Classifications

• • 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
  • B21B37/007—Control for preventing or reducing vibration, chatter or chatter marks
• • 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
  • B21B1/26—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 hot-rolling, e.g. Steckel hot mill

Definitions

• the subject invention relates to a method and apparatus for reducing vibrations due to a flat spot of a Steckel drum in a Steckel mill, wherein between Steckel drum of the Steckel furnace and drivers of the rolling stand a anstell ⁇ bare role is arranged, which is brought into engagement with the rolling stock.
• Vibrations occur in a Steckel mill known manner in that a Steckel drum is indeed cylindrical, but along the Steckel drum has a slot which serves to receive the Walzgutkopfes (tape head). This slot is connected with corre sponding transition radii with the cylindrical shell of the Steckeltrommel, so that the peripheral contour of the aufspachelten on the Steckel drum Walzguts is not nik ⁇ , but has a flat, which corresponds to a chord.
• EP-A-1180402 A solution to this problem is proposed by EP-A-1180402, where a movable driver roller alters the length of the path of the rolling stock, depending on the angle of rotation of the Steckel drum.
• the angular position of the flat position of the Steckel drum or its flat location is determined and from this the necessary position of the driver roller, which also depends on the position of the deflection roller, is determined.
• An object of the present invention is therefore to simplify the previously known method for reducing vibrations with regard to the control.
• the object is achieved by a method according to claim 1 or by a device according to claim 8.
• the fact that the force exerted by the roller on the rolling stock is controlled to a predetermined value, that is, the roller is pressed against the rolling stock with a predetermined force, it is ensured that on reaching the flat when reeling the strip tension drop by moving the Roll against the tape, which is due to the given force on the role is weakened. In this case, no influence is exerted on the drive control of the Steckel drum or on the Bandzugregelung, this works without coupling with the regulation of the force on the role.
• the belt tension is usually controlled by the drives of the two work rolls of the Waiszüsts and the drives of the two Steckeltrommeln.
• the speed of the Steckel ⁇ drums results, for example, from the rolling speed and the current Bund ⁇ diameter, the torque of the Steckeltrommeln from the specified strip tension and the collar diameter.
• the deflection of the roller at the flat causes a geometric change of Kraft ⁇ attack.
• the force on the roll remains the same, it changes only the point of application of the force on the rolling stock. Depending on the direction of the deflection, this means that the predetermined force on the roller causes a slight change in the strip tension.
• a possible embodiment of the invention provides that the force is kept constant during one or more revolutions of the Steckeltrommel.
• the strip tension decreases. Due to the constant contact force on the roller, the roller moves until it is in balance with the rolling stock in a new position. By slightly changing the position, the angle between the two rolling stock sections located before and after the roll decreases. With a constant force, the adjusting device causes the Anstellmoment is reduced at Bandzugsabfall, with An increase in tension the Anstellmoment is increased. However, it can be achieved that the strip tension does not become zero. As a rule, the strip tension is selected as a function of the rolling stock thickness (strip thickness), the temperature, the thickness, the width and the material properties of the rolling stock, which will not be discussed in more detail here since this belongs to general expert knowledge.
• Another possible solution provides that a constant force for a period of one or more revolutions of the Steckel drum force during a certain period of each revolution, an additional force is switched. This can be achieved by increasing the constant force for a certain period of time in advance of the appearance of the strip draft drop, and after this time period back to the original constant Value is lowered. In any case, the drop in the strip tension can be compensated for more quickly than in the case of the constant force during one revolution.
• the anticipatory Auf ⁇ circuit of an additional force can even better compensate for the inertia of the role.
• the time span of switching on the additional force corresponds to about 1/3 of the duration of the unwinding or coiling of the rolling stock on the flat.
• the force is changed depending on the collar diameter of the rolling stock on the Steckeltrommel. That is, the force remains e.g. During a revolution of the Steckel drum is substantially constant and is continuously larger or smaller with increasing collar diameter. In the case of execution of the periodic connection of an additional force also continuously increases the constant force, the additional power not.
• the force on the roller and the force exerted on the roller by the strip tension and the wrapping of the rolling stock are in equilibrium.
• the collar diameter increases or decreases, the spatial position of the rolling stock between roller and Steckeltrommel and thus the balance of power changes so that the force on the role or the spatial position of the role is changed to restore the former balance of power.
• the necessary change in the force can be determined or calculated from the force parallelogram from the forces acting on the roll (strip tension and contact force on the roll).
• the force on the roller is predetermined both as a function of the belt tension and of the belt diameter, then the force can be chosen such that it balances the momentary tension of the belt tensioner and the roller only briefly maintains its position during the belt tension fluctuation changes and then returns to the original -A-
• the force is usually chosen so that it cancels the force exerted by the predetermined strip tension on the roller force in a predetermined position of the roller.
• the variable position of the roll one determines the necessary force due to the geometrical conditions (arrangement of the rolling stock relative to the roll), e.g. at the beginning of the hasp pelvorganges due to the predetermined strip tension from the force parallelogram.
• the force on the roller during the reel operation is continuously adapted to the changing geometric conditions due to the increase or decrease in the diameter of the band tensioner acting on the reel with the aid of the parallelogram of forces.
• roller and / or its bearings such as a swivel arm
• the roller and / or its bearings is hydraulically operated, has the advantage that the employment can be faster and more accurate compared to the pneumatic employment or employment by means of an engine.
• the roller Due to the fact that the roller is moved substantially normal to the plane of the rolling stock between the driver and the driver, the largest possible effect is achieved with a low deflection of the roller.
• the employment of the role can be effected by obliquely aligned to this plane adjusting cylinder.
• the device for carrying out the method may comprise at least one preferably hydraulic setting cylinder, which acts on the bearing of the roller, for example a pivoting arm.
• the adjusting cylinder advantageously has a position-measuring device for determining the starting position and for checking the position of the roller during the reeling operation.
• the adjusting cylinder can have both a rod side and a piston side via a pressure measuring device, which has the advantage that the actual pressures can be monitored.
• a roll which has a low mass inertia.
• the role is designed as a tube.
• a ratio of wall thickness of the tube to outer tube diameter of about 1:10 is considered.
• Fig. 1 shows a schematic representation of a Steckel mill.
• Fig. 2 shows the position of the roll before and during a Bandzugabfalls during coiling.
• Fig. 3 shows the position of the roll before and during a Bandzuganieris during uncoiling.
• an additional adjustable roller 3 is arranged between the capping drum 1 of the so-called plug-in furnace (Coiler) and the drivers 2 arranged upstream of or behind the rolling stand 5.
• the roller is mounted in a pivoting arm and in engagement with the rolling stock 6.
• the drivers 2 are at this time opened with the fixed position of the upper drive roller.
• the threading slot 7 of the Steckel drum 1 necessitates a flat spot for the rolled-up rolling stock 6.
• Fig. 2 shows in left top in position a) a device according to the invention before the caused by the flat strip tension drop and bottom left in position b) during the Bandzugsabfalls.
• the Steckel drum 1 rotates counterclockwise in accordance with the arrow indicated about the rotation axis and winds up the rolling stock 6.
• the roller 3 is mounted at both ends on a pivoting arm 4, on each of which a hydraulic Anstell ⁇ cylinder 8 attacks.
• the two pivot arms 4 are pivotable about the pivot axis 9 and connected to each other in the area.
• the acting band train is represented by vectors 10.
• the resultant strip tension acting on the roller 3 results from the parallelogram of forces shown in the figure, in which the force 11 which is opposite to the resultant from the strip tension 10 but of equal magnitude must be applied by the adjusting cylinder 8 to the roller at that time. can be removed.
• the drive control of the Steckel drum 1 responds to the strip draw drop by increasing the rotational speed and the roll 3 is pulled back to the zero position before the strip draw. This ensures that the roll 3 is always in the starting position of the roll during coiling Passage of the flat returns, provided that the force on the role of the current 3 Bandzugultultierenden (as a function of the Bund josmes ⁇ sers) is adjusted. Otherwise (variable position of the roll) applies. that the roller continuously increases from a lower position to an upper position in accordance with the constant force of the adjusting cylinder 8.
• the flat part of the Steckel drum 1 causes a lengthening of the rolling stock 6 and thus a strip draft drop.
• the roller 3 is lowered by the Walz ⁇ good 6.
• the geometry of the articulation of the hydraulic setting cylinder 8 has been selected such that the lever arm of the cylinder force is reduced relative to the center of gravity of the pivoting arm 4, thereby slightly reducing the strip tension despite deflection of the pivoting arm 4.
• the torque control of the Steckel drum 1 reacts with an increase in the speed until the desired strip tension is restored.
• the roll 3 is thereby returned to its position before the strip tension reduction.
• FIG. 3 shows, analogously to FIG. 2, top left in position a), a device according to the invention before the strip tension increase caused by the flat position and, at the bottom left, in position b) during the strip tension increase.
• the geometry of the articulation of the hydraulic setting cylinder was chosen so that the lever arm of the cylinder force is magnified magnified ßert based on the center of gravity of the pivot arm 4 and thereby despite deflection of the pivot arm 4, the strip tension is slightly increased.
• the torque control of the Steckel drum 1 reacts with a reduction in the speed until the desired strip tension is restored.
• the roller 3 is therefore returned to its position before the strip tension increase.

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Metal Rolling (AREA)
• Winding, Rewinding, Material Storage Devices (AREA)
• Control Of Metal Rolling (AREA)
• Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
• Manufacture Of Motors, Generators (AREA)
• Vibration Prevention Devices (AREA)
• Crushing And Grinding (AREA)

Priority Applications (7)

Applications Claiming Priority (2)

Publications (1)

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ID=34970395

Family Applications (1)

Country Status (9)

Cited By (1)

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Citations (4)

Family Cites Families (5)

• 2004
  • 2004-07-07 AT AT0114404A patent/AT502723B1/de not_active IP Right Cessation
• 2005
  • 2005-06-17 CN CN2005800230765A patent/CN1984729B/zh not_active Expired - Fee Related
  • 2005-06-17 WO PCT/EP2005/006561 patent/WO2006002783A1/de active Application Filing
  • 2005-06-17 JP JP2007519652A patent/JP2008504969A/ja not_active Ceased
  • 2005-06-17 PL PL05752303T patent/PL1763410T3/pl unknown
  • 2005-06-17 EP EP05752303A patent/EP1763410B1/de not_active Revoked
  • 2005-06-17 AT AT05752303T patent/ATE414574T1/de not_active IP Right Cessation
  • 2005-06-17 DE DE502005006011T patent/DE502005006011D1/de active Active
  • 2005-06-17 BR BRPI0513148-0A patent/BRPI0513148A/pt not_active IP Right Cessation
  • 2005-06-17 CA CA002572986A patent/CA2572986A1/en not_active Abandoned
• 2012
  • 2012-03-22 JP JP2012065725A patent/JP2012110969A/ja active Pending

Patent Citations (4)

Non-Patent Citations (2)

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