändert, Bewirken, dass eine Walzenbiegekraft, die der Walzenausbalancierkraft entspricht, auf die Arbeitswalzeneinbaustücke als zusammengesetzte Kraft mit der Biegungsabnahmekraft wirkt, und Beenden des Walzens des Flachwalz-Metallerzeugnisses in diesem Zustand.
  6. Walzverfahren für ein Flachwalz-Metallerzeugnis nach Anspruch 5, gekennzeichnet durch Messen eines Hydraulikdrucks innerhalb eines Hydraulikzylinders, der die Biegungsabnahmekraft erzeugt, oder innerhalb einer Hydraulikleitung, die zum Hydraulikzylinder führt, und durch Verwenden des Messwerts als Grundlage, um die Biegungszunahmekraft so zu regeln, dass eine Walzenbiegekraft, die auf die Arbeitswalzeneinbaustücke als zusammengesetzte Kraft wirkt, einen vorbestimmten Wert annimmt.
EP11762310.8A 2010-03-31 2011-01-12 Walzmaschine und walzverfahren für metallplatten Not-in-force EP2554282B1 (de)

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KR101392078B1 (ko) 2011-03-24 2014-05-07 신닛테츠스미킨 카부시키카이샤 금속 판재의 압연기 및 압연 방법
JP5533754B2 (ja) * 2011-03-25 2014-06-25 新日鐵住金株式会社 金属板材のタンデム圧延設備及び熱間圧延方法
CN104923564B (zh) * 2014-03-21 2017-02-22 宝山钢铁股份有限公司 可避免工作辊窜动过程中轧辊脱出误报警的方法
JP6992032B2 (ja) * 2019-10-25 2022-01-13 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ株式会社 圧延機
EP3981522B1 (de) * 2019-10-25 2024-05-01 Primetals Technologies Japan, Ltd. Walzwerk

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US3864955A (en) * 1973-12-04 1975-02-11 Blaw Knox Foundry Mill Machine Rolling mill stand
JPS5942106A (ja) * 1982-09-01 1984-03-08 Hitachi Ltd 圧延機
DE3601239A1 (de) * 1986-01-17 1987-07-23 Schloemann Siemag Ag Biegevorrichtung fuer die axial verschiebbaren arbeitswalzen eines vierwalzen-walzgeruestes
JPS62142403U (de) * 1986-02-28 1987-09-08
JPH0749124B2 (ja) * 1986-03-20 1995-05-31 株式会社日立製作所 ロールシフト式圧延機
DE3628733A1 (de) * 1986-08-23 1988-02-25 Schloemann Siemag Ag Vorrichtung zum axialen anstellen der walzen von walzgeruesten zur herstellung von profilstahl
JPS63199006A (ja) * 1987-02-12 1988-08-17 Nippon Steel Corp 圧延機のワークロールベンディング方法
JPH02280910A (ja) * 1989-04-20 1990-11-16 Kawasaki Steel Corp 圧延機
JPH084812B2 (ja) 1990-06-15 1996-01-24 株式会社日立製作所 圧延機
JPH0687011A (ja) 1992-09-09 1994-03-29 Kawasaki Steel Corp 厚板の圧延方法
JP3040037B2 (ja) 1992-12-28 2000-05-08 株式会社日立製作所 圧延方法及び多段圧延機
JPH08215730A (ja) * 1995-02-21 1996-08-27 Nippon Steel Corp 板圧延機ロールベンディング装置及び板圧延方法
JP3879239B2 (ja) * 1998-03-24 2007-02-07 Ｊｆｅスチール株式会社 板クラウン制御方法

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TW201143922A (en) 2011-12-16
CN102821881B (zh) 2014-08-13
KR20120120476A (ko) 2012-11-01
KR101300236B1 (ko) 2013-08-26
WO2011122069A1 (ja) 2011-10-06
TWI430854B (zh) 2014-03-21
CN102821881A (zh) 2012-12-12
EP2554282A1 (de) 2013-02-06

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