EP2626149B1 - Device for rolling metal sheet material and method for rolling metal sheet material - Google Patents

Device for rolling metal sheet material and method for rolling metal sheet material Download PDF

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Publication number
EP2626149B1
EP2626149B1 EP20120761152 EP12761152A EP2626149B1 EP 2626149 B1 EP2626149 B1 EP 2626149B1 EP 20120761152 EP20120761152 EP 20120761152 EP 12761152 A EP12761152 A EP 12761152A EP 2626149 B1 EP2626149 B1 EP 2626149B1
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EP
European Patent Office
Prior art keywords
roll
rolling
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
EP20120761152
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2626149A1 (en
EP2626149A4 (en
Inventor
Taisuke Iwaki
Yasuhiro Nishiyama
Kunihiko Wakatsuki
Tsuyoshi Higo
Shigeru Ogawa
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.)
Nippon Steel Corp
Original Assignee
Nippon Steel and Sumitomo Metal Corp
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 Nippon Steel and Sumitomo Metal Corp filed Critical Nippon Steel and Sumitomo Metal Corp
Publication of EP2626149A1 publication Critical patent/EP2626149A1/en
Publication of EP2626149A4 publication Critical patent/EP2626149A4/en
Application granted granted Critical
Publication of EP2626149B1 publication Critical patent/EP2626149B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • 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
    • 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
    • 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
    • B21B13/14—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
    • 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
    • B21B2271/00—Mill stand parameters
    • B21B2271/02—Roll gap, screw-down position, draft position
    • 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
    • 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
    • B21B31/203—Balancing rolls

Definitions

  • the present invention relates to a device for rolling a metal sheet material and a method for rolling a metal sheet material.
  • a device in accordance with the preamble of claim 1 is e.g. known from JP-H 0452014 .
  • the present invention relates to a rolling device suitable for thick-plate rolling devices, or roughing rolling devices or finishing rolling devices in a thin-sheet hot rolling device, and capable of increasing the maximum gap between the top and the bottom work rolls and easily applying a strong roll bending force, whereby it is possible to achieve high-response and strong plate, strip-crown and shape controlling function, and a rolling method using this rolling device.
  • rolling devices such as rolling devices 1A and 1B illustrated in FIG. 12 and FIG. 13 are known, in which back up roll chocks cradle and hold work roll chocks to obtain increased roller gap.
  • an increase-bending device is incorporated in an arm portion extending from the back up roll chock for holding the work roll chock, and hence, it is difficult to employ a large-capacity hydraulic cylinder.
  • a rolling device disclosed in Patent Document 1 is a four-high rolling device having a structure type illustrated in FIG. 16 . More specifically, a top work roll chock 3-1 is held by an arm portion connected with a top back up roll chock 4-1. Top increase-bending devices 6-1 and 6-2 that each work to a top work roll 1-1 are assembled to the arm portion so as to achieve a large roller gap.
  • a rolling device such as a rolling device 1C illustrated in FIG. 14 in which the increase-bending devices 6-1 and 6-2 are incorporated in the bottom work roll chock 3-2 to achieve a large roller gap.
  • Patent Document 2 discloses a rolling device in which the increase-bending device of the work roll is incorporated in the work roll chock.
  • Patent Document 3 discloses a rolling device with a roll-cross system.
  • the increase-bending device is incorporated in the work roll chock.
  • This type of rolling device has the following problems.
  • a rolling device having a configuration in which an increase-bending device is provided to a project block to obtain a bending device having high responsiveness.
  • Patent Document 4 discloses a rolling device having a work-roll shift function.
  • this rolling device as illustrated in FIG. 15 , increase-bending devices 6-1 to 6-4 are incorporated in project blocks 5-1 and 5-2 formed integrally with a housing 9.
  • bottom increase-bending devices 6-3 and 6-4 working to a bottom work roll 1-2 are incorporated in a project block internally protruding from the housing 9.
  • the increase-bending device represents a hydraulic device that applies a force acting on the work roll chock and in the direction in which the roller gap increases, and is a generic name of a device including a hydraulic cylinder serving as an actuator of the hydraulic device and a piston rod of the hydraulic device.
  • the increase-bending device represents the hydraulic cylinder serving as the actuator of the increase-bending device and the piston rod of the hydraulic cylinder unless otherwise specified.
  • a force applied to the work roll by the increase-bending device is referred to as the increase-bending force.
  • a hydraulic device that applies, to the work roll chock, a force acting in a direction in which the roller gap decreases is referred to as a decrease-bending device.
  • a force applied to the work roll by the decrease-bending device is referred to as the decrease-bending force.
  • the decrease-bending device is a generic name of the device including the hydraulic cylinder serving as the actuator of the device and the piston rod of the hydraulic cylinder.
  • the decrease-bending device represents the hydraulic cylinder serving as the actuator of the decrease-bending device and the piston rod of the decrease-bending device, unless otherwise specified.
  • the rolling device for manufacturing the thick steel sheet does not have the decrease-bending device (see Patent Documents 1 to 4).
  • Patent Documents referred to in the description are listed as below.
  • a problem to be solved by the present invention is to provide a rolling device capable of increasing the maximum gap between the top and the bottom work rolls and applying a strong roll bending force, and a rolling method using this rolling device.
  • an object of the present invention is to provide a rolling device including a decrease-bending device as with a thin sheet rolling device and capable of: dealing with a steel sheet having a wide range of thickness; increasing the roller gap between the top and the bottom work rolls; easily applying a strong roll bending force; and overcoming the above-described drawbacks that the conventional rolling device has, and a rolling method using this rolling device.
  • the maximum gap between the top and the bottom work rolls can be increased, and even in the case where the decrease-bending device having low responsiveness is provided, this is compensated for by the increase-bending device having high responsiveness and provided to the pair of first project blocks, whereby it is possible to obtain a high-response and strong plate, strip-crown and shape controlling function.
  • the increase-bending force and the decrease-bending force are applied to the top work roll to achieve the strong plate, strip-crown and shape controlling function, and further, a multi-stage hydraulic cylinder is employed for the top-work-roll decrease-bending device to achieve generation of the roll balance force, whereby it is possible to largely increase the roll gap.
  • a multi-stage hydraulic cylinder is employed for the top-work-roll decrease-bending device to achieve generation of the roll balance force, whereby it is possible to largely increase the roll gap.
  • the force in the rolling direction acting on the top work roll chock is always borne by the housing window, whereby it is possible to stably support the top work roll chock.
  • top and the bottom increase-bending devices can be incorporated in the pair of first project blocks. This makes it possible to achieve the strong bending device having the large capacity and large stroke.
  • the increase-bending device is incorporated in the pair of first project blocks, which makes it possible to fix the hydraulic pipes and employ servo valves. With this configuration, it is possible to control the increase-bending force in a high response manner.
  • FIG. 1 is a side view illustrating an example of a structure of a rolling device 1 according to an embodiment of the present invention.
  • the rolling device 1 according to an embodiment of the present invention includes a top work roll chock 3-1, a bottom work roll chock 3-2, a top back up roll chock 4-1, a bottom back up roll chock 4-2, and a housing 9 containing these roll chocks.
  • the housing 9 has a pair of first project blocks 5-1 and 5-2 (in other words, a first project block provided on the side where a metal sheet material is inputted and a first project block provided on the output side) formed integrally with the housing, thereby forming a housing window 12.
  • the top work roll chock 3-1 supports a top work roll 1-1 for rolling a metal sheet material
  • the bottom work roll chock 3-2 supports a bottom work roll 1-2 for rolling the metal sheet material.
  • top back up roll chock 4-1 supports a top back up roll 2-1 disposed above the top work roll 1-1
  • the bottom back up roll chock 4-2 supports a bottom back up roll disposed below the bottom work roll 1-2.
  • the pair of the first project blocks 5-1 and 5-2 are formed integrally so as to protrude inwardly from the housing 9.
  • the pair of the first project blocks 5-1 and 5-2 are provided with top increase-bending devices 6-1 and 6-2 that each apply an increase-bending force through the top work roll chock 3-1 to the top work roll 1-1, and are provided with bottom increase-bending devices 6-3 and 6-4 that each apply an increase-bending force through the bottom work roll chock 3-2 to the bottom work roll 1-2.
  • the top increase-bending devices 6-1 and 6-2 are each formed by a first hydraulic cylinder serving as an actuator of the device 6-1, 6-2 and a piston rod (first piston rod) of the first hydraulic cylinder.
  • the first hydraulic cylinder is incorporated in the pair of the first project blocks 5-1 and 5-2, and is provided such that an end portion of the first piston rod protrudes from the top surface of each of the pair of the first project block 5-1, 5-2 and comes into contact with the top work roll chock 3-1.
  • the bottom increase-bending devices 6-3 and 6-4 are each formed by a second hydraulic cylinder serving as an actuator of the device 6-3, 6-4 and a piston rod (second piston rod) of the second hydraulic cylinder.
  • the second hydraulic cylinder is incorporated in the pair of the first project blocks 5-1 and 5-2, and is provided such that an end portion of the second piston rod protrudes from the bottom surface of each of the pair of the first project blocks 5-1 and 5-2 and comes into contact with the bottom work roll chock 3-2.
  • the rolling device 1 includes top decrease-bending devices 7-1 and 7-2 provided in the top back up roll chock 4-1 and having a function of applying the decrease-bending force through the top work roll chock 3-1 to the top work roll 1-1 and a function of causing a pulling-up force (roll balance force) for bringing the top work roll 1-1 into contact with the top back up roll 2-1.
  • the top decrease-bending devices 7-1 and 7-2 having the two functions are formed by a third hydraulic cylinder serving as an actuator of the device 7-1, 7-2 and a piston rod (third piston rod) of the third hydraulic cylinder.
  • the third hydraulic cylinder is provided in the top back up roll chock 4-1.
  • the third piston rod includes a top end shaped so as to engage with the top work roll chock 3-1.
  • the rolling device 1 includes bottom decrease-bending devices 7-3 and 7-4 that each apply the decrease-bending force through the bottom work roll chock 3-2 to the bottom work roll 1-2.
  • the bottom decrease-bending devices 7-3 and 7-4 are each formed by a fourth hydraulic cylinder serving as an actuator of the device 7-3, 7-4 and a piston rod (fourth piston rod) of the fourth hydraulic cylinder.
  • the fourth hydraulic cylinder is provided to the bottom back up roll chock 4-2, or is incorporated in a pair of second project blocks 5-3 and 5-4, which will be described later.
  • the fourth piston rod is provided such that a top end thereof is brought into contact with the bottom work roll chock 3-2.
  • a rolling device 1E illustrated in FIG. 16 improves the above-described points, and is frequently found in thick-sheet finishing rolling devices.
  • the top back up roll chock 4-1 includes an arm that cradles the top work roll chock 3-1. With this type of rolling device, the top back up roll chock 4-1 cradles the top work roll chock 3-1, and hence, the top work roll 1-1 ascends as the top back up roll 2-1 elevates, which makes it possible to increase the roller gap.
  • the rolling device having this structure does not have sufficient space for the increase-bending device and the decrease-bending device used for the top work roll 1-1.
  • the rolling device having this structure does not have sufficient space for the increase-bending device and the decrease-bending device used for the top work roll 1-1.
  • the small-capacity increase-bending devices 6-1 and 6-2 are provided between the top back up roll chock 4-1 and the top work roll chock 3-1, and no decrease-bending device is provided for the top work roll 1-1. This results in a drawback of limited shape-controlling ability.
  • the force in the rolling direction acting on the top work roll 1-1 is received by the contact surface on the downstream side in the rolling direction between the top back up roll chock 4-1 and the top work roll chock 3-1. Further, this force is finally received by the contact surface between the outer surface of the arm on the downstream side in the rolling direction of the top back up roll chock 4-1 and the inner side of the housing window 12.
  • the contact surface on the downstream side in the rolling direction has limited space, and it is difficult to install a load cell that can sufficiently support the top work roll chock 3-1. Further, a wobble remains on the contact surface between the top back up roll chock 4-1 and the housing window 12.
  • a stabilizer or load cell is required for each back up roll chock, and arrangement of wires necessary for activating these units significantly deteriorates workability.
  • the rolling device 1 includes the pair of the first project blocks 5-1 and 5-2 protruding inwardly from the housing 9 and disposed at positions shifted downward with respect to a pass line, as illustrated in FIG. 1 . More specifically, unlike the conventional configuration illustrated in FIG. 15 , the pair of the first project blocks 5-1 and 5-2 are disposed at positions that are not vertically symmetric with respect to the pass line.
  • the top work roll chock 3-1 is shaped such that a base portion adjacent to the portion located between the pair of the first project blocks 5-1 and 5-2, in other words, the top side portion corresponding to the width of the housing window 12 (housing window width) is set higher instead of increasing the height of the portion located between the pair of the first project blocks 5-1 and 5-2.
  • the force in the rolling direction such as a component of the offset force acting on the top work roll 1-1, in other words, the force in the rolling direction acting on the body portion of the top work roll 1-1 from the metal sheet (plate) material 10 or top back up roll 2-1 is borne by the contact surface between the top side portion of the top work roll chock 3-1 corresponding to the housing window width and the housing window 12 located above the pair of the first project blocks 5-1 and 5-2.
  • the area of the surface on which the top work roll chock 3-1 is brought into contact with the housing window 12 remains unchanged even if a drafting device 11 of the rolling device 1 is operated to increase the roller gap.
  • the position of the top work roll chock 3-1 can be stably maintained regardless of the amount of the roller gap.
  • the rolling device 1 includes the pair of the first project blocks 5-1 and 5-2 inwardly protruding from the housing 9 and including the top increase-bending devices 6-1 and 6-2 that apply the increase-bending force to the top work roll 1-1, and the bottom increase-bending devices 6-3 and 6-4 that apply the increase-bending force to the bottom work roll 1-2.
  • This configuration eliminates the need for detaching the hydraulic pipes of the increase-bending device every time the work roll is exchanged, and allows using fixed pipes. This makes it possible to employ accurate servo valves, thereby obtaining a high-responsive increase-bending device.
  • top decrease-bending devices 7-1 and 7-2 are formed by the third hydraulic cylinder incorporated in the top back up roll chock 4-1 and the third piston rod of the third hydraulic cylinder.
  • the top end of the third piston rod of the third hydraulic cylinder is operated to move in the roll axis direction at the time of exchanging the roll so as to be able to be connected with the top work roll chock 3-1, thereby applying the roll balance force.
  • the roller gap can be increased regardless of the stroke of the increase-bending device, and it is possible to apply the strong decrease-bending force in the case where a plate, strip crown control is necessary for a steel plate with a thickness of approximately 100 mm or less.
  • connection portion shows merely one embodiment, and does not limit the specific structure of the present invention.
  • FIG. 2 is a plan view of the top work roll 1-1 and the top work roll chock 3-1, and in the drawing, the near side shows the drive side, while the far side shows the work side.
  • a groove 31 having a reversed T-shape in cross-section and engaged with the top end of the third piston rod of the third hydraulic cylinder constituting the top decrease-bending device 7-1, 7-2 as a second engagement portion.
  • the groove 31 opens on the drive side, and extends up to the vicinity of the center of the chock.
  • the work roll having both ends each set with the roll chock from the operation side is delivered through a rail or other tool to a predetermined position in the housing of the rolling device 1.
  • the piston rod of the hydraulic cylinder serving as the decrease-bending device is retracted in the top back up roll chock 4-1, so that this piston rod does not obstruct the delivery.
  • the groove 31 of the top work roll chock 3-1 is positioned immediately in front of an expanded portion (first engagement portion) of the third piston rod of the third hydraulic cylinder to be engaged with the groove 31.
  • the piston rod is descended to a predetermined position.
  • the inner surface of the groove 31 is kept in a position where it does not come into contact with the external surface of the third piston rod, and the expanded portion of the third piston rod is moved into the groove 31 from the groove opening portion on the drive side.
  • FIG. 3A is a diagram illustrating a state where the expanded portion formed at the top end of the third piston rod of the third hydraulic cylinder of the top decrease-bending device 7-1, 7-2 is engaged with the groove 31. More specifically, FIG. 3A illustrates a state where, with the pulling-up operation made by the third hydraulic cylinder, the third piston rod is pulled upward and is brought into contact with the top surface of the groove 31 of the top work roll chock 3-1, thereby applying a lifting force f RB .
  • the lifting force f RB acts as the roll balance force.
  • FIG. 3B is a diagram illustrating a state where the top decrease-bending force is applied in the case of controlling plate, strip crown and shapes in such a case as finishing rolling in the thin-sheet hot rolling.
  • the third piston rod extends downward to apply a pressing force f DC to the bottom surface of the groove 31 of the top work roll chock 3-1, thereby applying the decrease-bending force.
  • FIG. 3C is a diagram illustrating a non-contact state where the groove 31 is brought into engagement with the third piston rod at the time of exchanging rolls as described above, or this engagement is canceled.
  • the groove 31 is formed in the top work roll chock 3-1, and the expanded portion to be engaged with the groove 31 is formed in the top decrease-bending device 7-1, 7-2.
  • the present invention is not limited to this mode.
  • the force in the rolling direction applied to the body portion of the bottom work roll 1-2 is borne by the contact surface between the bottom work roll chock 3-2 and the project block (5-1 or 5-2) provided on the output side.
  • a portion of the bottom work roll chock 3-2 located between the pair of the first project blocks 5-1 and 5-2 is raised.
  • the roller gap is adjusted mainly by moving upward and downward the top work roll chock 3-1, the amount of travel of the bottom work roll chock 3-2 is small in the vertical direction. Thus, the positions of the bottom work roll 1-2 remain stable even if the roller gap is increased.
  • FIG. 4 is a plan sectional view illustrating an example of arrangement of the top and bottom increase-bending devices 6-1 to 6-4.
  • FIG. 4 is a sectional view at the height of the pass line of the pair of the first project blocks 5-1 and 5-2.
  • the top and bottom increase-bending devices 6-1 to 6-4 so as to be positionally shifted to each other on the plan sectional view of the pair of the first project blocks 5-1 and 5-2.
  • the top and bottom increase-bending devices 6-1 to 6-4 do not interfere with each other within the pair of the first project blocks 5-1 and 5-2.
  • first hydraulic cylinder and the second hydraulic cylinder which are incorporated in each of the first project blocks 5-1 and 5-2, do not interfere with each other. This makes it possible to increase the capacity of the first hydraulic cylinder and the second hydraulic cylinder, increase the stroke of each of the first piston rod and the second piston rod, and increase the amount of operation of the increase bending.
  • the bottom increase-bending devices 6-3 and 6-4 are formed by two second hydraulic cylinders located on the input side and the output side.
  • a similar effect can be obtained by using one second hydraulic cylinder for each of the bottom increase-bending devices 6-3 and 6-4 and arranging them at different positions in the axial direction of the bottom work roll 1-2 to prevent the second hydraulic cylinder from interfering with the first hydraulic cylinder.
  • FIG. 5 is a plan sectional view illustrating an example of arrangement of the top and bottom increase-bending devices 6-1 to 6-4.
  • FIG. 5 is a sectional view at the height of the pass line of the pair of the first project blocks 5-1 and 5-2.
  • the first hydraulic cylinder and the second hydraulic cylinder may be arranged so as to be positionally shifted in the rolling direction. With this arrangement, the first hydraulic cylinder and the second hydraulic cylinder do not interfere with each other.
  • FIG. 12 and FIG. 13 illustrate rolling devices 1A and 1B according to conventional arts, each of which has an increased roller gap.
  • these rolling devices 1A and 1B cannot apply a strong roll bending force. This is because these rolling devices have a structure in which the top increase-bending devices 6-1 and 6-2 are incorporated in the arm portion protruding downward from the top back up roll chock 4-1, which prevents the large-capacity and large-stroke top increase-bending devices 6-1 and 6-2 from being installed. Further, these rolling devices 1A and 1B have the arm portion extending from the top back up roll chock 4-1, and hence, the top decrease-bending devices 7-1 and 7-2 are required to be installed at the space shifted to the axial center of the roll. Thus, interference with the bearing for the top back up roll 2-1 occurs, which makes it impossible to dispose the large-capacity and large-stroke top decrease-bending devices 7-1 and 7-2.
  • the large-capacity and large-stroke top increase-bending devices 6-1 and 6-2 can be disposed in the pair of the first project blocks 5-1 and 5-2 protruding inwardly from the housing 9 of the rolling device 1.
  • the top back up roll chock 4-1 does not have the arm portion. This allows the large-capacity and large-stroke top decrease-bending devices 7-1 and 7-2 to be disposed at positions of the top back up roll chock 4-1 that do not interfere with the bearing for the top back up roll 2-1, whereby it is possible to apply the large decrease-bending force to the top work roll 1-1.
  • the rolling device 1 of this embodiment having a structure in which, together with the positions of the pair of the first project blocks 5-1 and 5-2, the force in the rolling direction applied to the body portion of the top work roll 1-1 is received by the contact surface between the top work roll chock 3-1 and the housing window 12, it is possible to increase the roller gap and apply the strong roll bending force.
  • FIG. 6 is a side view illustrating a rolling device 1' according to a modification example of this embodiment.
  • the rolling device 1' illustrated in FIG. 6 has the same top roll systems as those illustrated in FIG. 1 and different bottom roll systems from those illustrated in FIG. 1 .
  • the bottom back up roll chock 4-2 has the bottom decrease-bending devices 7-3 and 7-4 that apply the decrease-bending force to the bottom work roll 1-2.
  • the bottom decrease-bending devices 7-3 and 7-4 are disposed to a pair of second project blocks 5-3 and 5-4 located below the pair of the first project blocks 5-1 and 5-2.
  • the hydraulic pipes of the decrease-bending device are required to be detached when the bottom back up roll 2-2 is exchanged. In other words, it is highly likely that small foreign substances enter the hydraulic pipes at the time of detachment.
  • the roll bending device has reduced responsiveness as compared with the case where the fixed pipes or servo valves are employed.
  • the rolling device 1' illustrated in FIG. 6 it is possible to overcome the above-described problem occurring at the time of exchanging the bottom back up roll 2-2.
  • servo valves for high-response hydraulic control can be used for the hydraulic pipes of the bottom decrease-bending devices 7-3 and 7-4 provided to the pair of the second project blocks 5-3 and 5-4, whereby it is possible to eliminate the need for using the flexible pipes.
  • the bottom back up roll 2-2 can be easily exchanged, and the high-response roll bending device can be obtained.
  • top decrease-bending devices 7-1 and 7-2 are provided to the top back up roll chock 4-1 as illustrated in FIG. 1 and FIG. 6 , the hydraulic pipes of the top decrease-bending devices 7-1 and 7-2 are required to be detached at the time of exchanging the top back up roll 2-1, and hence, it is highly likely that small foreign substances enter the hydraulic pipes at the time of exchange.
  • the responsiveness of the roll bending device reduces as compared with the case where the fixed pipes or servo valves are used.
  • the decrease-bending force cannot be applied at idle time when the rolling load is not applied.
  • it is necessary to rapidly complete setting the decrease-bending force by the start of rolling from the idle state in which the roll balance force is applied, and rapidly turn back into the roll balance state at the time of completion of the rolling.
  • the rolling method according to this embodiment solves the above-described problems.
  • the rolling method uses the rolling device 1, 1' according to this embodiment including the top back up roll chock 4-1 provided with the top decrease-bending devices 7-1 and 7-2, and solves the above-described problems that may occur in the rolling device 1, 1'.
  • the responsiveness of the decrease-bending device may deteriorate.
  • the rolling device 1, 1' has a structure in which the pair of the first project blocks 5-1 and 5-2 protruding inwardly from the housing 9 includes the top increase-bending devices 6-1 and 6-2, thereby obtaining the top increase-bending device having the large capacity and large stroke.
  • the rolling method according to this embodiment uses the increase-bending device having high responsiveness for changing the roll bending force at the time of starting rolling and at the time of finishing rolling, in the case where the decrease-bending force is applied to the work roll to control the plate, strip crown and shapes, thereby compensating for the responsiveness of the decrease-bending device.
  • FIG. 7 is a diagram illustrating an example of an operation flow of the rolling method according to this embodiment. More specifically, FIG. 7 is a diagram illustrating an operation flow performed by the increase-bending device having the high responsiveness and an operation flow performed by the decrease-bending device having relatively low responsiveness as compared with the increase-bending device.
  • FIG. 8 illustrates a change in time series of the roll bending force to one roll material or other parameters in this rolling method.
  • FIG. 8 indicates, from top to bottom, a change in time series of rolling load, output from the increase-bending device, output from the decrease-bending device, and work-roll bending force serving as the resultant force of these forces.
  • a setting value F R of the work-roll bending force during rolling that corresponds to a roll material to be next rolled.
  • the F R is a negative value, in other words, is calculated as the decrease-bending force.
  • the increase-bending force force acting in the increase direction in which roll is opened
  • the decrease-bending force force acting in the decrease direction in which the roll is pressed
  • both the increase-bending force and the decrease-bending force are activated, so that a roll bending force on the increase side corresponding to a roll balance force F B acts as a resultant force on the work roll chock.
  • I B + D B acts as the roll balance force F B (>0), where I B (>0) is the output from the increase-bending device and D B ( ⁇ 0) is the output from the decrease-bending device.
  • the roll balance force F B is determined to be a force by which slippage does not occur between the work roll driven by an electric motor even in the idle time and the back up roll, which is a follower.
  • D B is set to be the minimum hydraulic pressure at which the actuator of the decrease-bending device does not detach from the work roll chock.
  • the increase-bending force is changed (decreased) while the decrease-bending force is kept constant so that the predetermined work-roll bending force F R during rolling acts as a resultant force on the work roll chock.
  • the output from the increase-bending device is changed from Is to I R .
  • the work-roll bending force as the resultant force is rapidly changed from the roll balance force F B (>0) to the roll bending force F R ( ⁇ 0) during rolling operation through the control performed by the increase-bending device having high responsiveness, while the output from the decrease-bending device having low responsiveness is kept unchanged from D S .
  • the time (b) of starting rolling represents a time when the rolling starts, and may be determined to be the time when the load detected, for example, with a load cell for measuring the rolling load of the rolling device 1, 1' exceeds 30% of the expected rolling load.
  • the metal sheet is rolled while the roll bending force during rolling is maintained.
  • the roll bending force corresponding to the roll balance force F B is caused to act as the resultant force on the work roll chock, and the rolling ends.
  • the output from the increase-bending device having high responsiveness is changed from I R to Is, while the output from the decrease-bending device is kept to D S .
  • the work-roll bending force as the resultant force is rapidly changed from the work-roll bending force (F R ( ⁇ 0)) during rolling to the roll balance force (F S (>0)).
  • the time (c) of completion of rolling represents the time when the rolling ends, and may be determined, for example, to be the timing when the load detected, for example, with the load cell for measuring the rolling load of the rolling device 1, 1' falls below 50% of the average value of the actual rolling load.
  • the point in time when 1 to 3 seconds elapses from the time (c) of completion of rolling is determined to be a work completion timing (point (d) on the time axis), and at this timing, the output from the increase-bending device is changed to be I B , and the output from the decrease-bending device is changed to be D B . Even at these changes, the work-roll bending force as the resultant force is substantially kept to the roll balance force F B .
  • the increase-bending device having high responsiveness is used to change the roll bending force at the time of starting rolling and at the time of completion of rolling.
  • the increase-bending device having high responsiveness is compensated for by the increase-bending device having high responsiveness, so that it is possible to control plate, strip crown and shapes in a high-response and strong manner.
  • the rolling method of this embodiment it is possible to obtain favorable plate, strip crown and shape even if there exist external disturbances varying during rolling such as thickness of roll materials on the input side and temperatures of the roll material. This makes it possible to significantly improve the product quality and production yield.
  • FIG. 9 is a diagram illustrating a change in time series of the roll bending force and other parameters in the case where the decrease-bending device has significantly low responsiveness (in particular, the decrease-bending device has a hydraulic characteristic in which the pressure decreases if the loading force becomes lost).
  • FIG. 9 illustrates a change in time series of the roll bending force and other parameters occurring in association with operations of rolling a roll material performed in accordance with the operation flow of the increase-bending device and the decrease-bending device illustrated in FIG. 7 .
  • FIG. 9 illustrates an example in which the decrease-bending device has low response speed as compared with the case in FIG. 7 and FIG. 8 .
  • the output from the increase-bending device having high responsiveness sharply changes, and hence, the output from the decrease-bending device having low responsiveness varies.
  • the work-roll bending force as the resultant force reaches F R later than the timing (b), and reaches F B later than the timing (c).
  • the rolling method illustrated in FIG. 10 solves this problem.
  • FIG. 10 is a diagram illustrating an operation flow in the case where the increase-bending device having high responsiveness and the decrease-bending device having low responsiveness are provided.
  • FIG. 11 illustrates a change in time series of the roll bending force acting on one roll material and other parameters in this rolling method.
  • FIG. 11 indicates, from top to bottom, a change in time series of rolling load, output from the increase-bending device, output from the decrease-bending device, the work-roll bending force, which is the resultant force thereof.
  • the decrease-bending force is measured at all times with a load cell provided to the decrease-bending device, or the hydraulic pressure in the hydraulic pipes connected with the decrease-bending device is measured at all times.
  • the increase-bending device is dynamically controlled. More specifically, before and after the rolling, the output from the increase-bending device is controlled on the basis of the decrease-bending force or hydraulic pressure of the decrease-bending device so as to make the work-roll bending force equal to the roll balance force F B . Note that controls other than that described above are similar to those in the rolling method illustrated in FIG. 7 , and will be described in detail below.
  • both the increase-bending force and the decrease-bending force are activated, so that a roll bending force on the increase side corresponding to a roll balance force F B acts as the resultant force on the work roll chock.
  • I B + D B acts as the roll balance force F B (>0), where I B (>0) is the output from the increase-bending device and D B ( ⁇ 0) is the output from the decrease-bending device.
  • the increase-bending force is changed (decreased) while the decrease-bending force is kept constant so that the predetermined work-roll bending force F R during rolling acts as the resultant force on the work roll chock.
  • the output from the increase-bending device is changed from I S to I R .
  • the work-roll bending force as the resultant force is rapidly changed from the roll balance force F B (>0) to the roll bending force F R ( ⁇ 0) during rolling operation through the control performed by the increase-bending device having high responsiveness while the output from the decrease-bending device having low responsiveness is kept unchanged from D S .
  • the metal sheet is rolled while the roll bending force during rolling is maintained.
  • the output I R from the increase-bending device is controlled so as to always keep at constant the roll balance force F B that may slightly vary, and then, is outputted simultaneously with the output D S from the decrease-bending device.
  • the roll bending force corresponding to the roll balance force F B is caused to act as the resultant force on the work roll chock, and the rolling ends.
  • the output from the increase-bending device having high responsiveness is changed from I R to Is while the output from the decrease-bending device is kept to D S .
  • the work-roll bending force as the resultant force is rapidly changed from the work-roll bending force (F R ( ⁇ 0)) during rolling to the roll balance force (F S (>0)).
  • the point in time when 1 to 3 seconds elapses from the time (c) of completion of rolling is determined to be a work completion timing (point (d) on the time axis), and at this timing, the output from the increase-bending device is changed to I B , and the output from the decrease-bending device is changed to D B .
  • the output Is from the increase-bending device is controlled so as to always keep at constant the roll balance force F B that may slightly vary, and then, is outputted simultaneously with D S .
  • the variation in the output from the decrease-bending device is compensated for by the increase-bending device, as illustrated in FIG. 11 , whereby it is possible to control the work-roll bending force in an appropriate and high-response manner.
  • the roll balance force for the top work roll 1-1 is provided through the pull operation of the third piston rod, and then, in the case where rolling is performed with a roller gap not exceeding the stroke of the first hydraulic cylinder, the above-described rolling method (first step to sixth step) is applied.
  • the present invention may be expressed in the following manner.
  • this method for rolling the metal sheet material it may be possible to measure hydraulic pressure in a hydraulic cylinder that generates the decrease-bending force or in hydraulic pipes connected with the hydraulic cylinder, and control the increase-bending force on the basis of the measurement values so that the roll bending force acting as the resultant force on the work roll chock is equal to a predetermined value.
  • a device for rolling a steel sheet and a rolling method which can deal with steel materials having various thicknesses ranging from an extremely thick sheet to a thin sheet, and can be used in particular as a reverse rolling device having an increased gap or a rolling device that strongly controls plate, strip crown and shape.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
EP20120761152 2011-03-24 2012-03-05 Device for rolling metal sheet material and method for rolling metal sheet material Not-in-force EP2626149B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011066153 2011-03-24
PCT/JP2012/055515 WO2012128019A1 (ja) 2011-03-24 2012-03-05 金属板材の圧延機および圧延方法

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EP2626149A1 EP2626149A1 (en) 2013-08-14
EP2626149A4 EP2626149A4 (en) 2014-03-05
EP2626149B1 true EP2626149B1 (en) 2015-04-29

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JP (1) JP5059250B1 (zh)
KR (1) KR101392078B1 (zh)
CN (1) CN103237609B (zh)
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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
TWI499881B (zh) * 2014-04-29 2015-09-11 China Steel Corp Method of establishing the instant compensation system of width compensation and its database
JP7313768B2 (ja) * 2019-05-23 2023-07-25 スチールプランテック株式会社 圧延機、並びに圧延方法及びワークロールの運用方法
WO2021205548A1 (ja) * 2020-04-07 2021-10-14 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ 株式会社 圧延機、圧延機の製造方法、および圧延機の改造方法
CN113787095B (zh) * 2021-09-03 2024-05-03 太原理工大学 一种可施加水平振动的金属复合板轧制装置

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JPS6040928B2 (ja) * 1978-08-09 1985-09-13 株式会社日立製作所 圧延機
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JPS62142403U (zh) * 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
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CN2936473Y (zh) * 2006-06-27 2007-08-22 宝山钢铁股份有限公司 轧机支撑辊提升活塞杆的改进结构
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Publication number Publication date
EP2626149A1 (en) 2013-08-14
TWI496630B (zh) 2015-08-21
KR20130069875A (ko) 2013-06-26
JP5059250B1 (ja) 2012-10-24
CN103237609A (zh) 2013-08-07
JPWO2012128019A1 (ja) 2014-07-24
KR101392078B1 (ko) 2014-05-07
EP2626149A4 (en) 2014-03-05
WO2012128019A1 (ja) 2012-09-27
CN103237609B (zh) 2014-05-28
TW201304886A (zh) 2013-02-01

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