WO2013042204A1 - Laminoir à froid, installation de laminage en tandem, installation de laminage réversible, procédé de modification d'une installation de laminage et procédé d'exploitation d'un laminoir à froid - Google Patents

Laminoir à froid, installation de laminage en tandem, installation de laminage réversible, procédé de modification d'une installation de laminage et procédé d'exploitation d'un laminoir à froid Download PDF

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Publication number
WO2013042204A1
WO2013042204A1 PCT/JP2011/071391 JP2011071391W WO2013042204A1 WO 2013042204 A1 WO2013042204 A1 WO 2013042204A1 JP 2011071391 W JP2011071391 W JP 2011071391W WO 2013042204 A1 WO2013042204 A1 WO 2013042204A1
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Prior art keywords
rolling mill
roll
rolling
work roll
rolls
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PCT/JP2011/071391
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English (en)
Japanese (ja)
Inventor
晋一 安成
文久 島谷
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三菱日立製鉄機械株式会社
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=46261527&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2013042204(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by 三菱日立製鉄機械株式会社 filed Critical 三菱日立製鉄機械株式会社
Priority to JP2011554001A priority Critical patent/JP4928653B1/ja
Priority to CN201180018331.2A priority patent/CN103118813B/zh
Priority to BR112012027654-9A priority patent/BR112012027654B1/pt
Priority to PCT/JP2011/071391 priority patent/WO2013042204A1/fr
Priority to KR1020127032141A priority patent/KR101424375B1/ko
Priority to EP12184124.1A priority patent/EP2572808B1/fr
Publication of WO2013042204A1 publication Critical patent/WO2013042204A1/fr

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    • 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
    • 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
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • 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
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • B21B1/24—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a continuous or semi-continuous process
    • B21B1/28—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a continuous or semi-continuous process by cold-rolling, e.g. Steckel cold mill
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B1/00—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations
    • B21B1/22—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length
    • B21B1/30—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a non-continuous process
    • B21B1/32—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a non-continuous process in reversing single stand mills, e.g. with intermediate storage reels for accumulating work
    • B21B1/36—Metal-rolling methods or mills for making semi-finished products of solid or profiled cross-section; Sequence of operations in milling trains; Layout of rolling-mill plant, e.g. grouping of stands; Succession of passes or of sectional pass alternations for rolling plates, strips, bands or sheets of indefinite length in a non-continuous process in reversing single stand mills, e.g. with intermediate storage reels for accumulating work by cold-rolling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/142—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls by axially shifting the rolls, e.g. rolls with tapered ends or with a curved contour for continuously-variable crown CVC
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/028—Sixto, six-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2261/00—Product parameters
    • B21B2261/02—Transverse dimensions
    • B21B2261/06—Width
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2267/00—Roll parameters
    • B21B2267/02—Roll dimensions
    • B21B2267/06—Roll diameter
    • 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
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/14—Couplings, driving spindles, or spindle carriers specially adapted for, or specially arranged in, metal-rolling mills

Definitions

  • the present invention relates to a cold rolling mill, a tandem rolling facility, a reversible rolling facility, a method for remodeling the rolling facility, and a method for operating the cold rolling mill.
  • the steel sheet of ordinary steel or high-tensile steel is rolled in four or six stages with a work roll diameter of about 420 to 630 mm according to the past results. It is produced in large quantities at the tandem rolling mill. This can be confirmed, for example, from the facility specifications shown in Non-Patent Document 1.
  • the steel sheet of ordinary steel or high-tensile steel used mainly in automobiles is a 4- or 6-high rolling mill with a work roll diameter of about 420 to 630 mm.
  • the demand for high-tensile steel sheets has increased, and the need for high-strength steel sheets that are harder than before, and even higher-strength steel sheets with the same hardness is higher.
  • the following two means can be considered.
  • the work roll diameter of the rolling mill is reduced, and the cluster type multi-stage rolling mill described above is a typical rolling mill having a work roll diameter of 200 mm or less.
  • the second is a method of increasing the number of stands in a conventional tandem rolling mill. Even if the rolling capacity of one stand does not change, the total rolling reduction capacity of the tandem rolling mill can be improved by increasing the number of stands. That is, it is possible to roll a harder steel plate or roll at a higher reduction rate while maintaining the characteristics of a tandem rolling mill with high productivity.
  • increasing the number of rolling mill stands greatly increases initial investment for new construction and additional investment for remodeling.
  • the conventional rolling equipment has problems such as a decrease in production due to the use of a small-diameter work roll mill such as a cluster-type multi-stage rolling mill and a significant increase in cost due to the addition of a stand.
  • An object of the present invention is to reduce the diameter of a work roll of a six-high rolling mill, thereby enabling rolling of a steel plate that is harder than before and rolling at a higher reduction rate even with a steel plate of the same hardness, and a cluster type
  • the present invention provides a cold rolling mill, a tandem rolling facility, a reversible rolling facility, a remodeling method for a rolling facility, and an operating method for a cold rolling mill that do not cause a decrease in production due to the use of a small-diameter work roll mill such as a multistage rolling mill.
  • Another object of the present invention is to maintain the high productivity of conventional tandem rolling equipment, and to roll steel plates that are harder than before and to increase the reduction even with steel plates of the same hardness without increasing the number of stands. It is to provide a cold rolling mill capable of rolling at a rate, a tandem rolling facility, a method for remodeling the rolling facility, and a method for operating the cold rolling mill.
  • a first invention for achieving the above object is a cold rolling mill for rolling a steel sheet having a minimum sheet width of 600 mm or more and a maximum sheet width of 1,500 mm or more and 1,900 mm or less, a pair of upper and lower work rolls, and the work rolls
  • the diameter of the work roll is in the range of 300 mm to 400 mm
  • the diameter of the intermediate roll is in the range of 560 mm to 690 mm.
  • tandem rolling facility is configured by using at least one stand of the cold rolling mill of the present invention by using a work roll having a smaller diameter than the conventional one, the high productivity of the conventional tandem rolling facility is maintained.
  • the second invention is characterized in that, in the first invention, a work roll drive device for rotating the work roll is provided as a drive device for the rolling mill.
  • the overload prevention apparatus can immediately act and stop the rolling mill.
  • the work roll since there is no driving tangential force to the work roll that occurs in the case of intermediate roll drive, the work roll does not bend in the horizontal direction, and the original shape control capability of the rolling mill can be demonstrated. it can.
  • the third invention is characterized in that, in the second invention, the work roll driving device has a gear type spindle for transmitting a driving force of an electric motor to the work roll.
  • the fourth invention is characterized in that, in the second or third invention, the work roll drive device has an overload prevention device for preventing the spindle from being damaged.
  • the overload prevention device works immediately.
  • the rolling mill can be stopped without damaging the spindle.
  • one of the work roll and the intermediate roll is placed on the entry side or exit side in the rolling direction with respect to the axis of the other roll. It is further characterized by further comprising a roll offset device that can be offset to the position.
  • the sixth invention is characterized in that, in the first invention, an intermediate roll driving device for rotationally driving the intermediate roll is provided as a driving device for the rolling mill.
  • the intermediate roll diameter is usually designed to be larger than the work roll diameter, so the drive spindle of the drive device can also be designed within the range of the intermediate roll diameter, so that it can be manufactured with sufficient strength for the required torque.
  • the intermediate roll driving device has a cross-pin type spindle that transmits a driving force of an electric motor to the intermediate roll.
  • the eighth invention is the above sixth or seventh invention, wherein either one of the work roll and the intermediate roll is offset to the entry side or the exit side in the rolling direction with respect to the axis of the other roll. And a roll offset device that can be used.
  • a ninth aspect of the invention is a tandem rolling facility having a rolling mill row provided with a multi-stand rolling mill, wherein the multi-stand rolling mill is a cold rolling according to any one of the first to eighth aspects of the invention described above. Including at least one stand.
  • the multi-stand rolling mills may all be the cold rolling mills according to any of the first to eighth inventions described above.
  • a tenth invention is a reversible rolling equipment having at least one reversible rolling mill, wherein the reversible rolling mill includes at least one cold rolling mill according to any of the first to eighth inventions described above. It is characterized by.
  • An eleventh aspect of the invention is a method for remodeling a rolling facility equipped with a one-stand or multi-stand rolling mill, wherein at least one stand of the rolling mill is the cold rolling mill according to any one of the first to eighth inventions described above. It is characterized by changing to.
  • the rolling equipment is a reversible rolling equipment, it is possible to roll a steel plate that is harder than before and a steel plate having the same hardness with a higher reduction ratio by using existing equipment.
  • a twelfth invention is a method of operating a cold rolling mill, and uses the cold rolling mill according to any of the first to eighth inventions described above, and rolls the steel sheet at a rolling reduction higher than 12%. It is characterized by doing.
  • the present invention by reducing the diameter of the work roll, it is possible to roll a steel plate that is harder than before and to roll a steel plate having the same hardness even at a higher reduction rate, and for a cluster type multi-stage rolling mill. Such a decrease in productivity due to the use of a small diameter work roll mill can be prevented.
  • the high productivity of conventional tandem rolling equipment is maintained, and without increasing the number of stands, the rolling of a steel plate that is harder than before and the steel plate of the same hardness are higher. Rolling at a rolling reduction is possible.
  • FIG. 1 is a side view of a six-high rolling mill.
  • FIG. 2 shows a cross-sectional arrow view in the direction A of FIG.
  • FIG. 3 shows a cross-sectional arrow view in the direction B of FIG.
  • FIG. 4 is a graph showing a limit load that can maintain a good plate shape when various intermediate roll diameters are combined for each work roll from the viewpoint of the maximum load that can ensure a good plate shape.
  • FIG. 5 shows the allowable rolling load based on the contact pressure between rolls allowed from the strength of the rolls in the combination of each work roll diameter and the optimum intermediate roll diameter obtained from FIG. It is a figure which shows the result calculated
  • FIG. 5 shows the allowable rolling load based on the contact pressure between rolls allowed from the strength of the rolls in the combination of each work roll diameter and the optimum intermediate roll diameter obtained from FIG. It is a figure which shows the result calculated
  • FIG. 6 is a diagram in which the limit rolling load capable of maintaining a good plate shape in the combination of each work roll diameter and the optimum intermediate roll diameter for the work roll obtained in FIG. 4 is added to FIG.
  • FIG. 7 is a diagram in which the rolling reduction obtained at each work roll diameter is obtained by simulation when rolling is performed with the allowable rolling load obtained from FIG. 6, and this is added to FIG.
  • FIG. 8 is a diagram showing the same examination result as FIG. 7 in the combination of the intermediate roll diameter and each work roll diameter when the intermediate roll diameter is fixed at a certain value and the work roll diameter is changed.
  • FIG. 9 is a view showing the same examination results as FIG. 7 in the combination of each work roll diameter and the optimum intermediate roll diameter when the plate width is changed between 600 mm and 1,900 mm.
  • FIG. 7 is a diagram in which the limit rolling load capable of maintaining a good plate shape in the combination of each work roll diameter and the optimum intermediate roll diameter for the work roll obtained in FIG. 4 is added to FIG.
  • FIG. 7 is
  • FIG. 10 is a diagram showing the results of a comparative study of the number of necessary stands in the case of the work roll diameter of 340 mm and the conventional work roll of 475 mm in rolling a 780 MPa high-tensile steel plate.
  • FIG. 11 is a diagram showing the results of a comparative study of the rolling reduction ratio and the cumulative rolling reduction ratio at each stand in the case of the work roll diameter of 340 mm and the conventional work roll of 475 mm in rolling a 780 MPa high-tensile steel plate.
  • FIG. 11 is a diagram showing the results of a comparative study of the rolling reduction ratio and the cumulative rolling reduction ratio at each stand in the case of the work roll diameter of 340 mm and the conventional work roll of 475 mm in rolling a 780 MPa high-tensile steel plate.
  • FIG. 12 is a diagram showing the result of a comparative examination of the number of necessary stands in the case of a work roll diameter of 340 mm and a work roll diameter of 475 mm in the rolling of a 1,180 MPa high-tensile steel plate.
  • FIG. 13 is a diagram showing the results of comparing and examining the rolling reduction ratio and the cumulative rolling reduction ratio of each stand in the case of a work roll diameter of 340 mm and a conventional work roll of 475 mm in the rolling of a 1,180 MPa high-tensile steel plate. is there.
  • FIG. 14 is a view of the drive system of the work roll drive system as viewed from the side of the rolling mill.
  • FIG. 15 is a schematic longitudinal sectional view of a gear type spindle.
  • FIG. 16A is a schematic longitudinal sectional view showing a cross pin type spindle.
  • FIG. 16B is a cross-sectional view taken along line AA in FIG. 16A.
  • FIG. 17 is a diagram showing the relationship between the outer diameter of the spindle coupling and the maximum transmission torque.
  • FIG. 18A is a diagram showing a general arrangement of coupling portions of a pair of upper and lower spindles.
  • FIG. 18B is a diagram showing the arrangement of coupling portions that can improve the spindle strength.
  • FIG. 19A is a diagram showing a work roll drive device provided with a spindle type hydraulic torque limiter as an overload prevention device.
  • FIG. 19B is a view showing a work roll drive device provided with a coupling type hydraulic torque limiter as an overload prevention device.
  • FIG. 19A is a diagram showing a work roll drive device provided with a spindle type hydraulic torque limiter as an overload prevention device.
  • FIG. 19B is a view showing a work roll drive device
  • FIG. 19C is a diagram illustrating a configuration in which a shear pin is provided in a coupling that connects an output shaft of a gear box to an electric motor as an overload prevention device.
  • FIG. 20A is a diagram illustrating a work roll offset method.
  • FIG. 20B is a diagram illustrating an intermediate roll offset method.
  • FIG. 21 is a view of an intermediate roll drive type drive system as viewed from the side of the rolling mill.
  • FIG. 22 is a diagram showing an embodiment of a tandem rolling facility configured using the cold rolling mill of the present invention.
  • FIG. 23 is a diagram showing an embodiment of a reversible rolling facility constructed using the cold rolling mill of the present invention.
  • FIG. 24 is a diagram showing a modification of the tandem rolling equipment performed using the cold rolling mill of the present invention.
  • FIG. 25 is a diagram showing another modification of the tandem rolling equipment performed using the cold rolling mill of the present invention.
  • FIG. 26 is a diagram showing a good plate shape.
  • FIG. 27 is
  • FIG. 1 shows a side view of a six-high rolling mill
  • FIGS. 2 and 3 show sectional views in the A and B directions of FIG. 1, respectively.
  • a six-high rolling mill 51 includes a pair of upper and lower work rolls 2 that are rolled in direct contact with a rolled material (steel plate) 1 that is a metal plate, and a pair of upper and lower pairs that support the work roll 2.
  • a roll 3 and a pair of upper and lower reinforcing rolls 4 for supporting the intermediate roll 3 are provided.
  • a bearing box 8 and a bearing box 9 are attached to the roll ends of the work roll 2 and the intermediate roll 3, respectively, and by applying a vertical force to these bearing box 8 and bearing box 9, as shown in FIG.
  • a work roll bending apparatus 10 and an intermediate roll bending apparatus 11 for bending each roll are installed. The structure is supported by the housing 5 via the bearing box 6 of the reinforcing roll 4.
  • a hydraulic reduction device 7 is installed as a reduction means, and the rolling down of the rolled material 1 is performed by moving the bearing box 6 of the lower reinforcing roll 4 up and down by this reduction means.
  • the work roll bending apparatus 10 can give increment bending and decrease bending to the work roll.
  • a roll shift device 23 (FIG. 3) is installed on the pair of upper and lower intermediate rolls 3 so as to be movable in the roll axis direction.
  • An example of the shift device 23 will be described with reference to FIG.
  • the bearing box 9 of the intermediate roll 3 is sandwiched between intermediate roll offset devices 19, and the intermediate roll offset device 19 is incorporated in a shift block 12 that fits into the project block 17 and is movable in the roll axial direction.
  • the intermediate roll offset device 19 is installed for the purpose of moving the intermediate roll 3 in the horizontal direction and changing the relative position with respect to the work roll 2. Details of the configuration, purpose, and operation will be described later.
  • the drive side shift block 12 and the intermediate roll bearing box 9 are connected via a keeper plate 14 operated by a hydraulic cylinder 15, and the operation side shift block 12 and the drive side shift block 12 are connected by a stay 18. ing. Thereby, the intermediate roll 3 and the shift block 12 are united.
  • the shift cylinder 24 fixed to the housing 5 is provided with a hydraulic cylinder 16 and is connected to the drive-side shift block 12. With such a configuration, it is possible to move the intermediate roll 3 and the shift block 12 to free positions in the roll axis direction by driving the hydraulic cylinder 16.
  • the intermediate roll bending device 11 is built in the intermediate roll offset device 19, even if the intermediate roll 3 is shifted in the roll axial direction and / or the intermediate roll 3 is moved in the horizontal direction, It has the feature that the point of action of bending force does not change.
  • a chamfer 3a of about 1000R which is usually tapered, is attached to the roll end of the intermediate roll 3.
  • the distance from the starting point of the chamfer 3a to the end of the rolled material 1 is referred to as UC ⁇ .
  • the UC ⁇ is expressed as positive, and when it is inside, it is expressed as negative.
  • the “good plate shape” that will appear in the following description is defined.
  • various combinations of work roll diameter, intermediate roll diameter, and sheet width are performed to perform simulation of the sheet crown shape after rolling, and the limit load at which this sheet crown shape can satisfy the following conditions is: It was expressed as “the limit load that can keep the shape good”, and the plate shape at that time was defined as “good plate shape”. That is, h (0) ⁇ h (x) (0 ⁇ x ⁇ b) ...
  • FIG. 4 is a graph showing a limit load that can maintain a good plate shape when various intermediate roll diameters are combined for each work roll.
  • the horizontal axis represents the intermediate roll diameter
  • the vertical axis represents the rolling load (here, the load per unit plate width: ton / mm).
  • the rolling force of the limit that can keep the plate shape good by changing the intermediate roll diameter was calculated.
  • the intermediate roll diameter when the work roll diameter is 475 mm, if the intermediate roll diameter is increased in order from 500 mm, the maximum load that can maintain a good plate shape is increased up to 580 mm, but if it exceeds 580 mm, the intermediate roll diameter is further increased. It can be seen that the maximum value of the load capable of maintaining a good plate shape does not change even if the value is increased, and the effect of increasing the intermediate roll diameter is flat. In such a case, in actual operation, the roll diameter as small as possible is selected in consideration of the initial cost of roll production and the subsequent running cost. Further, an increase in the roll diameter leads to an increase in the overall dimensions of the rolling mill, which is not preferable in terms of capital investment. Therefore, the optimum intermediate roll diameter when the work roll diameter is 475 mm is 580 mm. Similarly, the optimum intermediate roll diameter is found for each of the other work rolls.
  • the allowable rolling load tends to increase as the work roll diameter decreases.
  • the limit of the contact pressure in the roll is closely related to the hardness of the roll, and the higher the hardness, the higher the allowable contact pressure.
  • the contact pressure between rolls is determined (geometrically) by the combination of roll diameters, and the contact pressure between rolls increases as the diameter decreases.
  • the optimum intermediate roll diameter with respect to each work roll diameter increases as the work roll diameter decreases.
  • the limit rolling load capable of maintaining a good plate shape is calculated, and what is added to FIG. 5 is shown in FIG. It is. From FIG. 6, an allowable rolling load that is a guide in actual rolling can be obtained. That is, the smaller numerical value of the two graphs is the allowable rolling load at the work roll diameter. For example, when the work roll diameter is 475 mm, the allowable rolling load is about 1.22 ton / mm due to the contact pressure limit, and when the work roll diameter is 250 mm, the allowable rolling load is about 0.95 ton / mm due to the plate shape limit. Become.
  • FIG. 7 shows the rolling reduction obtained by each work roll diameter when rolling is performed with the allowable rolling load obtained as described above by simulation, and this is added to FIG. 6.
  • the vertical axis on the right side of the figure is the rolling reduction (%).
  • the rolling reduction obtained gradually increases, and eventually reaches a peak around the work roll diameter of 340 mm. Further, it can be seen that the rolling reduction decreases as the work roll diameter is further reduced. Furthermore, when the work roll diameter is in the range of 300 to 400 mm, the rolling reduction is approximately equal to about 14.5 to 15%. However, when the work roll diameter is smaller than 300 mm and larger than 400 mm, it is It was found that the rolling reduction is lower than that. The rolling reduction of about 14.5 to 15% obtained when the working roll diameter is in the range of 300 to 400 mm is about 21 to 25% higher than the rolling reduction of about 12% obtained with the conventional working roll diameter.
  • the work roll diameter will be about 320 to 360mm. In this case, a high reduction ratio of about 15.0% is almost the same as the reduction value of the peak value. You can see that Therefore, it has been found that it is optimal to set the work roll diameter in the range of 320 to 360 mm (about 340 ⁇ 5%) in order to obtain a higher rolling reduction.
  • the intermediate roll diameter is not necessarily an optimum value. That is, as described above, the range of the appropriate work roll diameter of the present invention is 300 to 400 mm, the optimum intermediate roll diameter when the work roll diameter is 300 mm is 630 mm, and the optimum intermediate when the work roll diameter is 400 mm.
  • the roll diameter is 600 mm as shown in FIG. Even when the work roll diameter is 400 mm, the same effect as in the case of 600 mm can be obtained if the intermediate roll diameter is 600 mm or more.
  • the minimum diameter of the intermediate roll required to obtain the maximum effect in a work roll of 300 to 400 mm is 630 mm, which is the larger of 600 mm and 630 mm.
  • a roll has a use range, which is generally about 10%. From this, 1.1 times the intermediate roll 630 mm is about 690 mm, so it can be said that the optimum upper limit of the intermediate roll diameter with respect to the work roll diameter 300 to 400 mm is 630 to 690 mm.
  • FIG. 8 is a diagram showing the same examination result as FIG. 7 in the combination of the intermediate roll diameter and each work roll diameter when the intermediate roll diameter is fixed at a certain value and the work roll diameter is changed.
  • the intermediate roll diameter is 530mm, 550mm, 560mm, 630mm, 690mm.
  • the optimum intermediate roll as described above for the critical rolling load of the inter-roll contact pressure, the critical rolling load of the plate shape, and the rolling reduction ratio.
  • the peak value of the rolling reduction can be obtained when the work roll diameter is in the range of 300 to 400 mm.
  • the appropriate intermediate roll diameter range for work roll diameters of 300 to 400 mm is 560 to 690 mm.
  • FIG. 4 to 8 show the case where the plate material is a high-strength steel plate and the plate width is 1650 mm
  • FIG. 9 shows each work roll when the plate width is changed to 600 mm and 1,900 mm. It is a figure which shows the examination result similar to FIG. 7 in the combination of a diameter and the optimal intermediate
  • the work rolls are the same as in the case of the plate width of 1650 mm in terms of the limit rolling load of the contact pressure between rolls, the limit rolling load of the plate shape, and the rolling reduction. A tendency to a high rolling reduction is obtained in the diameter range of 300 to 400 mm.
  • the diameter of the reinforcing roll used in this simulation was 1370 mm, which is conventionally used in rolling mills with a maximum sheet width of about 1,500 to 1,900 mm.
  • this is only an example.
  • the reinforcing roll diameter is determined from the neck diameter of the reinforcing roll and the size of the neck bearing capable of supporting the required maximum rolling load, other than that The diameter of the reinforcing roll may be sufficient.
  • the present invention can be rolled at a higher reduction ratio than the conventional combination of the work roll diameter and the intermediate roll diameter.
  • the optimum intermediate roll diameter at that time is 620 mm from FIG.
  • the related art is a tandem rolling mill with a work roll diameter of 475 mm, and the optimum intermediate roll diameter at that time is 580 mm as in FIG.
  • FIG. 10 shows the result of a comparative study of the number of necessary stands in the case of the work roll diameter of 340 mm and the conventional work roll of 475 mm in the rolling of a 780 MPa high-tensile steel plate. Looking at the smaller value of the allowable rolling load resulting from the contact pressure and the limit rolling load that can maintain a good plate shape as shown in FIG. 6, when the work roll diameter is 475 mm, it is 1.22 ton / mm. When the work roll diameter is 340 mm, it is 1.13 ton / mm. These are used as a guideline of restriction as an allowable rolling load at each work roll diameter.
  • FIG. 11 shows the reduction ratio and the cumulative reduction ratio at each stand in FIG. 10 by comparing the present invention with the conventional one.
  • the present invention shows the case of a total of 4 stands and the conventional case of a total of 5 stands.
  • the bar graph shows the rolling reduction at each stand, and the hatched lines indicate the present invention, and the white lines indicate the conventional ones. Looking at this, in each stand, the present invention can obtain a rolling reduction 4-5% higher than the conventional one.
  • the line graph shows the cumulative rolling reduction after passing through each stand, the solid line shows the present invention, and the broken line shows the conventional one. Comparing the two, when passing through three stands, the present invention can obtain a cumulative reduction ratio of about 10% as compared with the prior art, and the result is that the number of stands can be reduced.
  • FIG. 12 shows the result of comparative examination of the necessary number of stands in the case of a work roll diameter of 340 mm and a conventional work roll diameter of 475 mm in the rolling of a 1,180 MPa high-tensile steel plate.
  • FIG. 13 shows the comparison between the present invention and the conventional rolling reduction rate and cumulative rolling reduction rate at each stand in FIG. 12, as in FIG.
  • the present invention shows the case of a total of 5 stands and the conventional case of a total of 6 stands.
  • the bar graph shows the rolling reduction at each stand, and the hatched lines indicate the present invention, and the white lines indicate the conventional ones.
  • the present invention can obtain a rolling reduction that is 2 to 3% higher than the conventional one.
  • the line graph shows the cumulative rolling reduction after passing through each stand
  • the solid line shows the present invention
  • the broken line shows the conventional one. Comparing the two, when passing through 4 stands, the present invention can obtain a cumulative reduction ratio of about 8% as compared with the prior art, which is a result of reducing the number of stands.
  • a work roll drive or an intermediate roll drive may be adopted as the rolling mill drive system, but the work roll drive is suitable for the following reasons.
  • an overload prevention device there are a method using a hydraulic torque limiter and a pin called a shear pin that is cut when an overload is applied. Furthermore, another advantage of the work roll drive is that the work roll is driven directly, so there is no drive tangential force to the work roll that occurs in the case of the intermediate roll drive, so that the work roll bends in the horizontal direction. Absent. If the work roll is not bent in the horizontal direction, the original shape control capability of the rolling mill can be exhibited, which is a great merit in terms of product quality.
  • the drive spindle can be designed within the range of the intermediate roll diameter, so that it can be manufactured with sufficient strength for the required torque.
  • the driven intermediate roll may continue to rotate while causing slippage with the work roll. The damage of each roll is very great. In particular, when a plate breakage occurs in a tandem rolling mill, a plurality of stands are affected.
  • the drive tangential force acts on the work roll, and this drive tangential force causes the work roll to bend in the horizontal direction. When the work roll bends in the horizontal direction, it leads to deterioration of the plate shape, which is a big problem in terms of product quality.
  • FIG. 14 is a view of the drive system of the work roll drive system as viewed from the side of the rolling mill
  • FIG. 15 is a schematic longitudinal sectional view of a gear type spindle.
  • the cold rolling mill 51 has a work roll driving device 21 as its driving device.
  • the work roll drive device 21 includes a pair of upper and lower spindles 20, a gear box 52, a coupling 53, and an electric motor 54.
  • the driving force of the electric motor 54 does not decelerate, increase, or change speed at a predetermined rate in the gear box 52.
  • the upper and lower pair of spindles 20 absorb the displacement in the height direction, and are transmitted to the upper and lower pair of work rolls 2.
  • each of the pair of upper and lower spindles 20 includes an intermediate shaft 61 and gear coupling portions 62 and 63 provided at both ends of the intermediate shaft 61.
  • the gear coupling portions 62 and 63 are respectively
  • the outer cylinders 64, 65 having the inner teeth 64a, 65a and the inner cylinders 66, 67 having outer teeth 66a, 67a meshing with the inner teeth 64a, 65a of the outer cylinders 64, 65 are provided.
  • the outer cylinders 64 and 65 are formed with axial recesses 68 and 69 having an oval cross section on the side opposite to the intermediate shaft, and the gear coupling portions 62 and 63 are formed in the recesses 68 and 69 with the shaft end of the work roll 2 and the gear box.
  • the shaft ends of the output shafts 52 are inserted to be connected to the work roll 2 and the output shaft of the gear box 52, respectively.
  • FIG. 16A and 16B are diagrams showing a cross-pin type spindle for comparison, FIG. 16A is a schematic longitudinal sectional view, and FIG. 16B is a sectional view taken along line AA of FIG. 16A.
  • the cross-pin type spindle 20A has cross-pin coupling portions 72 and 73 having cross pins 76 at both ends of the intermediate shaft 71, and the cross-pin coupling portions 72 and 73 have an axial recess with an oval cross section on the side opposite to the intermediate shaft. 74 and 75 are formed, and the cross pin coupling parts 72 and 73 are inserted into the recesses 74 and 75 by inserting the shaft end of the work roll 2 and the shaft end of the output shaft of the gear box 52, respectively. It is connected to the output shaft of the gear box 52.
  • FIG. 17 shows the relationship between the maximum transmission torque of the spindle of the work roll and the outer diameter of the spindle coupling in a conventional unidirectional tandem rolling mill.
  • the solid line is for the gear type spindle and the broken line is for the cross pin type spindle.
  • the gear type has a transmission torque about 1.7 times that of the cross pin type.
  • the spindle is also reduced in diameter. Therefore, a gear type having a large transmission torque even if the spindle is small is preferable.
  • FIGS. 18A and 18B show a general arrangement of gear coupling portions of a pair of upper and lower spindles
  • FIG. 18B shows an arrangement of gear coupling portions that can improve the spindle strength.
  • the one-dot chain line is the gear center position of the gear coupling portion.
  • the rolling mill side gear coupling portions of the pair of upper and lower spindles 20 align the axial direction positions of the gear coupling portions 62 so that the gear center positions coincide with each other vertically. It is configured.
  • the distance between the axes of the upper and lower spindles is L, and the diameter of the coupling part 62 is D1.
  • the gear coupling portions 62A of the pair of upper and lower spindles 20A are shifted up and down and arranged in a staggered manner, and the gear center position is shifted up and down. Configure the coupling part.
  • the distance between the axes of the upper and lower spindles is L, and the diameter of the coupling portion 62A is D2.
  • FIG. 19A is a diagram showing a work roll drive device provided with a spindle type hydraulic torque limiter as an overload prevention device.
  • the work roll drive device 21 ⁇ / b> A has a hydraulic torque limiter 85 between the gear coupling portion 63 of the pair of upper and lower spindles 20 and the upper and lower output shafts of the gear box 52.
  • the upper and lower output shafts are connected via a hydraulic torque limiter 85.
  • FIG. 19B is a diagram showing a work roll drive device provided with a coupling type hydraulic torque limiter as an overload prevention device.
  • the work roll driving device 21B has a hydraulic torque limiter 86 between the input shaft of the gear box 52 and the output shaft of the electric motor 54.
  • the input shaft of the gear box 52 is coupled to the output shaft of the electric motor 54 with the coupling 53 and the hydraulic pressure.
  • a torque limiter 86 is connected.
  • FIG. 19C is a diagram showing a configuration in which a shear pin is provided in a coupling that connects an input shaft of a gear box to an electric motor as an overload prevention device.
  • the coupling 53 includes coupling halves 53c and 53d having flange portions 53a and 53b, and shear pins 87 are provided on the flange portions 53a and 53b.
  • the work roll When a plate breakage occurs, the work roll may stop suddenly when the broken steel plate is bitten so as to be folded between the upper and lower work rolls or wound around the work roll. In such a state, in the case of work roll drive, an overload immediately acts on the drive system that transmits torque from the electric motor 54 to the gear box 52 and the spindle 20, so it is installed in the middle of the drive system.
  • the overload prevention device (hydraulic torque limiter 85, 86 or shear pin 87) is activated, the torque transmitted to the work roll is cut off, and the rolling mill can be stopped.
  • the overload prevention device indicated by 19A, 19B, and 19C is an effective means for protecting the spindle in a situation where the strength of the spindle itself must be reduced as the work roll diameter decreases. .
  • the spindle on which the overload prevention device is installed is a gear type, but the overload prevention device may be applied to a cross pin type spindle.
  • an intermediate roll offset device 19 is provided in the roll shift device 23 (FIG. 3).
  • the intermediate roll offset device 19 will be described again.
  • an intermediate roll offset device 19 is incorporated in the shift block 12 of the roll shift device 23.
  • an operation method of the intermediate roll offset device 19 a method using a hydraulic cylinder, a method using a screw jack, a method using a wedge plate, and the like can be considered.
  • the intermediate roll offset device 19 further includes an intermediate roll bending device 11 that applies vertical bending to the intermediate roll.
  • the intermediate roll 3, the shift block 12, and the intermediate roll offset device 19 are structured to always shift simultaneously in the roll longitudinal direction.
  • the intermediate roll offset device 19 is operated in the rolling direction by means such as a hydraulic cylinder, a screw jack, and a wedge plate, and this operation amount is detected by a position detector.
  • Each of the intermediate roll offset devices 19 is controlled up and down alone or simultaneously.
  • the position of the roll vertical bending device 11 is always “L1” from the center of the intermediate roll 3, and the intermediate roll also in the roll longitudinal direction. Since the center of the offset device 19 is aligned with the center of the bearing of the bearing housing 9, an offset load is not applied to the bearing of the bearing housing 9.
  • this work roll offset device also has a roll bending device built in, a hydraulic cylinder, a screw jack, a wedge plate, etc. can be applied as operation means, and the operation amount is detected by a position detector. is there.
  • the present invention relates to the reduction of the diameter of the work roll, but it is well known that, in general, when the diameter of the work roll is reduced, bending tends to occur in the horizontal direction during rolling. As described above, it is effective from the viewpoint of stable operation to take measures for suppressing horizontal deflection as much as possible.
  • the horizontal force acting on the work roll is roughly classified into the following four types, and the direction and magnitude of the deflection are actually determined by the resultant force.
  • (a), (b), and (c) are determined by the rolling conditions in operation, and it is possible to grasp the value, but it is difficult to change intentionally.
  • (d) is determined by the rolling load and the offset, and the rolling load is difficult to change intentionally, as in (a) to (c), but if the offset can be changed, the value can be changed by a horizontal force. is there.
  • an offset device is provided in the rolling mill so that the horizontal force acting on the work roll can be operated. Specifically, the resultant force of the horizontal force (a), (b), (c) and the rolling load are grasped in advance, and the resultant force of (a), (b), (c) and (d) are balanced. If the offset size is determined, the horizontal force acting on the work roll can theoretically be zero. However, in actual rolling, it is difficult to accurately grasp (a), (b), (c), and since each value changes with time, it cannot be completely zeroed. Theoretically, the offset is usually set so as to leave a certain level of horizontal force.
  • 20A and 20B are diagrams showing the two types of offset methods.
  • the offset is to relatively shift the center of the work roll and the center of the intermediate roll. Therefore, as shown in FIG. 20A, the work roll is moved in the horizontal direction to add the offset, As shown in 20B, a method of adding an offset by moving the intermediate roll in the horizontal direction is conceivable.
  • the work roll offset or the intermediate roll offset may be adopted, but the intermediate roll offset is preferable in consideration of the comparison result as described above.
  • FIG. 21 is a view of an intermediate roll drive type drive system as viewed from the side of the rolling mill.
  • the roll configuration of the cold rolling mill 51A is the same as that of the embodiment shown in FIGS.
  • the cold rolling mill 51A of this Embodiment has the intermediate roll drive device 22 as the drive device.
  • the intermediate roll driving device 22 includes a pair of upper and lower spindles 90, a gear box (reduction gear) 94, a coupling 95, and an electric motor 96.
  • the driving force of the electric motor 96 is reduced or increased at a predetermined rate in the gear box 94 or The speed is not changed, and the displacement in the height direction is absorbed by the pair of upper and lower spindles 90 and transmitted to the pair of upper and lower intermediate rolls 3.
  • the pair of upper and lower spindles 90 are, for example, the cross pin type spindles described with reference to FIGS. 14A and 14B, and each have an intermediate shaft 91 and cross pin coupling portions 92 and 93 provided at both ends of the intermediate shaft 91. ing.
  • the cross-pin type spindle 90 has the advantage that it is less expensive than the gear spindle.
  • the cold rolling mill 51A has a roll offset capable of offsetting one of the intermediate roll 3 and the work roll 2 to the entry side or the exit side in the rolling direction with respect to the axis of the other roll.
  • the roll offset device is preferably an intermediate roll offset device as in the embodiment shown in FIGS. 1 to 3, but may be a work roll offset device.
  • FIG. 22 is a diagram showing an embodiment of a tandem rolling facility constructed using the cold rolling mill of the present invention.
  • the tandem rolling mill has a rolling mill row composed of five stands of rolling mills 100a to 100e, and all of the rolling mills 100a to 100e are the above-described cold rolling mills of the present invention, for example, the cold rolling mill 51 (FIG. 14). It is comprised by.
  • This makes it possible to maintain the high productivity of conventional tandem rolling equipment and to roll steel plates that are harder than before without increasing the number of stands, and even steel plates of the same hardness can be rolled at a higher reduction rate. It becomes.
  • the rolling mills 100a to 100e may be configured to include at least one stand of the cold rolling mill of the present invention. Even in this case, all of the rolling mills 100a to 100e can be rolled at a higher rolling reduction than the rolling equipment composed of conventional rolling mills. Is possible.
  • FIG. 23 is a diagram showing an example of an embodiment of a reversible rolling facility configured using the cold rolling mill of the present invention.
  • the reversible rolling equipment has a single reversible cold rolling mill 110, and coil winding / unwinding devices 111, 112 are arranged on the input / output side of the rolling mill 110, and the rolling mill 110 and the winding / unwinding device 111 are arranged. , 112 are provided with deflector rolls 113, 114.
  • the rolling mill 110 is comprised by the cold rolling mill mentioned above of this invention, for example, the cold rolling mill 51.
  • the reversible rolling equipment may have a two-stand rolling mill, and at least one of the two stands may be the above-described cold rolling mill of the present invention, for example, the cold rolling mill 51, so that all conventional Rolling at a high reduction rate is possible compared to rolling equipment composed of a rolling mill.
  • FIG. 24 is a diagram showing a modification example of the tandem rolling equipment performed using the cold rolling mill of the present invention.
  • the tandem rolling mill before the modification has a rolling mill row composed of five conventional rolling mills 120a to 120e.
  • the final rolling mill 120e is used as the above-described cold rolling of the present invention.
  • a cold rolling mill 51 is used.
  • the entire one-stand rolling mill may be replaced, or the one-stand rolling mill may be partially modified.
  • the high productivity of the tandem rolling equipment before the modification is maintained, and the rolling of the steel plate that is harder than before the modification and the rolling with the higher reduction ratio is possible even with the same hardness steel plate without increasing the number of stands. It becomes possible.
  • the number of rolling mills to be changed may be two stands or more.
  • FIG. 25 is a diagram showing another modification of the tandem rolling equipment performed using the cold rolling mill of the present invention.
  • the tandem rolling equipment before remodeling has a rolling mill row consisting of five conventional rolling mills 120a to 120e, and in the illustrated remodeling example, the cold rolling described above of the present invention is provided on the outlet side of the rolling mill row.
  • a machine, for example, a cold rolling mill 51 is additionally installed.
  • the position where the rolling mill of the present invention is additionally installed may be on the entry side or both sides of the rolling mill row.
  • the reversible rolling equipment shown in FIG. 23 is modified in the same manner as the tandem rolling equipment by changing the reversible cold rolling mill 110 to the above-described cold rolling mill of the present invention. Is possible. This makes it possible to roll a steel plate that is harder than before and to roll at a higher reduction rate even with a steel plate having the same hardness using existing equipment.

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

Abstract

Afin de réduire le diamètre des cylindres de travail d'un laminoir à six cages et d'ainsi permettre le laminage d'une tôle d'acier ayant une dureté sans précédent et de permettre le laminage d'une tôle d'acier ayant une dureté conventionnelle mais soumise à une plus forte réduction de laminage et d'empêcher une baisse de la production due à l'utilisation d'un laminoir ayant un petit cylindre de travail, tel qu'un train multi-cage du type en faisceau, un laminoir à froid (51), qui lamine une tôle (1) ayant une largeur de plaque supérieure ou égale à 600 mm et une largeur maximale de plaque de 1.500 à 1.900 mm, est équipé de: une paire de cylindres de travail (2), supérieur et inférieur, qui laminent le matériau laminé (1); une paire de cylindres intermédiaires (3), supérieur et inférieur, qui soutiennent chacun des cylindres de travail (2); une paire de cylindres de renfort (4), supérieur et inférieur, qui soutiennent chacun des cylindres intermédiaires (3); des dispositifs (23) de changement de direction axiale pour les cylindres intermédiaires (3); et des dispositifs de cintrage (10, 11) pour les cylindres de travail (2) et les cylindres intermédiaires (3). Le diamètre des cylindres de travail (2) est fixé entre 300 et 400 mm et le diamètre des cylindres intermédiaires (3) est fixé entre 560 et 690 mm.
PCT/JP2011/071391 2011-09-20 2011-09-20 Laminoir à froid, installation de laminage en tandem, installation de laminage réversible, procédé de modification d'une installation de laminage et procédé d'exploitation d'un laminoir à froid WO2013042204A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
JP2011554001A JP4928653B1 (ja) 2011-09-20 2011-09-20 冷間圧延機、タンデム圧延設備、可逆圧延設備、圧延設備の改造方法および冷間圧延機の運転方法
CN201180018331.2A CN103118813B (zh) 2011-09-20 2011-09-20 冷轧机、串列轧制设备、可逆轧制设备、轧制设备的改造方法以及冷轧机的运转方法
BR112012027654-9A BR112012027654B1 (pt) 2011-09-20 2011-09-20 Laminador a frio para laminar uma tira de aço, sistemas de laminação em tandem e de laminação inversor, e, métodos de modificação de um sistema de laminação e operacional de um laminador a frio
PCT/JP2011/071391 WO2013042204A1 (fr) 2011-09-20 2011-09-20 Laminoir à froid, installation de laminage en tandem, installation de laminage réversible, procédé de modification d'une installation de laminage et procédé d'exploitation d'un laminoir à froid
KR1020127032141A KR101424375B1 (ko) 2011-09-20 2011-09-20 냉간 압연기, 탠덤 압연 설비, 가역 압연 설비, 압연 설비의 개조 방법 및 냉간 압연기의 운전 방법
EP12184124.1A EP2572808B1 (fr) 2011-09-20 2012-09-12 Laminoir à froid, système de laminage en tandem, système de roulement d'inversion, procédé de modification d'un système de roulement et procédé de fonctionnement d'un laminoir à froid

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PCT/JP2011/071391 WO2013042204A1 (fr) 2011-09-20 2011-09-20 Laminoir à froid, installation de laminage en tandem, installation de laminage réversible, procédé de modification d'une installation de laminage et procédé d'exploitation d'un laminoir à froid

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JP (1) JP4928653B1 (fr)
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JP2017060969A (ja) * 2015-09-25 2017-03-30 Ｊｆｅスチール株式会社 冷間タンデム圧延機及び高強度冷延鋼板の製造方法
JP2020163400A (ja) * 2019-03-28 2020-10-08 Ｊｆｅスチール株式会社 タンデム圧延設備におけるロールオフセット量の上限値の設定方法及び設定装置
WO2021205548A1 (fr) * 2020-04-07 2021-10-14 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ 株式会社 Laminoir, procédé de fabrication de laminoir, et procédé de modification de laminoir
CN114786832A (zh) * 2019-12-11 2022-07-22 Sms集团有限公司 用于热轧机和用于制造金属扁平产品的热轧机架、热轧机以及用于运行热轧机的方法

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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
US20220118492A1 (en) * 2020-10-21 2022-04-21 Digi Drives Private Limited Cold rolling mill
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JP2017018971A (ja) * 2015-07-08 2017-01-26 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ株式会社 圧延機および圧延方法
US10421106B2 (en) 2015-07-08 2019-09-24 Primetals Technologies Japan, Ltd. Rolling mill and rolling method
JP2017060969A (ja) * 2015-09-25 2017-03-30 Ｊｆｅスチール株式会社 冷間タンデム圧延機及び高強度冷延鋼板の製造方法
JP2020163400A (ja) * 2019-03-28 2020-10-08 Ｊｆｅスチール株式会社 タンデム圧延設備におけるロールオフセット量の上限値の設定方法及び設定装置
JP6992783B2 (ja) 2019-03-28 2022-01-13 Ｊｆｅスチール株式会社 タンデム圧延設備におけるロールオフセット量の上限値の設定方法及び設定装置
CN114786832A (zh) * 2019-12-11 2022-07-22 Sms集团有限公司 用于热轧机和用于制造金属扁平产品的热轧机架、热轧机以及用于运行热轧机的方法
WO2021205548A1 (fr) * 2020-04-07 2021-10-14 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ 株式会社 Laminoir, procédé de fabrication de laminoir, et procédé de modification de laminoir
CN114340811A (zh) * 2020-04-07 2022-04-12 普锐特冶金技术日本有限公司 轧机、轧机的制造方法及轧机的改造方法

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EP2572808B1 (fr) 2014-05-21
CN103118813B (zh) 2016-01-20
JPWO2013042204A1 (ja) 2015-03-26
CN103118813A (zh) 2013-05-22
KR101424375B1 (ko) 2014-07-31
BR112012027654B1 (pt) 2018-03-13

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