CA2572986A1 - Method and device for reducing vibrations in a steckel mill - Google Patents
Method and device for reducing vibrations in a steckel mill Download PDFInfo
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- CA2572986A1 CA2572986A1 CA002572986A CA2572986A CA2572986A1 CA 2572986 A1 CA2572986 A1 CA 2572986A1 CA 002572986 A CA002572986 A CA 002572986A CA 2572986 A CA2572986 A CA 2572986A CA 2572986 A1 CA2572986 A1 CA 2572986A1
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- roll
- steckel
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- rolling stock
- strip tension
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- 238000000034 method Methods 0.000 title claims abstract description 15
- 238000005096 rolling process Methods 0.000 claims abstract description 42
- 230000001105 regulatory effect Effects 0.000 claims description 4
- 238000009530 blood pressure measurement Methods 0.000 claims description 2
- 238000005259 measurement Methods 0.000 claims 1
- 230000033228 biological regulation Effects 0.000 description 9
- 230000008859 change Effects 0.000 description 5
- 230000009467 reduction Effects 0.000 description 3
- 238000011144 upstream manufacturing Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 230000005484 gravity Effects 0.000 description 2
- 230000000737 periodic effect Effects 0.000 description 2
- 238000004904 shortening Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
- 239000013598 vector Substances 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
Classifications
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- 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
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Metal Rolling (AREA)
- Winding, Rewinding, Material Storage Devices (AREA)
- Vibration Prevention Devices (AREA)
- Crushing And Grinding (AREA)
- Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
- Manufacture Of Motors, Generators (AREA)
- Control Of Metal Rolling (AREA)
Abstract
The invention relates to a method and a corresponding device for reducing vibrations that are caused by a flat spot of a Steckel roll (1) in a Steckel mill. An adjustable roll (3) is mounted between the Steckel roll (1) of the Steckel furnace and the driver (2) of the roll stand (5) and can be contacted with the rolling stock (6). The invention is characterized in that the force which is exerted onto the rolling stock (6) by the roll (3) is adjusted to a defined value.
Description
Method and device for reducing vibrations in a Steckel mill The present invention relates to a method and a device for reducing vibrations due to a flat spot on a Steckel roll in a Steckel mill, an advanceable roll which is brought into engagement with the rolling stock being arranged between the Steckel roll of the Steckel furnace and the driver of the roll stand.
Oscillations arise in a Steckel mill in a known way in that, although a Steckel roll is cylindrical, it has, along the Steckel roll, a slot which serves for receiving the rolling stock head (strip head). This slot is connected by means of corresponding transition radii to the cylindrical casing of the Steckel roll, so that the circumferential contour of the rolling stock coiled on the Steckel roll is not circular, but has a flat spot which corresponds to a chord.
During the coiling or uncoiling of the rolling stock, therefore, at the flat spot in each case a strip tension drop occurs, which corresponds to a lengthening of the rolling stock portion located between the Steckel roll and the roll stand, or, respectively, a strip tension rise occurs, which corresponds to a shortening of the rolling stock portion located between the Steckel roll and the roll stand. In the event of a strip tension drop, the strip tension may in this region become very low or even zero.
A solution to this problem is proposed in EP-A-1180402, where a movable driver roll varies the length of travel of the rolling stock, specifically as a function of the rotary angle of the Steckel roll. However, it is necessary, here, that the angular position of the flat spot of the Steckel roll or its flat spot is determined and that the necessary position of the driver roll, which also depends on the position of the deflecting roll, is determined from this.
PCT/EP2005/006561 - la -An object of the present invention, then, is to simplify the known method for reducing vibrations in terms of regulation.
The object is achieved by means of a method according to claim 1 and by means of a device according to claim 8.
Since the force which the roll exerts on the rolling stock is regulated to a predetermined value, that is to say the roll is pressed with predetermined force against the rolling stock, this ensures that, when the flat spot is reached, during coiling, the strip tension drop is attenuated due to the displacement of the roll with respect to the strip, this taking place by virtue of the predetermined force on the roll.
In this case, no influence is exerted on the drive control of the Steckel roll or on the strip tension regulation, this operating without any coupling to the regulation of the force on the roll. As a rule, the strip tension is regulated via the drives of the two working rolls of the roll stand and the drives of the two Steckel rolls. The rotational speed of the Steckel rolls is obtained, for example, from the rolling speed and the current coil diameter, the torque of the Steckel rolls being obtained from the predetermined strip tension and the coil diameter.
The deflection of the roll at the flat spot causes a geometric change in the force action. The force on the roll remains the same, only the point of actiqn of the force on the rolling stock changing. Depending on the direction of deflection, this means that the predetermined force on the roll entails a slight change in the strip tension.
The regulation of the drive of the Steckel roll can, after the flat spot has been passed, compensate the length error of the rolling stock by a change in rotational speed (with the aim of keeping the torque constant in terms of the strip tension) and can thereby draw the roll back into the initial position which the roll had upstream of the flat spot. This takes place automatically by means of the existing regulation of the Steckel roll.
In one possible implementation of the invention, the force is kept constant during one or more revolutions of the Steckel roll.
If, therefore, too little strip is for a short time wound up during the coiling of the rolling stock when the latter passes through at the flat spot, the strip tension falls. Due to the constant advancing force on the roll, the roll is displaced until it is in force equilibrium with the rolling stock in a PCT/EP2005/006561 - 2a -new position. Due to the slight variation in position, the angle between the two rolling stock portions located upstream and downstream of the roll decreases. In the case of a constant force, the advancing device causes the advancing moment to be reduced in the event of a strip tension drop and causes the advancing moment to be increased in the event of a strip tension rise. However, what can be achieved is 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, this not being discussed in any more detail here because it is part of general specialized knowledge.
In another possibility for a solution, during a specific time span of each revolution, an additional force is added to a force which is constant for the duration of one or more revolutions of the Steckel roll. This may be achieved in that the constant force is increased for a specific time span prior to the occurrence of the strip tension drop and is lowered to the original constant value again after this time span. In any event, the drop in strip tension can be compensated more quickly than in the case of a force which is constant during a revolution. The prior addition of an additional force can in this case compensate the inertia of the roll even better.
The time span for the addition of the additional force corresponds to approximately 1/3 of the duration of the uncoiling or coiling of the rolling stock over the flat spot.
To determine the adding of the additional force, the angular position of the Steckel roll or of the flat spot can be determined.
Further, there may be provision for changing the force as a function of the coil diameter of the rolling stock on the Steckel drum. That is to say, for example, the force remains essentially constant during, a revolution of the Steckel roll and becomes continuously higher or lower with an increasing coil diameter. In the embodiment involving the periodic addition of an additional force, the constant force likewise rises continuously, but not the additional force.
In a given position of the roll, the force on the roll and the force exerted on the roll by the strip tension and the looping of the rolling stock are in equilibrium. If, then, the coil diameter rises or falls, the spatial position of the rolling stock between roll and Steckel roll and therefore also the force equilibrium change, so that, to restore the earlier force equilibrium, the force on the roll or the spatial position of the roll is changed. The necessary change in the for'ce can be determined or calculated from the force- parallelogram: formed from the forces on the roll (strip tension and advancing force on the roll).
There are therefore two possible solutions: either the force on the roll is dependent only on the strip tension resultant at a PCT/EP2005/006561 - 3a -specific time point and is therefore essentially constant (with the exception of the periodic additional force applied if appropriate) over the entire coiling duration, and then, for example during coiling, due to the increase in coil diameter the strip tension resultant at the roll becomes increasingly higher and the roll is increasingly forced further out of the path of the rolling stock. Thus, with the exception of deflection due to the flat spot of the Steckel roll, the position of the roll is variable, the roll traveling continuously from an initial position at the start of the coiling operation to a final position at the end of the coiling operation.
Or the force on the roll is predetermined both as a function of the strip tension and as a function of the coil diameter, and then the force can be selected such that it maintains the equilibrium with the instantaneous strip tension resultant, and the roll changes its position briefly during the strip tension fluctuation only and thereafter returns again into the initial position before strip tension fluctuation.
The spatial position of the roll therefore remains fixed during the entire coiling or uncoiling operation, with the exception of deflection due to the flat spot on the Steckel roll.
As a rule, the force is selected such that, in a predetermined position of the roll, this force cancels the force exerted on the roll by the predetermined strip tension. In the first case of the variable position of the roll, the necessary force is determined on the basis of the geometric conditions (arrangement of the rolling stock in relation to the roll), for example at the start of the coiling operation on the basis of the predetermined strip tension arising from the force parallelogram.
In the second case of the fixed position of the roll, with the aid of the force parallelogram the force on the roll is adapted continuously during the coiling operation to the changing geometric conditions due to the increase or decrease in the coil diameter of the strip tension resultant acting in each case on the roll.
The fact that the roll and/or its bearings, such as, for example, a pivoting arm, are advanced hydraulically has the advantage that the advance can take place more quickly and more accurately, as compared with pneumatic advancing or advancing by means of a motor.
Since the roll is moved essentially perpendicularly with respect to the plane of the rolling stock located between the Steckel roll and the driver, a maximum possible effect is achieved with a low deflection of the roll. However, the advance of the roll may be brought about by advancing cylinders oriented obliquely with respect to this plane.
PCT/EP2005/006561 - 4a -The device for carrying out the method may comprise at least one preferably hydraulic advancing cylinder which engages on the mounting of the roll, for example a pivoting arm.
The advancing cylinder advantageously has a position measuring device for determining the starting position and for monitoring the position of the roll during-the coiling operation.
Further, the advancing cylinder may have a pressure measurement device both on the rod side and on the piston side, the advantage of this being that the actual pressures can be monitored.
So that strip tension fluctuations can be compensated quickly by means of the roll according to the invention, a roll which has low mass inertia is to be provided. For this purpose, there may be provision for the roll to be designed as a tube. A ratio of the wall thickness of the tube to the outside tube diameter of about 1:10 is considered sufficiently stable.
It proves advantageous for the hydraulics if the roll is mounted on a pivoting arm on which the advancing cylinder engages, the lever arm of the advancing cylinder with respect to the axis of the pivoting arm being smaller than the distance between the roll axis and the axis of the pivoting arm. As a result, the advancing cylinder has to execute only movements with a lower speed than that of the roll, so that advancing cylinders with smaller valves and with shorter switching times can be used.
The invention is explained, with reference to an example, by means of the following figures 1 to 3:
Fig. 1 shows a diagrammatic illustration of a Steckel mill.
Fig. 2 shows the position of the roll before and during a strip tension drop during coiling.
Fig. 3 shows the position of the roll before and during a strip tension rise during uncoiling.
According to fig. 1, an additional advanceable roll 3 is arranged between the Steckel roll 1 of what is known as the Steckel furnace (coiler furnace) of the drivers 2 arranged upstream and downstream of the roll stand 5. The roll is mounted in a pivoting arm and is in engagement with the rolling stock 6. The drivers 2 are open at this time point with a fixed position of the upper driver roll. The threading-in slot 7 of the Steckel roll 1 causes a flat spot for the'coiled rolling stock 6.
Fig. 2 shows at top left, in position a), a device according to the invention before the strip tension drop caused by the flat spot and at bottom left, in position b), during the strip tension drop. The Steckel roll 1 rotates counterclockwise according to the arrow indicated around the axis of rotation and coils the rolling stock 6. The roll 3 is mounted at both ends on the pivoting arm 4 on which a hydraulic advancing PCT/EP2005/006561 - 5a -cylinder 8 engages in each case. The two pivoting arms 4 are pivotable about the pivot axis 9 and are connected to one another in the region of the latter. The acting strip tension is illustrated by vectors 10. The resultant strip tension acting on the roll 3 is obtained from the force parallelogram which is shown below this figure in which the force 11 which is opposite to the resultant of the strip tension 10, but is equal in size, and which the advancing cylinder 8 must apply to the roll at this timepoint can be taken.
In position b), the strip tension has already decreased. The roll 3 has already been lowered by the advancing cylinder 8 in order to absorb the strip tension drop. Due to the geometry of the advancing device, the advancing moment is reduced in the case of a constant cylinder force.
The two positions a) and b) are illustrated, superposed, at bottom right in fig. 2 in a simplified way only in the form of the rolling stock and of the roll with a pivoting arm. The arrow 12 shows the direction of movement of the roll 3 during winding over the flat spot of the Steckel roll 1.
The regulation of the drive of the Steckel roll 1 reacts to the strip tension drop by an increase in the rotational speed, and the roll 3 is drawn back into the zero position before the strip tension drop. This ensures that, during coiling, the roll 3 always returns into the initial position of the roll before the passage of the flat spot, presupposing that the force on the roll 3 is adapted to the instantaneous strip tension resultant (as a function of the coil diameter). Otherwise (variable position of the roll) the roll rises continuously from a lower position to an upper position according to the constant force of the advancing cylinder 8.
During coiling, due to the flat spot on the Steckel roll 1, a lengthening of the rolling stock 6 and consequently a strip tension drop occur. The roll 3 is lowered by the rolling stock 6.
The geometry of the articulation of the hydraulic advancing cylinder 8 has been selected such that the lever arm of the cylinder force with respect to the center of gravity of the pivoting arm 4 is reduced, and as a result, despite the deflection of the pivoting arm 4, the strip tension is reduced slightly. The torque regulation of the Steckel roll 1 reacts to this reduction by an increase in the rotational speed until the desired strip tension is restored. The roll 3 is thereby returned into its position before the strip tension reduction.
Fig. 3, in a similar way to fig. 2, shows at top left, in position a), a device according to the invention before the strip tension rise caused by the flat spot and at bottom left, in position b), during the strip tension rise.
PCT/EP2005/006561 - 6a -During uncoiling, due to the flat spot on the Steckel roll 1, a shortening of the rolling stock 6 and consequently a strip tension rise occur. The roll 3 is raised by the rolling stock 6.
The geometry of the articulation of the hydraulic advancing cylinder has been selected such that the lever arm of the cylinder force with respect to the center of gravity of the pivoting arm 4 is increased, and as a result, despite the deflection of the pivoting arm 4, the strip tension is increased slightly. The torque regulation of the Steckel roll 1 reacts to this increase by a reduction in the rotational speed until the desired strip tension is restored. The roll 3 is thereby returned into its position before the strip tension increase.
This ensures that, during uncoiling, the roll 3 returns into the initial position of the roll before the passage of the flat spot, presupposing that the force on the roll 3 is adapted to the instantaneous strip tension resultant. Otherwise (variable position of the roll), the roll travels continuously from an upper position to a lower position according to the constant force of the advancing cylinder 8.
The regulation of the other Steckel roll on the other side of the roll stand takes place in a similar way, in each case one Steckel roll winds up and the other unwinds, with the exception of the first and the last pass where in each case only one Steckel roll is used.
List of reference symbols:
1 Steckel roll 2 Driver 3 Roll 4 Pivoting arm Roll stand 6 Rolling stock 7 Threading-in slot 8 Advancing cylinder 9 Pivot axis Strip tension 11 Force on the roll 12 Direction of movement of the roll
Oscillations arise in a Steckel mill in a known way in that, although a Steckel roll is cylindrical, it has, along the Steckel roll, a slot which serves for receiving the rolling stock head (strip head). This slot is connected by means of corresponding transition radii to the cylindrical casing of the Steckel roll, so that the circumferential contour of the rolling stock coiled on the Steckel roll is not circular, but has a flat spot which corresponds to a chord.
During the coiling or uncoiling of the rolling stock, therefore, at the flat spot in each case a strip tension drop occurs, which corresponds to a lengthening of the rolling stock portion located between the Steckel roll and the roll stand, or, respectively, a strip tension rise occurs, which corresponds to a shortening of the rolling stock portion located between the Steckel roll and the roll stand. In the event of a strip tension drop, the strip tension may in this region become very low or even zero.
A solution to this problem is proposed in EP-A-1180402, where a movable driver roll varies the length of travel of the rolling stock, specifically as a function of the rotary angle of the Steckel roll. However, it is necessary, here, that the angular position of the flat spot of the Steckel roll or its flat spot is determined and that the necessary position of the driver roll, which also depends on the position of the deflecting roll, is determined from this.
PCT/EP2005/006561 - la -An object of the present invention, then, is to simplify the known method for reducing vibrations in terms of regulation.
The object is achieved by means of a method according to claim 1 and by means of a device according to claim 8.
Since the force which the roll exerts on the rolling stock is regulated to a predetermined value, that is to say the roll is pressed with predetermined force against the rolling stock, this ensures that, when the flat spot is reached, during coiling, the strip tension drop is attenuated due to the displacement of the roll with respect to the strip, this taking place by virtue of the predetermined force on the roll.
In this case, no influence is exerted on the drive control of the Steckel roll or on the strip tension regulation, this operating without any coupling to the regulation of the force on the roll. As a rule, the strip tension is regulated via the drives of the two working rolls of the roll stand and the drives of the two Steckel rolls. The rotational speed of the Steckel rolls is obtained, for example, from the rolling speed and the current coil diameter, the torque of the Steckel rolls being obtained from the predetermined strip tension and the coil diameter.
The deflection of the roll at the flat spot causes a geometric change in the force action. The force on the roll remains the same, only the point of actiqn of the force on the rolling stock changing. Depending on the direction of deflection, this means that the predetermined force on the roll entails a slight change in the strip tension.
The regulation of the drive of the Steckel roll can, after the flat spot has been passed, compensate the length error of the rolling stock by a change in rotational speed (with the aim of keeping the torque constant in terms of the strip tension) and can thereby draw the roll back into the initial position which the roll had upstream of the flat spot. This takes place automatically by means of the existing regulation of the Steckel roll.
In one possible implementation of the invention, the force is kept constant during one or more revolutions of the Steckel roll.
If, therefore, too little strip is for a short time wound up during the coiling of the rolling stock when the latter passes through at the flat spot, the strip tension falls. Due to the constant advancing force on the roll, the roll is displaced until it is in force equilibrium with the rolling stock in a PCT/EP2005/006561 - 2a -new position. Due to the slight variation in position, the angle between the two rolling stock portions located upstream and downstream of the roll decreases. In the case of a constant force, the advancing device causes the advancing moment to be reduced in the event of a strip tension drop and causes the advancing moment to be increased in the event of a strip tension rise. However, what can be achieved is 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, this not being discussed in any more detail here because it is part of general specialized knowledge.
In another possibility for a solution, during a specific time span of each revolution, an additional force is added to a force which is constant for the duration of one or more revolutions of the Steckel roll. This may be achieved in that the constant force is increased for a specific time span prior to the occurrence of the strip tension drop and is lowered to the original constant value again after this time span. In any event, the drop in strip tension can be compensated more quickly than in the case of a force which is constant during a revolution. The prior addition of an additional force can in this case compensate the inertia of the roll even better.
The time span for the addition of the additional force corresponds to approximately 1/3 of the duration of the uncoiling or coiling of the rolling stock over the flat spot.
To determine the adding of the additional force, the angular position of the Steckel roll or of the flat spot can be determined.
Further, there may be provision for changing the force as a function of the coil diameter of the rolling stock on the Steckel drum. That is to say, for example, the force remains essentially constant during, a revolution of the Steckel roll and becomes continuously higher or lower with an increasing coil diameter. In the embodiment involving the periodic addition of an additional force, the constant force likewise rises continuously, but not the additional force.
In a given position of the roll, the force on the roll and the force exerted on the roll by the strip tension and the looping of the rolling stock are in equilibrium. If, then, the coil diameter rises or falls, the spatial position of the rolling stock between roll and Steckel roll and therefore also the force equilibrium change, so that, to restore the earlier force equilibrium, the force on the roll or the spatial position of the roll is changed. The necessary change in the for'ce can be determined or calculated from the force- parallelogram: formed from the forces on the roll (strip tension and advancing force on the roll).
There are therefore two possible solutions: either the force on the roll is dependent only on the strip tension resultant at a PCT/EP2005/006561 - 3a -specific time point and is therefore essentially constant (with the exception of the periodic additional force applied if appropriate) over the entire coiling duration, and then, for example during coiling, due to the increase in coil diameter the strip tension resultant at the roll becomes increasingly higher and the roll is increasingly forced further out of the path of the rolling stock. Thus, with the exception of deflection due to the flat spot of the Steckel roll, the position of the roll is variable, the roll traveling continuously from an initial position at the start of the coiling operation to a final position at the end of the coiling operation.
Or the force on the roll is predetermined both as a function of the strip tension and as a function of the coil diameter, and then the force can be selected such that it maintains the equilibrium with the instantaneous strip tension resultant, and the roll changes its position briefly during the strip tension fluctuation only and thereafter returns again into the initial position before strip tension fluctuation.
The spatial position of the roll therefore remains fixed during the entire coiling or uncoiling operation, with the exception of deflection due to the flat spot on the Steckel roll.
As a rule, the force is selected such that, in a predetermined position of the roll, this force cancels the force exerted on the roll by the predetermined strip tension. In the first case of the variable position of the roll, the necessary force is determined on the basis of the geometric conditions (arrangement of the rolling stock in relation to the roll), for example at the start of the coiling operation on the basis of the predetermined strip tension arising from the force parallelogram.
In the second case of the fixed position of the roll, with the aid of the force parallelogram the force on the roll is adapted continuously during the coiling operation to the changing geometric conditions due to the increase or decrease in the coil diameter of the strip tension resultant acting in each case on the roll.
The fact that the roll and/or its bearings, such as, for example, a pivoting arm, are advanced hydraulically has the advantage that the advance can take place more quickly and more accurately, as compared with pneumatic advancing or advancing by means of a motor.
Since the roll is moved essentially perpendicularly with respect to the plane of the rolling stock located between the Steckel roll and the driver, a maximum possible effect is achieved with a low deflection of the roll. However, the advance of the roll may be brought about by advancing cylinders oriented obliquely with respect to this plane.
PCT/EP2005/006561 - 4a -The device for carrying out the method may comprise at least one preferably hydraulic advancing cylinder which engages on the mounting of the roll, for example a pivoting arm.
The advancing cylinder advantageously has a position measuring device for determining the starting position and for monitoring the position of the roll during-the coiling operation.
Further, the advancing cylinder may have a pressure measurement device both on the rod side and on the piston side, the advantage of this being that the actual pressures can be monitored.
So that strip tension fluctuations can be compensated quickly by means of the roll according to the invention, a roll which has low mass inertia is to be provided. For this purpose, there may be provision for the roll to be designed as a tube. A ratio of the wall thickness of the tube to the outside tube diameter of about 1:10 is considered sufficiently stable.
It proves advantageous for the hydraulics if the roll is mounted on a pivoting arm on which the advancing cylinder engages, the lever arm of the advancing cylinder with respect to the axis of the pivoting arm being smaller than the distance between the roll axis and the axis of the pivoting arm. As a result, the advancing cylinder has to execute only movements with a lower speed than that of the roll, so that advancing cylinders with smaller valves and with shorter switching times can be used.
The invention is explained, with reference to an example, by means of the following figures 1 to 3:
Fig. 1 shows a diagrammatic illustration of a Steckel mill.
Fig. 2 shows the position of the roll before and during a strip tension drop during coiling.
Fig. 3 shows the position of the roll before and during a strip tension rise during uncoiling.
According to fig. 1, an additional advanceable roll 3 is arranged between the Steckel roll 1 of what is known as the Steckel furnace (coiler furnace) of the drivers 2 arranged upstream and downstream of the roll stand 5. The roll is mounted in a pivoting arm and is in engagement with the rolling stock 6. The drivers 2 are open at this time point with a fixed position of the upper driver roll. The threading-in slot 7 of the Steckel roll 1 causes a flat spot for the'coiled rolling stock 6.
Fig. 2 shows at top left, in position a), a device according to the invention before the strip tension drop caused by the flat spot and at bottom left, in position b), during the strip tension drop. The Steckel roll 1 rotates counterclockwise according to the arrow indicated around the axis of rotation and coils the rolling stock 6. The roll 3 is mounted at both ends on the pivoting arm 4 on which a hydraulic advancing PCT/EP2005/006561 - 5a -cylinder 8 engages in each case. The two pivoting arms 4 are pivotable about the pivot axis 9 and are connected to one another in the region of the latter. The acting strip tension is illustrated by vectors 10. The resultant strip tension acting on the roll 3 is obtained from the force parallelogram which is shown below this figure in which the force 11 which is opposite to the resultant of the strip tension 10, but is equal in size, and which the advancing cylinder 8 must apply to the roll at this timepoint can be taken.
In position b), the strip tension has already decreased. The roll 3 has already been lowered by the advancing cylinder 8 in order to absorb the strip tension drop. Due to the geometry of the advancing device, the advancing moment is reduced in the case of a constant cylinder force.
The two positions a) and b) are illustrated, superposed, at bottom right in fig. 2 in a simplified way only in the form of the rolling stock and of the roll with a pivoting arm. The arrow 12 shows the direction of movement of the roll 3 during winding over the flat spot of the Steckel roll 1.
The regulation of the drive of the Steckel roll 1 reacts to the strip tension drop by an increase in the rotational speed, and the roll 3 is drawn back into the zero position before the strip tension drop. This ensures that, during coiling, the roll 3 always returns into the initial position of the roll before the passage of the flat spot, presupposing that the force on the roll 3 is adapted to the instantaneous strip tension resultant (as a function of the coil diameter). Otherwise (variable position of the roll) the roll rises continuously from a lower position to an upper position according to the constant force of the advancing cylinder 8.
During coiling, due to the flat spot on the Steckel roll 1, a lengthening of the rolling stock 6 and consequently a strip tension drop occur. The roll 3 is lowered by the rolling stock 6.
The geometry of the articulation of the hydraulic advancing cylinder 8 has been selected such that the lever arm of the cylinder force with respect to the center of gravity of the pivoting arm 4 is reduced, and as a result, despite the deflection of the pivoting arm 4, the strip tension is reduced slightly. The torque regulation of the Steckel roll 1 reacts to this reduction by an increase in the rotational speed until the desired strip tension is restored. The roll 3 is thereby returned into its position before the strip tension reduction.
Fig. 3, in a similar way to fig. 2, shows at top left, in position a), a device according to the invention before the strip tension rise caused by the flat spot and at bottom left, in position b), during the strip tension rise.
PCT/EP2005/006561 - 6a -During uncoiling, due to the flat spot on the Steckel roll 1, a shortening of the rolling stock 6 and consequently a strip tension rise occur. The roll 3 is raised by the rolling stock 6.
The geometry of the articulation of the hydraulic advancing cylinder has been selected such that the lever arm of the cylinder force with respect to the center of gravity of the pivoting arm 4 is increased, and as a result, despite the deflection of the pivoting arm 4, the strip tension is increased slightly. The torque regulation of the Steckel roll 1 reacts to this increase by a reduction in the rotational speed until the desired strip tension is restored. The roll 3 is thereby returned into its position before the strip tension increase.
This ensures that, during uncoiling, the roll 3 returns into the initial position of the roll before the passage of the flat spot, presupposing that the force on the roll 3 is adapted to the instantaneous strip tension resultant. Otherwise (variable position of the roll), the roll travels continuously from an upper position to a lower position according to the constant force of the advancing cylinder 8.
The regulation of the other Steckel roll on the other side of the roll stand takes place in a similar way, in each case one Steckel roll winds up and the other unwinds, with the exception of the first and the last pass where in each case only one Steckel roll is used.
List of reference symbols:
1 Steckel roll 2 Driver 3 Roll 4 Pivoting arm Roll stand 6 Rolling stock 7 Threading-in slot 8 Advancing cylinder 9 Pivot axis Strip tension 11 Force on the roll 12 Direction of movement of the roll
Claims (15)
1. A method for reducing vibrations due to a flat spot on a Steckel roll (1) in a Steckel mill, an advanceable roll (3), which is brought into engagement with the rolling stock (6), being arranged between the Steckel roll (1) of the Steckel furnace and the driver (2) of the roll stand (5), characterized in that the force which the roll (3) exerts on the rolling stock (6) is regulated to a predetermined value.
2. The method as claimed in claim 1, characterized in that the force is kept constant during one or more revolutions of the Steckel roll (1).
3. The method as claimed in claim 1, characterized in that an additional force is added during a specific timespan of each revolution to a force which is constant for the duration of one or more revolutions of the Steckel roll (1).
4. The method as claimed in one of claims 1 to 3, characterized in that the force is changed as a function of the coil diameter of the rolling stock (6) on the Steckel roll (1).
5. The method as claimed in one of claims 1 to 4, characterized in that the force is selected such that, in a predetermined position of the roll, this force cancels the force exerted on the roll by the predetermined strip tension.
6. The method as claimed in one of claims 1 to 5, characterized in that the roll (3) and/or its mounting, such as, for example, a pivoting arm (4), are advanced hydraulically.
7. The method as claimed in one of claims 1 to 6, characterized in that the roll (3) is moved essentially - 8a -perpendicularly with respect to the plane of the rolling stock (6) located between the Steckel roll (1) and the driver (2).
8. A device for carrying out the method as claimed in one of claims 1 to 7, consisting at least of an advanceable roll (3) which is arranged between the Steckel roll (1) and the driver (2) of the roll stand (5), so that said roll can be brought into engagement with the rolling stock (6), characterized in that a device (4, 8) is provided, by means of which the force which the roll (3) exerts on the rolling stock (6) can be regulated to a predetermined value.
9. The device as claimed in claim 8, characterized in that the device comprises at least one preferably hydraulic advancing cylinder (8) which engages on the mounting of the roll (3), for example a pivoting arm (4).
10. The device as claimed in claim 9, characterized in that the advancing cylinder (8) has a position measurement device.
11. The device as claimed in either one of claims 9 and 10, characterized in that the advancing cylinder (8) has a pressure measurement device both on the rod side and on the piston side.
12. The device as claimed in one of claims 8 to 11, characterized in that the roll (3) can be moved essentially perpendicularly with respect to the plane of the rolling stock (6) located between the Steckel roll (1) and driver (2).
13. The device as claimed in one of claims 8 to 12, characterized in that the roll is designed as a tube.
14. The device as claimed in one of claims 9 to 13, characterized in that the roll (3) is mounted on the pivoting arm (4) on which the advancing cylinder (8) engages, the lever arm of the advancing cylinder (8) with respect to the axis (9) of the pivoting arm being smaller than the distance between the roll axis and the axis of the pivoting arm.
15. The device as claimed in one of claims 8 to 14, characterized in that the device (4, 8) is arranged such that the advancing moment is reduced in the event of a strip tension drop and the advancing moment is increased in the event of a strip tension rise.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT0114404A AT502723B1 (en) | 2004-07-07 | 2004-07-07 | METHOD AND DEVICE FOR REDUCING VIBRATIONS IN A SLIDING ROLLER |
| ATA1144/2004 | 2004-07-07 | ||
| PCT/EP2005/006561 WO2006002783A1 (en) | 2004-07-07 | 2005-06-17 | Method and device for reducing vibrations in a steckel mill |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2572986A1 true CA2572986A1 (en) | 2006-01-12 |
Family
ID=34970395
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002572986A Abandoned CA2572986A1 (en) | 2004-07-07 | 2005-06-17 | Method and device for reducing vibrations in a steckel mill |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP1763410B1 (en) |
| JP (2) | JP2008504969A (en) |
| CN (1) | CN1984729B (en) |
| AT (2) | AT502723B1 (en) |
| BR (1) | BRPI0513148A (en) |
| CA (1) | CA2572986A1 (en) |
| DE (1) | DE502005006011D1 (en) |
| PL (1) | PL1763410T3 (en) |
| WO (1) | WO2006002783A1 (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102007005378A1 (en) | 2007-02-02 | 2008-08-07 | Siemens Ag | Operating method for a reel device for winding or unwinding a tape and control device and reel device for this purpose |
| AT506398B1 (en) | 2008-06-18 | 2009-09-15 | Siemens Vai Metals Tech Gmbh | METHOD AND DEVICE FOR SUPPRESSING VIBRATIONS IN A ROLLING SYSTEM |
| CN104226727A (en) * | 2014-09-26 | 2014-12-24 | 武汉钢铁(集团)公司 | Control method of coefficient-variable uncoiler |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60231516A (en) * | 1984-04-28 | 1985-11-18 | Sumitomo Metal Ind Ltd | Coiler having looper mechanism |
| JPS6333116A (en) * | 1986-07-25 | 1988-02-12 | Hitachi Ltd | Furnace coiler winding control method |
| JPH10180327A (en) * | 1996-12-20 | 1998-07-07 | Nisshin Steel Co Ltd | Tension control method for chip end and tail end of strip in steckel mill |
| DE19818207C2 (en) * | 1998-04-23 | 2000-05-31 | Schloemann Siemag Ag | Steckel hot rolling mill |
| GB0020160D0 (en) * | 2000-08-17 | 2000-10-04 | Vai Ind Uk Ltd | Steckel furnace coiler and apparatus therefor |
| DE10133756A1 (en) * | 2001-07-11 | 2003-01-30 | Sms Demag Ag | Cold rolling mill and method for cold rolling metallic strip |
| CN1152755C (en) * | 2001-08-20 | 2004-06-09 | 燕山大学 | Composite roll system with controllable small opening for rolling mill |
| UA79184C2 (en) * | 2002-12-14 | 2007-05-25 | Sms Demag Ag | Method and installation for hot-rolling strips using reversible steckel rolling frame |
| JP4334539B2 (en) * | 2002-12-14 | 2009-09-30 | エス・エム・エス・ジーマーク・アクチエンゲゼルシャフト | Method and equipment for hot-rolling strips with one stickel rolling stand |
-
2004
- 2004-07-07 AT AT0114404A patent/AT502723B1/en not_active IP Right Cessation
-
2005
- 2005-06-17 CN CN2005800230765A patent/CN1984729B/en not_active Expired - Fee Related
- 2005-06-17 AT AT05752303T patent/ATE414574T1/en not_active IP Right Cessation
- 2005-06-17 WO PCT/EP2005/006561 patent/WO2006002783A1/en active Application Filing
- 2005-06-17 JP JP2007519652A patent/JP2008504969A/en not_active Ceased
- 2005-06-17 EP EP05752303A patent/EP1763410B1/en not_active Revoked
- 2005-06-17 CA CA002572986A patent/CA2572986A1/en not_active Abandoned
- 2005-06-17 PL PL05752303T patent/PL1763410T3/en unknown
- 2005-06-17 BR BRPI0513148-0A patent/BRPI0513148A/en not_active IP Right Cessation
- 2005-06-17 DE DE502005006011T patent/DE502005006011D1/en active Active
-
2012
- 2012-03-22 JP JP2012065725A patent/JP2012110969A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| AT502723A1 (en) | 2007-05-15 |
| CN1984729A (en) | 2007-06-20 |
| WO2006002783A1 (en) | 2006-01-12 |
| EP1763410A1 (en) | 2007-03-21 |
| JP2012110969A (en) | 2012-06-14 |
| EP1763410B1 (en) | 2008-11-19 |
| BRPI0513148A (en) | 2008-04-29 |
| ATE414574T1 (en) | 2008-12-15 |
| PL1763410T3 (en) | 2009-04-30 |
| AT502723B1 (en) | 2008-08-15 |
| CN1984729B (en) | 2010-06-16 |
| DE502005006011D1 (en) | 2009-01-02 |
| JP2008504969A (en) | 2008-02-21 |
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Legal Events
| Date | Code | Title | Description |
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| FZDE | Discontinued |