WO2019221297A1 - 圧延機及び圧延機の設定方法 - Google Patents
圧延機及び圧延機の設定方法 Download PDFInfo
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- WO2019221297A1 WO2019221297A1 PCT/JP2019/019809 JP2019019809W WO2019221297A1 WO 2019221297 A1 WO2019221297 A1 WO 2019221297A1 JP 2019019809 W JP2019019809 W JP 2019019809W WO 2019221297 A1 WO2019221297 A1 WO 2019221297A1
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- Prior art keywords
- roll
- work
- load
- chock
- difference
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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
- B21B37/58—Roll-force control; Roll-gap control
-
- 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
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
-
- 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
- B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
- B21B31/028—Prestressing of rolls or roll mountings in stand frames
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
- B21B38/10—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring roll-gap, e.g. pass indicators
- B21B38/105—Calibrating or presetting roll-gap
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
- B21C51/00—Measuring, gauging, indicating, counting, or marking devices specially adapted for use in the production or manipulation of material in accordance with subclasses B21B - B21F
-
- 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
- B21B2031/206—Horizontal offset of work rolls
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
- B21B2203/18—Rolls or rollers
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
- B21B2203/34—Rotational position or alignment
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2269/00—Roll bending or shifting
- B21B2269/02—Roll bending; vertical bending of rolls
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/16—Adjusting or positioning rolls
- B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
- B21B31/32—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis by liquid pressure, e.g. hydromechanical adjusting
-
- 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
- B21B37/58—Roll-force control; Roll-gap control
- B21B37/62—Roll-force control; Roll-gap control by control of a hydraulic adjusting device
-
- 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
- B21B37/68—Camber or steering control for strip, sheets or plates, e.g. preventing meandering
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
- B21B38/08—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring roll-force
Definitions
- the present invention relates to a rolling mill for rolling a material to be rolled and a setting method for the rolling mill.
- Patent Document 1 the thrust reaction force in the roll axis direction and the load in the rolling direction are measured, one or both of the rolling position zero point and the deformation characteristics of the rolling mill are obtained, and the rolling position is set at the time of rolling.
- a plate rolling method for controlling the rolling is disclosed.
- the thrust force generated in the roll is calculated based on a micro-cross between rolls (skew angle) measured using a distance sensor provided in the rolling mill, and the reduction is performed based on the thrust force.
- a meandering control method is disclosed in which a differential load component caused by meandering is calculated from a load measurement value in a direction and the reduction leveling control is performed.
- Patent Document 3 discloses a cross point correcting device that corrects a deviation of a point (cross point) where the center axes of upper and lower rolls intersect in the horizontal direction in a pair cross rolling mill.
- Such an apparatus includes an actuator that absorbs play generated between the cross head and the roll chock, and a detector that detects the roll chock position, and corrects the deviation of the cross point based on the roll chock position.
- Patent Document 4 when the load difference between the drive side and the operation side is detected and the meandering of the rolled material is controlled by independently operating the reduction positions on the drive side and the operation side based on the detected load difference.
- the differential load during rolling is separated into that due to the meandering of the rolled material and that due to the thrust, and driven based on these separated differential loads.
- the roll skew angle is obtained from the horizontal distance of the roll measured by a vortex type distance sensor.
- the thrust force It is difficult to accurately measure the horizontal displacement of the roll.
- the friction coefficient of the roll changes from time to time because the roughness of the roll changes with time as the number of rolling rolls increases. For this reason, the thrust force cannot be calculated accurately only from the roll skew angle measurement without identifying the friction coefficient.
- a bending force is applied while driving the roll in a state where the upper and lower rolls are not in contact with each other before rolling, and it is obtained from a load difference between the driving side and the working side generated at that time.
- the differential load caused by the thrust is estimated from the thrust coefficient or skew amount.
- the thrust coefficient or the skew amount is identified only from the measured value in one rotational state of the upper and lower rolls. For this reason, when the deviation of the zero point of the load detection device or the influence of the frictional resistance between the housing and the roll chock is different on the left and right, there is a possibility that an asymmetrical error occurs between the measured value on the drive side and the measured value on the work side. is there. In particular, when the load level is small such as a bending force, the error can be a fatal error in identifying the thrust coefficient or the skew amount.
- Patent Document 4 the thrust coefficient or the skew amount cannot be identified unless the friction coefficient between rolls is given. Furthermore, in Patent Document 4, the thrust reaction force of the backup roll is assumed to act on the roll axis position, and changes in the position of the acting point of the thrust reaction force are not taken into consideration. Usually, since the chock of the backup roll is supported by a reduction device or the like, the position of the point of action of the thrust reaction force is not always located at the roll axis. For this reason, an error occurs in the thrust force between the rolls obtained from the load difference between the driving-side rolling direction load and the working-side rolling direction load, and the thrust coefficient or skew amount calculated based on the inter-roll thrust force is also an error. Occurs. When an error occurs in the thrust coefficient or the skew amount in this way, the accuracy of meander control of the material to be rolled decreases due to the influence of the error.
- the zero point of the reduction position in the kiss roll state is adjusted by the operator based on the values of the work side and the drive side of the reduction direction load.
- an inter-roll thrust force is generated by the micro roll-to-roll cross, there is a difference in the rolling direction load between the working side and the driving side, and the zero-point adjustment of the rolling position may not be performed correctly.
- the techniques described in any of the above-mentioned patent documents cannot reduce the inter-roll thrust force before the reduction position zero point adjustment.
- an object of the present invention is to reduce the thrust force generated between rolls before the reduction position zero point adjustment or before the start of rolling.
- Another object of the present invention is to provide a new and improved rolling mill and a rolling mill setting method capable of suppressing the meandering of the material to be rolled and the occurrence of camber.
- a rolling mill having four or more stages including a plurality of rolls including at least a pair of work rolls and a pair of reinforcing rolls supporting the work rolls.
- Load detection for detecting a roll-down load acting in the roll-down direction at the work-side and drive-side roll-down fulcrum positions of the reinforcing roll using any one of the rolls arranged in the roll-down direction as a reference roll A device, a pressing device that presses the roll chock in the rolling direction, and a roll other than at least the reference roll, provided on either the entry side or the exit side in the rolling direction of the material to be rolled relative to the roll chock of the roll other than at least the reference roll
- the roll chock is provided so as to face the pressing device in the rolling direction, and the roll chock is moved in the rolling direction.
- the rolling direction position of the rolling device and the roll chock of the reference roll is fixed as the reference position, and the difference between the rolling direction load detected by the work side load detection device and the rolling direction load detected by the drive side load detection device
- a rolling mill provided with a position control device that drives a driving device so as to control a position in a rolling direction of a roll chock of a roll other than the reference roll so that a certain rolling direction load difference becomes a value within an allowable range. Is done.
- the roll positioned at the lowest or uppermost position in the rolling direction may be used as the reference roll.
- a bending device that applies bending force to the roll may be provided.
- the position control device opens the roll gap between the work rolls and applies a bending force to the work roll chock on the roll whose position is to be adjusted by the bending device.
- the drive device may be a hydraulic cylinder equipped with a roll chock position detection device.
- a rolling mill setting method wherein the rolling mill includes at least a pair of work rolls and a pair of reinforcing rolls that support the work rolls.
- a rolling roll having four or more stages, including a plurality of rolls, and a load detection device that detects a rolling direction load acting in a rolling direction of the roll at the working side and driving side rolling fulcrum positions of the reinforcing roll, Executed before the zero point adjustment or before the start of rolling, with any one of the rolls arranged in the rolling direction as a reference roll, the rolling direction load detected by the work side load detection device and the driving side load detection Calculate the rolling direction load difference, which is the difference from the rolling direction load detected by the machine, so that the rolling direction load difference is within the allowable range. It was fixed as a reference position, and by moving the roll chocks other than the reference roll in the rolling direction of the rolled material, to adjust the position of the roll chock, setting of the mill is provided.
- the roll positioned at the lowest or uppermost position in the rolling direction may be used as the reference roll.
- a plurality of rolls provided on the upper side in the rolling direction with respect to the material to be rolled are an upper roll system
- a plurality of rolls provided on the lower side in the reduction direction with respect to the material to be rolled are used as a lower roll system.
- the first step of adjusting the position and the second step of adjusting the positions of the roll chock of the upper roll system and the lower roll system by putting the work roll into a kiss roll state after finishing the first step are performed.
- the roll is rotated in a predetermined rotation direction, and the upper roll system and the lower roll system are each operated.
- a first reference value calculation step of detecting a driving-side load in the rolling direction and calculating a first reference value based on a rolling-direction load difference that is a difference between the work-side rolling-down load and the driving-side rolling-down load.
- the roll direction of the roll is reversed, and the work side and drive side roll direction loads are detected for each of the upper roll system and the lower roll system, and the difference between the work side roll direction load and the drive side roll direction load is detected.
- the roll chock of the work roll of the roll system on the reference roll side, or the roll chock of either the work roll of the roll system on the side opposite to the reference roll or the reinforcing roll is moved in the rolling direction so as to be a value within Low
- the first adjustment step for adjusting the position of the chock is performed, and in the second step, the work roll is set in a kiss roll state, the roll is rotated in a predetermined rotation direction, and the upper roll system and the lower roll system are respectively
- a second reference value is calculated based on a difference in the reduction direction load, which is a difference between the reduction direction load on the operation side and the reduction direction load on the drive side.
- the reference value calculation step and the roll rotation direction are reversed to detect the work-side and drive-side roll-down loads for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down direction
- the upper roll system or the lower roll system is used as a reference roll system, and the roll chock of each roll of the other roll system is controlled simultaneously and in the same direction while maintaining the relative position between the roll chock. Then, a second adjustment step of adjusting the position of the roll chock may be performed.
- a plurality of rolls provided on the upper side in the reduction direction with respect to the material to be rolled are arranged on the upper roll system and the material to be rolled.
- a plurality of rolls provided in the lower side of the rolling direction are set as the lower roll system, the roll gap of the work roll is opened, and a bending force is applied to the roll chock of the intermediate roll by a bending device.
- the second step of adjusting the position of the roll chock of the intermediate roll and the roll chock of the work roll, and after finishing the second step, the work roll is put into a kiss roll state, and the upper roll system and the lower roll system
- a first reference value calculating step for detecting a directional load and calculating a first reference value based on a rolling direction load difference that is a difference between a working side rolling load and a driving side rolling load; Reverse the direction and detect the work side and drive side roll-down loads for the upper roll system and the lower roll system, respectively, and the work side roll-down load and the drive side roll-down load.
- a first control target value calculating step for calculating a first control target value based on a deviation between the rolling direction load difference and the first reference value, and the rolling direction load difference is the first control target value.
- the calculation step and the roll rotation direction are reversed to detect the work side and drive side reduction load for each of the upper roll system and the lower roll system, and the work side reduction load and the drive side reduction load
- a second control target value calculating step for calculating a second control target value based on the deviation between the rolling direction load difference and the second reference value, and the rolling direction load difference of the second control target value Roll either the roll chock of the work roll of the roll system on the reference roll side and the roll chock of the work roll of the roll system opposite to the reference roll or the roll chock of the intermediate roll and the reinforcing roll so that the value falls within the allowable range.
- the third reference value calculation step for calculating the third reference value based on the directional load difference, and the roll rotation direction is reversed, and the roll-side loads on the working side and the driving side are respectively applied to the upper roll system and the lower roll system.
- One of the upper roll system and the lower roll system is set as a reference roll system, and each of the other roll systems is set so that the target value calculation step and the rolling direction load difference are within the allowable range of the third control target value.
- Roll roll chock Controlled simultaneously and in the same direction while maintaining the relative position between Ruchokku, a third adjustment step of adjusting the position of the roll chock may be carried out.
- a plurality of rolls provided on the upper side in the rolling direction with respect to the material to be rolled is an upper roll system
- a plurality of rolls provided on the lower side in the rolling direction with respect to the material to be rolled are lower rolls.
- the roll gap of the work roll and the roll chock of the reinforcing roll for each of the upper roll system and the lower roll system in a state where the roll gap of the work roll is opened and bending force is applied to the roll chock of the work roll by a bending device.
- each of the upper roll system and the lower roll system In the first step, in the state where the rotation of the roll is stopped, each of the upper roll system and the lower roll system
- the work-side and drive-side roll-down loads are detected, and a first reference value is calculated based on a roll-down load difference that is the difference between the work-side roll-down load and the drive-side roll-down load.
- a first control target value calculation step for setting a first control target value based on the value, and rotating the roll to detect the rolling-down load on the working side and the driving side for each of the upper roll system and the lower roll system.
- a first load difference step for calculating a difference in the reduction direction load which is a difference between the reduction direction load on the work side and the reduction direction load on the drive side, and the reduction direction load difference is within an allowable range of the first control target value.
- Adjust the roll chock position by moving the roll chock of the roll-type work roll on the reference roll side, or the roll-type work roll on the opposite side of the reference roll or the roll chock of the reinforcing roll in the rolling direction so that the
- the work roll and the lower roll system are driven and driven for each of the upper roll system and the lower roll system in a state where the work roll is in a kiss roll state and rotation of the roll is stopped.
- the second reference value is calculated based on the difference in the reduction direction load, which is the difference between the reduction load on the working side and the reduction load on the drive side, and the second reference value is calculated based on the second reference value.
- a second control target value calculation step for setting a control target value of 2 and rotating the roll to detect the rolling load on the working side and the driving side for each of the upper roll system and the lower roll system,
- a second load difference calculation step for calculating a difference in the reduction direction load, which is a difference between the reduction direction load and the reduction load on the driving side, and the reduction direction load difference becomes a value within an allowable range of the second control target value;
- As the upper roll system or A second roll for adjusting the position of the roll chock by setting one of the lower roll systems as a reference roll system and controlling the roll chock of each roll of the other roll system simultaneously and in the same direction while maintaining the relative position between the roll chock And an adjustment step.
- a plurality of rolls provided on the upper side in the reduction direction with respect to the material to be rolled are arranged on the upper roll system and the material to be rolled.
- a plurality of rolls provided in the lower side of the rolling direction are set as the lower roll system, the roll gap of the work roll is opened, and a bending force is applied to the roll chock of the intermediate roll by a bending device.
- the second step of adjusting the position of the roll chock of the intermediate roll and the roll chock of the work roll, and after finishing the second step, the work roll is put into a kiss roll state, and the upper roll system and the lower roll system
- a load is detected, a first reference value is calculated based on a difference in the reduction direction load that is a difference between the reduction load on the work side and the reduction load on the drive side, and the first control target is calculated based on the first reference value.
- a first control target value calculating step for setting a value, and rotating the roll to detect the rolling load on the working side and the driving side for each of the upper roll system and the lower roll system,
- a first load difference calculating step for calculating a difference in the reduction direction load, which is a difference between the reduction direction load on the driving side and the reduction direction load on the drive side, and a value within the allowable range of the first control target value.
- Adjust the position of the roll chock by moving either the roll chock of the intermediate roll of the roll system on the reference roll side, or the roll chock of the intermediate roll of the roll system opposite to the reference roll or the reinforcing roll in the rolling direction.
- the load on the working side and the driving side are detected for the upper roll system and the lower roll system, respectively.
- the second reference value is calculated based on the difference in the rolling direction load between the work side rolling direction load and the driving side rolling direction load, and the second control target value is set based on the second reference value.
- the target value calculation step the roll is rotated, and the rolling load on the working side and the driving side is detected for each of the upper roll system and the lower roll system, and the rolling load on the working side and the rolling load on the driving side are detected.
- a second load difference calculating step for calculating the load difference in the reduction direction which is the difference between the two, and the work of the roll system on the reference roll side so that the load difference in the reduction direction falls within the allowable range of the second control target value.
- the upper roll system and the lower roll system are respectively set in a state where the work roll is in a kiss roll state and the rotation of the roll is stopped.
- the work-side and drive-side roll-down loads are detected, and a third reference value is calculated from the roll-down load difference that is the difference between the work-side roll-down load and the drive-side roll-down load.
- a third control target value calculating step for setting a third control target value based on the reference value, and rotating the roll to detect the rolling load on the working side and the driving side for each of the upper roll system and the lower roll system
- a third load difference calculating step for calculating a load difference in the reduction direction, which is a difference between the load in the reduction direction on the working side and the load on the driving side, and the allowable range of the third control target value in the reduction direction load difference. Control the roll chock of each roll of the other roll system at the same time and in the same direction while maintaining the relative position between the roll chock. And low
- a third adjustment step of adjusting the position of the chocks may be carried out.
- FIG. 6 is an explanatory diagram showing the difference in the rolling direction load obtained when the lower roll is rotated forward and when the lower roll is reversed in the rolling mill in the state of FIG. 5.
- It is a flowchart explaining the setting method of the rolling mill which performs roll chock position adjustment based on the rolling direction load at the time of roll stop and roll rotation which concerns on the 2nd Embodiment of this invention, Comprising: 1st in a roll gap open state Explains the adjustment.
- 10 is an explanatory diagram showing the difference in the rolling direction load obtained when the lower roll is stopped and rotated in the rolling mill in the state of FIG. 9. It is explanatory drawing which shows arrangement
- the thrust force generated between the rolls is eliminated, and the product having no meandering and cambering or having extremely slight meandering and cambering is stably provided.
- the purpose is to manufacture.
- FIG. 1 the schematic side view and schematic front view of a rolling mill for demonstrating the thrust force and thrust reaction force which generate
- the working side in the roll body length direction is expressed as WS (Work Side), and the driving side is expressed as DS (Drive Side).
- the rolling mill shown in FIG. 1 includes a pair of work rolls composed of an upper work roll 1 and a lower work roll 2, and an upper reinforcing roll 3 and a lower work roll 2 that support the upper work roll 1 in the rolling direction (Z direction). It has a pair of reinforcement roll which consists of the lower reinforcement roll 4 to support.
- the plate thickness of the material to be rolled S is set to a predetermined thickness.
- Detecting devices 28a, 28b, and down-pressing downward load detecting devices 29a, 29b for detecting a down-load in the lower roll system comprising the lower work roll 2 and the lower reinforcing roll 4 arranged on the lower surface side of the material S to be rolled; Is provided.
- the up / down direction load detecting device 28a and the down / down load detecting device 29a detect the down load on the work side.
- the upper and lower load detecting device 28b and the lower and lower load detecting device 29b detect the lower load on the drive side.
- the upper work roll 1, the lower work roll 2, the upper reinforcing roll 3, and the lower reinforcing roll 4 are arranged so that the body length directions of the rolls are parallel to each other so as to be orthogonal to the conveying direction of the material S to be rolled.
- the roll slightly rotates around an axis parallel to the rolling-down direction (Z-axis), and the upper work roll 1 and the upper reinforcement roll 3 are displaced in the trunk length direction, or the lower work roll 2 and the lower reinforcement roll 4
- a thrust force acting in the barrel length direction of the roll is generated between the work roll and the reinforcing roll.
- the inter-roll thrust force generates a moment in the roll, which is a cause of asymmetric roll deformation and makes the rolling unstable. For example, it causes meandering or camber.
- This inter-roll thrust force is generated by the occurrence of a shift in the roll body length direction between the work roll and the reinforcing roll and the occurrence of a cross-angle between rolls. For example, if an inter-roll cross angle is generated between the lower work roll 2 and the lower reinforcement roll 4, a thrust force is generated between the lower work roll 2 and the lower reinforcement roll 4, and as a result, the lower reinforcement A moment is generated in the roll 4, and the load distribution between the rolls changes so as to balance the moment, and asymmetric roll deformation occurs.
- Such an asymmetrical roll deformation causes meandering or camber, and rolling becomes unstable.
- the present invention proposes a method of adjusting the roll chock position of each roll so that the inter-roll thrust force generated between the rolls is eliminated even when the thrust reaction force applied to the rolls cannot be measured.
- FIG. 2 is an explanatory diagram showing the configuration of the rolling mill according to the present embodiment and an apparatus for controlling the rolling mill.
- the rolling mill shown in FIG. 2 has shown the state seen from the operation
- standard roll is shown.
- any one of the rolls arranged in the reduction direction may be set as the reference roll.
- the reference roll is preferably a roll located at the lowermost or uppermost position where the contact area between the chock and the housing is large and the position is stable.
- the rolling mill shown in FIG. 2 is a four-stage rolling mill having a pair of work rolls 1 and 2 and a pair of reinforcing rolls 3 and 4 that support the work rolls 1 and 2.
- the upper work roll 1, the lower work roll 2, the upper reinforcing roll 3, and the lower reinforcing roll 4 are a plurality of rolls arranged in the reduction direction.
- the upper work roll 1 is supported by an upper work roll chock 5, and the lower work roll 2 is supported by a lower work roll chock 6.
- the upper work roll chock 5 and the lower work roll chock 6 are similarly provided on the back side (drive side) of FIG. 2, and support the upper work roll 1 and the lower work roll 2, respectively.
- the upper work roll 1 and the lower work roll 2 are rotationally driven by a drive motor 21.
- the upper reinforcing roll 3 is supported by an upper reinforcing roll chock 7, and the lower reinforcing roll 4 is supported by a lower reinforcing roll chock 8.
- the upper reinforcing roll chock 7 and the lower reinforcing roll chock 8 are similarly provided on the back side (drive side) of FIG. 2 and support the upper reinforcing roll 3 and the lower reinforcing roll 4 respectively.
- the upper work roll chock 5, the lower work roll chock 6, the upper reinforcement roll chock 7 and the lower reinforcement roll chock 8 are held by the housing 30.
- the upper work roll chock 5, the lower work roll chock 6, the upper reinforcement roll chock 7, and the lower reinforcement roll chock 8 may be simply referred to as a roll chock.
- the upper work roll chock 5 is provided on the entry side in the rolling direction, provided on the upper work roll chock pressing device 9 that presses the upper work roll chock 5 in the rolling direction, and provided on the output side in the rolling direction.
- An upper work roll chock position detection function-equipped drive device 11 that drives the work roll chock 5 in the rolling direction is provided.
- the lower work roll chock 6 is provided on the entry side in the rolling direction, and is provided on the lower work roll chock pressing device 10 that presses the lower work roll chock 6 in the rolling direction, and on the outgoing side in the rolling direction, and detects the position in the rolling direction.
- the lower work roll chock position detection function-equipped drive device 12 for driving the lower work roll chock 6 in the rolling direction is provided.
- a hydraulic cylinder is used for the drive device 11 with the upper work roll chock position detection function, the drive device 12 with the lower work roll chock position detection function, the drive mechanism of the upper work roll chock pressing device 9, and the drive mechanism of the lower work roll chock pressing device 10. It is done.
- the upper and lower work roll chock position detection function-equipped drive devices 11 and 12 and the upper and lower work roll chock pressing devices 9 and 10 display only the work side, but on the back side (drive side) of the page. Is also provided in the same way.
- the upper reinforcing roll chock 7 is provided on the outlet side in the rolling direction, and is provided on the upper reinforcing roll chock pressing device 13 that presses the upper reinforcing roll chock 7 in the rolling direction.
- An upper reinforcing roll chock position detecting function-equipped drive device 14 for driving the reinforcing roll chock 7 in the rolling direction is provided.
- a hydraulic cylinder is used as the drive mechanism of the upper reinforcing roll chock position detection function-equipped driving device 14 and the upper reinforcing roll chock pressing device 13.
- the upper reinforcing roll chock position detecting function-equipped driving device 14 and the upper reinforcing roll chock pressing device 13 are shown only on the working side, but are also provided on the back side (driving side) in the same manner. .
- the lower reinforcing roll chock 8 is a reference reinforcing roll chock because the lower reinforcing roll 4 is used as a reference roll in this embodiment. Therefore, since the position adjustment is not performed by driving the lower reinforcing roll chock 8, the driving device and the position detecting device do not necessarily have to be provided like the upper reinforcing roll chock 7.
- a lower reinforcing roll chock pressing device 40 for example, is provided on the entry side or the exit side in the rolling direction so as not to change the position of the reference reinforcing roll chock as a reference for position adjustment so as to suppress rattling of the lower reinforcing roll chock 8. May be.
- the lower reinforcing roll chock pressing device 40 shows only the work side, but is also provided on the back side (drive side) in the same manner.
- the upper work roll chock pressing device 9, the lower work roll chock pressing device 10, the upper reinforcing roll chock pressing device 13 and the lower reinforcing roll chock pressing device 40 are provided on either the entry side or the exit side in the rolling direction of the material to be rolled. It is a pressing device that presses in the rolling direction, and may be simply referred to as a pressing device.
- the pressing device should just be provided with respect to the roll chock of rolls other than a reference
- the upper work roll chock position detection function drive device 11, the lower work roll chock position detection function drive device 12 and the upper reinforcement roll chock position detection function drive device 14 are provided so as to face the pressing device in the rolling direction. Is a drive device that moves the plate in the rolling direction, and may be simply referred to as a drive device.
- the drive apparatus should just be provided with respect to the roll chock of rolls other than a reference
- the rolling mill includes an entry-side upper increase bending device 24a and an output-side upper increase bending device 24b in a project block between the upper work roll chock 5 and the housing 30. Further, the rolling mill includes an entry-side lower increase bending device 25 a and an output-side lower increase bending device 25 b in a project block between the lower work roll chock 6 and the housing 30.
- the entry-side upper increment bending device 24a, the exit-side upper increment bending device 24b, the entry-side lower increment bending device 25a, and the exit-side lower increment bending device 25b are also the same on the back side (drive side) of FIG. Is provided.
- Each increase bending apparatus applies an increase bending force for applying a load to the upper work roll 1 and the upper reinforcement roll 3, and the lower work roll 2 and the lower reinforcement roll 4 to the work roll chock.
- the entry-side upper increment bending device 24a, the exit-side upper increment bending device 24b, the entry-side lower increment bending device 25a, and the exit-side lower increment bending device 25b are bending devices that apply a bending force to the roll. May be simply referred to as a bending device.
- a roll chock rolling direction force control device 15 for example, a roll chock rolling direction force control device 15, a roll chock position control device 16, a drive motor control device 22, and an inter-roll cross control device. 23 and an increment bending control device 26.
- the roll chock rolling direction force control device 15 controls the pressing force in the rolling direction of the upper work roll chock pressing device 9, the lower work roll chock pressing device 10, the upper reinforcing roll chock pressing device 13, and the lower reinforcing roll chock pressing device 40.
- the roll chock rolling direction force control device 15 is based on the control instruction of the inter-roll cross control device 23 to be described later. By driving the device 13 and applying a predetermined pressing force, a state where the chock position can be controlled is formed.
- the roll chock position control device 16 performs drive control of the drive device 11 with an upper work roll chock position detection function, the drive device 12 with a lower work roll chock position detection function, and the drive device 14 with an upper reinforcement roll chock position detection function.
- the roll chock position control device 16 is also simply referred to as a position control device.
- the roll chock position control device 16 is based on the control instruction of the inter-roll cross control device 23 so that the rolling load difference, which is the difference between the rolling work load on the roll side and the driving load on the driving side, falls within a predetermined range.
- the drive device 11 with the upper work roll chock position detection function, the drive device 12 with the lower work roll chock position detection function, and the drive device 14 with the upper reinforcement roll chock position detection function are driven.
- the drive devices 11, 12, and 14 with position detection function are arranged on both sides of the work side and the drive side, and the same amount is reversed in the work side and the drive side in the rolling direction on the work side and the drive side. By controlling, only the roll cross angle can be changed without changing the average rolling direction position on the working side and the driving side.
- the drive motor control device 22 controls the drive motor 21 that rotationally drives the upper work roll 1 and the lower work roll 2.
- the drive motor control device 22 according to the present embodiment controls driving of the upper work roll 1 or the lower work roll 2 based on an instruction from the inter-roll cross control device 23.
- the inter-roll cross control device 23 is configured so that the inter-roll cross angle of the upper work roll 1, the lower work roll 2, the upper reinforcing roll 3, and the lower reinforcing roll 4 constituting the rolling mill is zero. Control the position.
- the roll-to-roll cross control device 23 is configured such that the roll chock rolling direction force control device 15 and the roll chock are such that a reduction in load in the reduction direction, which is a difference between the reduction in load on the work side of the roll and the reduction in load on the drive side, is within a predetermined range. Control instructions are given to the position control device 16 and the drive motor control device 22 so that the cross between the rolls is eliminated. In addition, the detail of the setting method of the said rolling mill is mentioned later.
- the increase bending control device 26 is a device that controls the entry-side upper increase bending device 24a, the output-side upper increase bending device 24b, the entry-side lower increase bending device 25a, and the output-side lower increase bending device 25b. .
- the increase bending control device 26 controls the increase bending device so as to apply an increase bending force to the work roll chock based on an instruction from the inter-roll cross control device 23.
- the increase bending control device 26 controls the increase bending device, for example, when performing crown control or shape control of the material to be rolled. You may go.
- a rolling device 27 is provided in the rolling mill.
- the reduction device 27 is a device that is installed above the uppermost roll (upper reinforcing roll 3 in FIG. 2) and presses the roll downward.
- the position of each roll in the rolling down direction can be adjusted by rolling down the roll from above with the rolling down device 27. For example, when the upper work roll 1 and the lower work roll 2 are put into the kiss roll state, the positions of the upper work roll 1 and the lower work roll 2 are adjusted by applying a predetermined load to the upper work roll 1 and the lower work roll 2. .
- upper reduction / downward direction load detection devices 28 a and 28 b and a reduction device 27 are provided at a reduction fulcrum position 30 a between the upper reinforcement roll chock 7 and the housing 30, and between the lower reinforcement roll chock 8 and the housing 30.
- Downward pressure downward load detecting devices 29a and 29b are provided at the downward pressure fulcrum position 30b.
- FIG. 2 shows only the upper and lower load detecting device 28a and 29a on the working side, but as shown in FIG. 1, the driving side on the back side of FIG. Are provided with an upward pressure downward load detection device 28b and a downward pressure downward load detection device 29b.
- the up-and-down load detecting devices 28a and 28b and the down-and-down load detecting devices 29a and 29b are devices that detect the down-direction load that is disposed at the fulcrum fulcrum position of the upper and lower reinforcing roll chocks and that acts in the down-direction.
- the load detection devices 28a and 28b detect a reduction direction load related to the uppermost roll
- the lower pressure reduction direction load detection devices 29a and 29b detect a reduction direction load related to the lowermost roll.
- the up / down direction load difference calculation unit 32 calculates a down direction load difference, which is a difference between the work side down load and the drive side down load detected by the up / down load detecting devices 28a and 28b.
- the downward pressure downward load difference calculation unit 33 calculates a downward load difference that is a difference between the work-side downward load detected by the downward-pressure downward load detection devices 29a and 29b and the drive-side downward load.
- the roll-down load difference calculated by the roll-up / down-direction load difference calculation section 32 and the roll-down / down-direction load difference calculation section 33 is output to the inter-roll cross control device 23.
- the inter-roll cross control device 23 recognizes the state of the inter-roll cross based on the input rolling direction load difference.
- the driving devices 11 and 12 with position detection function are provided on the exit side of the rolling mill
- the pressing devices 9 and 10 are provided on the entry side
- the upper reinforcing roll chock 7 is provided on the rolling mill.
- the drive device 14 with position detection function on the entry side, the press device 13 on the exit side, and the lower reinforcing roll chock 8 the example in which the press device 40 is arranged on the exit side of the rolling mill has been described, but the present invention is limited to this example. Not. For example, these arrangements may be installed reversely on the entry side and the exit side of the rolling mill, or may be installed in the same direction with work rolls and reinforcing rolls.
- the drive devices with position detection function 11, 12, and 14 have been described as being disposed on both sides of the work side and the drive side, and the position of each is controlled, but the present invention is not limited to this example. It is possible to control the roll cross angle by arranging these devices only on one side of the working side and the driving side, or by operating only one side and using the opposite side as a fulcrum of rotation to control the position, Needless to say, the same effect of reducing the cross between rolls can be obtained.
- 2 shows an example in which only the pressing device 40 is provided in the lower reinforcing roll chock 8 of the lower reinforcing roll 4 as the reference roll, but the present invention is not limited to this example, and the entry side of the lower reinforcing roll chock 8 is used.
- the reference reinforcing roll chock can be driven by the roll chock position control device 16 to finely adjust the position of the reference roll. It becomes possible. Further, by arranging the drive device with position detection function on all the rolls, the reference roll may be changed according to the situation, and the control may be performed based on the changed reference roll.
- FIG. 3A and FIG. 3B are flowcharts for explaining a setting method of the rolling mill that performs roll chock position adjustment based on the rolling direction load during roll normal rotation and roll reverse rotation according to the present embodiment.
- FIG. 4A is an explanatory diagram showing a procedure for adjusting the roll chock position in the setting method of the rolling mill according to the present embodiment, and shows the position adjustment in the roll gap open state.
- FIG. 4B is an explanatory diagram illustrating a procedure for adjusting the roll chock position in the setting method of the rolling mill according to the present embodiment, and illustrates position adjustment in a kiss roll state.
- FIG. 5 is a schematic side view and a schematic front view showing an example of a driving state of the rolling mill at the time of identifying the cross angle between rolls.
- the load distribution changes with the change in the direction of the thrust force between the lower work roll 2 and the lower reinforcing roll 4 during forward and reverse rotation of the roll, but the difference here is a slight change. Is not specified.
- FIG. 6 is an explanatory diagram showing the difference in the rolling direction load obtained when the lower roll is rotated forward and when it is reversed in the rolling mill in the state of FIG. 5.
- the lower reinforcing roll 4 will be described as a reference roll.
- the reference roll may be either the uppermost roll or the lowermost roll in the reduction direction
- the upper reinforcing roll 3 may be the reference roll. is there.
- the upper pressure downward load detection devices 28a and 28b are used.
- the difference in the downward direction load is calculated from the detected downward load on the drive side and the working side, and the difference in the downward direction load is calculated from the downward load on the drive side and the working side detected by the downward pressure downward load detecting devices 29a and 29b. Is calculated.
- the position of the roll chock is adjusted based on the calculated rolling direction load difference, and the roll-to-roll cross of each roll of the rolling mill is within a predetermined range.
- the rolling direction position of the roll chock of the reference roll is fixed as the reference position, and the position of the roll chock of the roll other than the reference roll is moved to adjust the position of the roll chock. This will be described in detail below.
- the first adjustment for adjusting the position when the roll gap is open the upper work roll and the lower work roll are opened, an increase bending force is applied, and a load is applied between the work roll and the reinforcing roll.
- the upper and lower work roll chock positions are controlled so that the difference in the rolling direction load generated by the thrust force between the rolls becomes a predetermined target value.
- the inter-roll cross control device 23 is in an open state in which the roll gap between the upper work roll 1 and the lower work roll 2 has a predetermined gap with respect to the reduction device 27.
- the roll position in the reduction direction is adjusted (S100).
- the reduction device 27 applies a predetermined load to the roll based on the instruction, and opens the roll gaps of the work rolls 1 and 2.
- the inter-roll cross control device 23 instructs the increase bending control device 26 to apply a predetermined increase bending force to the work roll chocks 5 and 6 by the increase bending devices 24a, 24b, 25a, and 25b.
- the increase bending control device 26 controls each increase bending device 24a, 24b, 25a, 25b based on the instruction, and applies a predetermined increase bending force to the work roll chocks 5, 6.
- a predetermined load can be applied only between the upper and lower work rolls and the reinforcing roll without applying a load between the upper and lower work rolls.
- the increment bending apparatus has a balancer function for lifting the weight of the work roll, the order of steps S100 and S102 is reversed, that is, after the increase bending force is applied, the upper and lower work rolls The gap may be adjusted.
- the inter-roll cross control device 23 Instruct the drive motor controller 22 and Drive the drive motor 21 and The work roll is rotated at a predetermined rotation speed and a predetermined rotation direction (S104).
- the rotation speed and rotation direction which are roll rotation conditions, are preset
- the drive motor control device 22 The upper work roll 1 and the lower work roll 2 are rotated under the set roll rotation conditions.
- Up / down load detecting device 28a, 28b and lower pressure downward load detection device 29a, 29b detects the load in the rolling direction on the working side and the driving side, This is output to the upper pressure lower load difference calculation unit 32 and the lower pressure lower load difference calculation unit 33.
- the upper pressure lower load difference calculating unit 32 and the lower pressure lower load difference calculating unit 33 are: When an input of rolling direction load is received, In each case, a difference in the reduction direction load, which is a difference between the reduction direction load on the work side and the reduction direction load on the drive side, is calculated.
- the calculated load difference in the rolling direction during normal roll rotation is Is input to the inter-roll cross control device 23, Reference value 1 (corresponds to the “first reference value” of the present invention). (S106).
- the inter-roll cross control device 23 drives the drive motor 21 by the drive motor control device 22 to rotate the work roll at a predetermined rotation speed and a predetermined rotation direction (S108).
- the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b respectively detect the down load on the working side and the driving side. This is output to the upper pressure lower load difference calculation unit 32 and the lower pressure lower load difference calculation unit 33.
- the rotation direction of each work roll 1 and 2 in step S108 is the reverse rotation direction.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side.
- the difference is calculated, and the calculated differential load at the time of roll reverse rotation is output to the inter-roll cross control device 23.
- the inter-roll cross control device 23 determines the first control target for each of the upper roll system and the lower roll system from the deviation between the rolling direction load difference during the reverse rotation of the roll and the reference value 1 calculated in step S106.
- the value is calculated (S110).
- the first control target value is preferably half the deviation from the reference value 1.
- the first control target value may be set based on the degree of difference in the magnitude of the rolling direction load difference between forward rotation and reverse rotation based on the previously identified result. That is, the first control target value may be a value other than half of the deviation from the reference value 1.
- the inter-roll cross control device 23 compares the rolling direction load difference at the time of the reverse rotation of the roll calculated in step S112 with the first control target value calculated in step S110. It is determined whether or not (S114). Note that, in the determination in step S114, the first control target value of the rolling direction load difference at the time of roll reverse rotation is not only the case where the rolling direction load difference at the time of roll reverse rotation and the first control target value completely coincide.
- the allowable range is, for example, the amount of meandering at the tail end (mm) or the actual camber value per 1 m of the tip (mm / m) and the rolling direction load difference at the time of roll reversal in the actual hot rolling process.
- the amount of asymmetric deformation obtained from roll deformation analysis or the like is converted into a reduction leveling amount, and the relationship with the deviation from the first control target value, that is, the relationship with the micro cross between the rolls is obtained,
- the camber may be determined to be below the standard required for the product.
- step S114 If it is determined in step S114 that the load difference in the rolling direction during the reverse rotation of the roll is not the first control target value or is not within the allowable range, the inter-roll cross control device 23 controls the roll chock position control device 16. Then, an instruction is given to adjust the position of the roll-type work roll chock that does not satisfy the requirement of step S114 (S116). And if the position of a work roll chock is adjusted, the process from step S112 will be performed again. At this time, the position of the upper reinforcing roll chock instead of the upper working roll chock may be controlled so that the differential load caused by the thrust force between the upper working roll and the reinforcing roll is reduced.
- step S114 If it is determined in step S114 that the rolling load difference during reverse rotation of the roll coincides with the first control target value or is within the allowable range, the inter-roll cross control device 23 is shown in FIG. 3B. Transition to processing.
- a rolling direction load difference that is a difference between the working side rolling direction load and the driving side rolling direction load is calculated (P11 in FIG. 4A, P12).
- the rolling direction load difference of each roll system is calculated from the following equation (1).
- P df1 T is the difference (upper reference value 1 T ) in the rolling direction load measurement value between the working side and the driving side of the upper roll system in the roll normal rotation state
- P df1 B is the roll normal rotation state Is the difference (lower reference value 1 B ) in the measured value in the rolling direction load between the working side and the driving side of the lower roll system.
- Step reference value 1 of S106 refers to the upper reference value 1 T and the lower reference value 1 B.
- P W T is a measured value in the rolling direction load on the work side of the upper roll system in the roll normal rotation state
- P W B is a measured value in the down direction load on the work side of the lower roll system in the roll normal rotation state
- P D T is a measured value in the rolling direction load on the driving side of the upper roll system in the roll normal rotation state
- P D B is a measured value in the rolling direction load on the driving side of the lower roll system in the roll normal rotation state.
- the first control target value is calculated from the measured values on the working side and the driving side of the upper and lower rolling direction loads measured in the roll reverse rotation state and the reference value 1 calculated by the above formula (1).
- the relationship between the rolling direction load difference which is the difference in the rolling direction load between the working side and the driving side, during the forward rotation and reverse rotation of the roll was examined.
- the roll gap between the work rolls 1 and 2 was opened.
- the upper work roll 1 is supported by the upper work roll chock 5a on the work side and the upper work roll chock 5b on the drive side.
- the lower work roll 2 is supported by the lower work roll chock 6a on the work side and the lower work roll chock 6b on the drive side.
- the upper reinforcing roll 3 is supported by the upper reinforcing roll chock 7a on the work side and the upper reinforcing roll chock 7b on the driving side.
- the lower reinforcing roll 4 is supported by the lower reinforcing roll chock 8a on the work side and the lower reinforcing roll chock 8b on the driving side.
- An increase bending force is applied to the upper work roll chock 5a, 5b and the lower work roll chock 6a, 6b by an increase bending apparatus (not shown) with the work rolls 1, 2 being separated from each other.
- FIG. 6 is a view showing the relationship between the roll normal rotation and the roll reverse rotation when the cross roll angle of the lower work roll is changed by 0.1 ° so as to face the exit side on the driving side in a small rolling mill having a work roll diameter of 80 mm. It is one measurement result which detected the change of the rolling direction load difference.
- the increase bending force applied to each work roll chock was 0.5 tonf / chock.
- the difference in the rolling direction load which is the difference between the driving side rolling direction load and the working side rolling direction load obtained during the forward roll rotation
- the rolling direction load difference which is the difference between the driving side rolling direction load and the work side rolling direction load acquired during the reverse rotation of the roll
- the magnitude of the rolling direction load difference is approximately the same between the roll forward rotation and the roll reverse rotation, but the directions are opposite.
- Control target value (first control target value).
- the first control target value can be expressed by the following equation (2).
- P ′ dfT1 T is the first control target value for the upper roll system
- P ′ dfT1 B is the first control target value for the lower roll system.
- 'the W T upper roll system tasks lateral pressure downward measured load
- P in the roll reversal state' P is W B is working side pressure downward load measurements of lower roll system in the roll reversal state.
- P 'D T is the pressing direction measured load on the drive side of the upper roll system in roll reversal state
- P' D B is the pressing direction measured load on the drive side of the lower roll system in roll reversal state
- P 'df T is the difference of the work side and drive side of the rolling direction measured load of the upper roll system in roll reversal state
- P 'df B is the working side and the driving side of the rolling direction measured load of the lower roll system in the roll reversal state It is a difference.
- the first control target values for the upper roll system and the lower roll system can be calculated.
- the formula (2) is defined assuming that the magnitude of the rolling direction load difference is approximately the same between the roll forward rotation and the roll reverse rotation. Due to the influence of the above, there may be a difference in the characteristics of the load difference in the rolling direction in the direction of the thrust force acting in the forward rotation and reverse rotation.
- the first control target value may be set based on the degree of difference in the magnitude of the rolling direction load difference between forward rotation and reverse rotation based on the previously identified result. That is, the first control target value may be a value other than half of the deviation from the reference value 1.
- the driving of the rook chock position during roll reversal is for roll chock of rolls other than the standard roll. That is, for the upper roll system, the position of the upper work roll chock may be controlled as shown in the center of FIG. 4A (P13), or the position of the upper reinforcing roll chock may be controlled as shown in the lower side of FIG. 4A. Good (P15). On the other hand, for the lower roll system, the lower reinforcing roll 4 is not moved because it is a reference roll, and the position of the lower work roll chock is controlled as shown in the center and lower side of FIG. 4A (P14, P16).
- the inter-roll cross control device 23 drives the drive motor 21 with the drive motor control device 22 to rotate the work roll at a predetermined rotation speed and a predetermined rotation direction (S120).
- the rotation speed and the rotation direction which are roll rotation conditions, are set in advance, and the drive motor controller 22 rotates the upper work roll 1 and the lower work roll 2 under the set roll rotation conditions.
- the rotation direction of each work roll 1 and 2 in step S120 is a normal rotation direction.
- the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b detect the lower and lower loads on the working side and the driving side, respectively. It is output to the calculation unit 32 and the downward pressure downward load difference calculation unit 33.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side. Calculate the difference.
- the calculated rolling direction load difference at the time of roll forward rotation is input to the inter-roll cross control device 23 and is set to the reference value 2 (corresponding to the “second reference value” of the present invention) (S122).
- the inter-roll cross control device 23 drives the drive motor 21 by the drive motor control device 22 to rotate the work roll at a predetermined rotation speed and a predetermined rotation direction (S124).
- the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b respectively detect the down load on the working side and the driving side. This is output to the upper pressure lower load difference calculation unit 32 and the lower pressure lower load difference calculation unit 33.
- the rotation direction of each work roll 1 and 2 in step S124 is the reverse rotation direction.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side.
- the difference is calculated, and the calculated rolling direction load difference at the time of reverse rotation of the roll is output to the inter-roll cross control device 23.
- the inter-roll cross control device 23 determines the second control target for each of the upper roll system and the lower roll system from the deviation between the rolling direction load difference during the reverse rotation of the roll and the reference value 2 calculated in step S122.
- the value is calculated (S126).
- the second control target value is, for example, a value that is half the deviation of the reference value 2.
- the second control target value may be set according to the degree of difference in the magnitude of the rolling direction load difference between forward rotation and reverse rotation based on the previously identified result. That is, the second control target value may be a value other than half of the deviation from the reference value 2.
- the rolling load on the working side and the rolling load on the driving side at the time of roll reversal are measured, and the rolling is the difference between them.
- a directional load difference is calculated (S128).
- the roll-to-roll cross control device 23 compares the rolling direction load difference at the time of reverse rotation of the roll calculated in step S128 with the second control target value calculated in step S126. Whether or not is determined (S130). Note that, in the determination of step S130, the second control target value of the roll-down load difference at the time of roll reverse rotation is not only the case where the roll-down load difference at the roll reverse rotation and the second control target value completely coincide with each other.
- step S ⁇ b> 130 that the load difference in the rolling direction during the reverse rotation of the roll is not the second control target value or not within the allowable range
- the inter-roll cross control device 23 controls the roll chock position control device 16. Then, an instruction is given to adjust the position of the roll-type work roll chock that does not satisfy the requirement of step S130 (S132). And if the position of a work roll chock is adjusted, the process from step S128 will be performed again.
- step S130 If it is determined in step S130 that the rolling load difference during the reverse rotation of the roll coincides with the second control target value or is within the allowable range, the inter-roll cross control device 23 determines that the upper reinforcing roll 3
- the roll gap between the upper work roll 1 and the lower work roll 2 is predetermined with respect to the reduction device 27, assuming that the cross between rolls of the upper work roll 1, the lower work roll 2 and the lower reinforcement roll 4 is adjusted within an allowable range. (S134). Thereafter, the rolling position zero adjustment by the rolling mill or rolling of the material to be rolled is started.
- P df2 T is the difference (upper reference value 2 T ) between the measured values in the rolling direction between the work side and the drive side of the upper roll system in the roll normal rotation state in the kiss roll state
- P df2 B is the kiss roll state.
- Step reference value 2 of S122 refers to the upper reference value 2 T and the lower reference value 2 B.
- the rotation of the roll is reversed in the kiss roll state, and the second control is performed from the measured values on the working side and the driving side of the measured upper and lower rolling loads and the reference value 2 calculated by the above equation (3).
- the target value is set to 1 ⁇ 2 of the deviation from the reference in the roll reverse rotation state when the roll normal rotation state is set as a reference, between the upper and lower work rolls and the reinforcing rolls.
- the control target value (second control target value) of the difference in the rolling direction load at which the thrust force becomes zero can be obtained. That is, the second control target value can be expressed by the following equation (4).
- P ′ dfT2 T is a second control target value for the upper roll system
- P ′ dfT2 B is a second control target value for the lower roll system.
- the second control target values for the upper roll system and the lower roll system can be calculated.
- the load is generated by the thrust force between the upper and lower work rolls in a kiss roll state in which the upper and lower work rolls are in contact. Since this is the difference in the rolling direction load, the influence of this cross between rolls appears in the same way on both the upper and lower sides. Therefore, in this case, at least one of the upper and lower values may be used to control the work roll and reinforcing roll chock positions on the side opposite to the reference roll (P23 in FIG. 4B).
- the magnitude of the rolling direction load difference is approximately the same between the roll forward rotation and the roll reverse rotation, and the formula (4) is defined. Due to the influence of this, there may be a difference in the characteristics of the load difference in the rolling direction in the direction of the thrust force during forward rotation and reverse rotation.
- the second control target value may be set according to the degree of difference in the magnitude of the rolling direction load difference between forward rotation and reverse rotation based on the previously identified result. That is, the second control target value may be a value other than half of the deviation from the reference value 2.
- the roll-direction load difference is substantially the same between the roll forward rotation and the roll reverse rotation, but the direction is reversed, so that the roll-to-roll cross is calculated from the roll-direction load difference.
- the control target value for making the angle zero is calculated and set, and the first adjustment and the second adjustment are performed before the reduction position zero point adjustment or before the rolling starts.
- FIGS. 7A and 7B are flowcharts for explaining a setting method of the rolling mill according to the present embodiment, and show an example in which the position adjustment is performed based on the rolling direction load when the roll is stopped and when the roll is rotated.
- FIG. 8A is an explanatory diagram showing a procedure for adjusting the roll chock position in the setting method of the rolling mill according to the present embodiment, and shows the position adjustment in the roll gap open state.
- FIG. 8B is an explanatory diagram illustrating a procedure for adjusting the roll chock position in the setting method of the rolling mill according to the present embodiment, and illustrates position adjustment in a kiss roll state.
- the description of the load distribution acting between the rolls is omitted.
- standard roll should just be either one of the roll in the uppermost part or the lowest part in the rolling-down direction, and the upper reinforcement roll 3 becomes a reference
- the upper pressure downward load detection devices 28a and 28b are used.
- a reduction load difference is calculated from the detected reduction load on the drive side and the work side, and a reduction load difference is calculated from the reduction load on the drive side and the operation side detected by the down pressure load detection devices 29a and 29b. Is calculated.
- the position adjustment of a roll chock is performed based on the calculated rolling direction load difference, and the cross between rolls of each roll of a rolling mill is set within a predetermined range.
- the control target value for adjusting the position of the roll chock is derived using the rolling direction load on the working side and the driving side of the upper roll system and the lower roll system, which are measured when the roll is stopped and rotated.
- the rolling direction position of the roll chock of the reference roll is fixed as the reference position, and the position of the roll chock of the roll other than the reference roll is moved to adjust the position of the roll chock. This will be described in detail below.
- the first adjustment for adjusting the position when the roll gap is open the upper work roll and the lower work roll are opened, an increase bending force is applied, and a load is applied between the work roll and the reinforcing roll.
- the upper and lower work roll chock positions are controlled so that the difference in the rolling direction load generated by the thrust force between the rolls becomes a predetermined target value.
- the inter-roll cross control device 23 is in an open state in which the roll gap between the upper work roll 1 and the lower work roll 2 has a predetermined gap with respect to the reduction device 27.
- the roll position in the reduction direction is adjusted (S200).
- the reduction device 27 applies a predetermined load to the roll based on the instruction, and opens the roll gaps of the work rolls 1 and 2.
- the inter-roll cross control device 23 instructs the increase bending control device 26 to apply a predetermined increase bending force to the work roll chocks 5 and 6 by the increase bending devices 24a, 24b, 25a, and 25b.
- the increase bending control device 26 controls each increase bending device 24a, 24b, 25a, 25b based on the instruction, and applies a predetermined increase bending force to the work roll chocks 5, 6.
- a predetermined load can be applied only between the upper and lower work rolls and the reinforcing roll without applying a load between the upper and lower work rolls.
- the increment bending apparatus has a balancer function for lifting the weight of the work roll, the order of steps S200 and S202 is reversed, that is, the upper and lower work rolls are applied after the increase bending force is applied.
- the gap may be adjusted.
- the inter-roll cross control device 23 puts the roll in a stopped state (S204). Then, in the roll stop state, the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b detect the lower load on the working side and the driving side, respectively, and the upper and lower load difference calculating unit 32 and It is output to the lower pressure downward load difference calculation unit 33.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side. Calculate the difference.
- the calculated rolling direction load difference when the roll is stopped is input to the inter-roll cross control device 23 to be a reference value 1 (corresponding to the “first reference value” of the present invention). Based on this, the first control target value is calculated (S206).
- the inter-roll cross control device 23 drives the drive motor 21 by the drive motor control device 22 to rotate the work roll at a predetermined rotation speed and a predetermined rotation direction (S208).
- the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b detect the lower and lower loads on the working side and the driving side, respectively. And output to the lower pressure downward load difference calculation unit 33.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side. The difference is calculated, and the calculated rolling direction load difference during roll rotation is output to the inter-roll cross control device 23 (S210).
- the roll-to-roll cross control device 23 compares the rolling direction load difference during roll rotation calculated in step S210 with the first control target value calculated in step S206, and determines whether or not they match. Is determined (S212).
- the first control target value of the rolling direction load difference during roll rotation is not limited to the case where the rolling direction load difference during roll rotation and the first control target value completely match. It also includes the case where the deviation from is within a predetermined range.
- the inter-roll cross control device 23 controls the roll chock position control device 16.
- step S214 an instruction is given to adjust the position of the roll-type work roll chock that does not satisfy the requirements of step S212 (S214). Then, when the positions of the upper and lower work roll chocks are adjusted, the processing from step S210 is executed again. At this time, the position of the upper reinforcing roll chock instead of the upper working roll chock may be controlled so that the differential load caused by the thrust force between the upper working roll and the reinforcing roll is reduced.
- step S212 If it is determined in step S212 that the rolling load difference during reverse rotation of the roll coincides with the first control target value or is within the allowable range, the inter-roll cross control device 23 is shown in FIG. 7B. Transition to processing.
- P 0 df1 T is a difference (upper reference value 1 T ) in the rolling direction load measurement value between the working side and the driving side of the upper roll system in the roll stopped state
- P 0 df1 B is the roll stopped state.
- Step reference value 1 of S206 refers to the upper reference value 1 T and the lower reference value 1 B.
- the P 0 W T is upper roll system working side of the pressing direction measured load
- P 0 W B is the pressing direction measured load of the working side of the lower roll system in the roll stop state in the roll stop state.
- the P 0 D T is upper roll system drive side pressing direction measured load
- P 0 D B is the pressing direction measured load on the drive side of the lower roll system in the roll stop state in the roll stop state.
- the first control target value is set.
- the relationship between the rolling direction load difference when the roll was stopped and when the roll was rotated was examined.
- FIG. 9 for example, in a rolling mill having the same configuration as in FIG. State. An increase bending force is applied to the upper work roll chock 5a, 5b and the lower work roll chock 6a, 6b by an increase bending apparatus (not shown) with the work rolls 1, 2 being separated from each other.
- FIG. 10 shows the change in the rolling direction load difference, which is the difference in the rolling direction load detected on the driving side and the working side, when the roll is stopped and when the roll is rotated.
- a predetermined inter-roll cross angle was provided between the lower work roll 2 and the lower reinforcement roll 4 to detect a reduction load in a state where the roll was stopped, and then the roll was rotated to detect a reduction load.
- FIG. 10 is a graph showing a difference between the roll normal rotation and the roll reverse rotation when the cross roll angle of the lower work roll is changed by 0.1 ° so as to face the exit side on the driving side in a small rolling mill having a work roll diameter of 80 mm. It is one measurement result which detected the change of the rolling direction load difference.
- the increase bending force applied to each work roll chock was 0.5 tonf / chock.
- the rolling direction load difference when the roll is rotated is larger in the negative direction than the rolling direction load difference when the roll is stopped.
- the rolling direction load difference is different between when the roll is stopped and when the roll is rotated.
- the first control target value is set as the first control target value based on the rolling direction load difference in the roll stopped state. By controlling the position, the thrust force between the upper and lower work rolls and the reinforcing roll can be made zero.
- the first control target value is represented by the following formula (6).
- P r dfT1 T is a first control target value for the upper roll system
- P r dfT1 B is a first control target value for the lower roll system.
- the roll rotation state here does not particularly define the direction of rotation, and the rotation of the roll may be forward rotation or reverse rotation. In this way, the first control target values for the upper roll system and the lower roll system can be calculated.
- the driving of the rook chock position during roll rotation is for roll chock of rolls other than the standard roll. That is, for the upper roll system, as shown in the center of FIG. 8A, the position of the upper work roll chock may be controlled (P33), or as shown in the lower side of FIG. 8A, the position of the upper reinforcing roll chock may be controlled. Good (P35). On the other hand, for the lower roll system, the lower reinforcing roll 4 is not moved because it is a reference roll, and the position of the lower work roll chock is controlled as shown in the center and lower side of FIG. 8A (P34, P36).
- the inter-roll cross control device 23 puts the roll in a stopped state (S218). Then, in the roll stop state, the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b detect the lower load on the working side and the driving side, respectively. It is output to the lower pressure downward direction difference load difference calculation unit 33.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side. Calculate the difference.
- the calculated rolling direction load difference when the roll is stopped is input to the inter-roll cross control device 23 to be a reference value 2 (corresponding to the “second reference value” of the present invention). Based on this, the second control target value is calculated (S220).
- the inter-roll cross control device 23 drives the drive motor 21 by the drive motor control device 22 to rotate the work roll at a predetermined rotation speed and a predetermined rotation direction (S222).
- the upper and lower load detecting devices 28a and 28b and the lower and lower load detecting devices 29a and 29b detect the lower and lower loads on the working side and the driving side, respectively. And output to the lower pressure downward load difference calculation unit 33.
- the up-down direction load difference calculating unit 32 and the down-down direction load difference calculating unit 33 are each the down-direction load that is the difference between the down-side load on the working side and the down-side load on the driving side. The difference is calculated, and the calculated rolling direction load difference during the roll rotation is output to the inter-roll cross control device 23 (S224).
- the inter-roll cross control device 23 compares the rolling direction load difference during roll rotation calculated in step S224 with the second control target value calculated in step S220, and determines whether or not they match. Is determined (S226).
- the second control target value of the rolling direction load difference during roll rotation is not limited to the case where the rolling direction load difference during roll rotation and the second control target value coincide completely. It also includes the case where the deviation from is within a predetermined range. If it is determined in step S226 that the rolling direction load difference during roll rotation is not the second control target value or not within the allowable range, the roll-to-roll cross control device 23 controls the roll chock position control device 16. Then, an instruction is given to adjust the position of the roll-type work roll chock that does not satisfy the requirement of step S226 (S228). And if the position of a work roll chock is adjusted, the process from step S224 will be performed again.
- step S226 when it is determined in step S226 that the rolling direction load difference during the reverse rotation of the roll coincides with the second control target value or is within the allowable range, the inter-roll cross control device 23 performs the upper reinforcement.
- the roll gap between the upper work roll 1 and the lower work roll 2 with respect to the rolling-down device 27 assuming that the roll-to-roll cross of the roll 3, the upper work roll 1, the lower work roll 2 and the lower reinforcing roll 4 is adjusted within an allowable range. Is adjusted to a predetermined size (S230). Thereafter, the rolling position zero adjustment by the rolling mill or rolling of the material to be rolled is started.
- P 0 df2 T is the difference (upper reference value 2 T ) between the measured values in the rolling direction between the working side and the driving side of the upper roll system in the roll stop state in the kiss roll state
- P 0 df2 B is The difference (lower reference value 2 B ) in the rolling direction load measurement value between the working side and the driving side of the lower roll system in the roll stop state in the kiss roll state.
- Step reference value 2 of S220 refers to the upper reference value 2 T and the lower reference value 2 B.
- the roll is rotated in the kiss roll state, and the second control target value is calculated from the measured values on the working side and the driving side of the measured upper and lower rolling direction loads and the reference value 2 calculated by the above equation (7). Is calculated.
- the second control target value is set to a control target value (second control target value) that sets the thrust force between the upper and lower work rolls to zero with reference to the roll stop state. Can do.
- the second control target value can be expressed by the following equation (8).
- P r dfT2 T is a second control target value for the upper roll system
- P r dfT2 B is a second control target value for the lower roll system.
- the load is generated by the thrust force between the upper and lower work rolls in the kiss roll state in which the upper and lower work rolls are in contact. Since this is the difference in the rolling direction load, the influence of this cross between rolls appears in the same way on both the upper and lower sides. Therefore, in this case, at least one of the upper and lower values may be used to control the position of the work roll and the reinforcing roll chock on the side opposite to the reference roll (P43).
- FIG. 11 is an explanatory view showing the arrangement of the work rolls 1 and 2 and the reinforcing rolls 3 and 4 in the rolling mill with the roll gap open.
- FIG. 12 is an explanatory diagram showing the definition of the cross angle between rolls.
- FIG. 13 is a graph showing experimental results performed in a small rolling mill having a work roll diameter of 80 mm, and showing a relationship between the reinforcing roll cross angle and the rolling direction load difference in the roll gap open state.
- the rolling load difference between the upper and lower reinforcing rolls is measured when the reinforcing roll cross angle is set in the increasing direction and when the reinforcing roll cross angle is set in the decreasing direction, and the measured value in the increasing direction and the decreasing direction are measured.
- the value obtained by averaging the measured values at is displayed.
- the roll gap between the upper work roll 1 and the lower work roll 2 was opened, and a state in which an increase bending force was applied to the work roll chock by an increase bending apparatus was formed.
- the change of the rolling direction load difference when changing the cross angle of the upper reinforcement roll 3 and the lower reinforcement roll 4 was investigated.
- the cross angle of the reinforcing roll indicates that the working side of the roll axis A roll extending in the roll body length direction is positive in the direction from the width direction (X direction) to the exit side.
- the increment bending force was 0.5 tonf per roll chock.
- FIG. 14 is an explanatory view showing the arrangement of the work rolls 1 and 2 and the reinforcing rolls 3 and 4 in the rolling mill in a kiss roll state.
- FIG. 15 is a graph showing a relationship between the pair cross angle between the work roll and the reinforcing roll and the rolling direction load difference in the kiss roll state.
- the load difference in the rolling direction between the upper and lower reinforcing rolls is measured when the pair cross angle between the work roll and the reinforcing roll is set in the increasing direction and when it is set in the decreasing direction. A value obtained by averaging the measured value and the measured value in the decreasing direction is displayed.
- the upper work roll 1 and the lower work roll 2 are in a kiss roll state, and the change in the rolling direction load difference when the pair cross angle between the work roll and the reinforcing roll is changed is examined. .
- the kiss roll tightening load was 6.0 tonf.
- the housing liner and the chock liner were periodically exchanged without using the function of the inter-roll cross control device of the present invention, and the facilities were managed so that the inter-roll cross did not occur.
- the facilities were managed so that the inter-roll cross did not occur.
- the thrust reaction force of each roll is measured in the kiss roll tightened state using the function of the inter-roll cross control device according to the first embodiment, and is shown in FIGS. 3A and 3B.
- the roll chock position of each roll was controlled so that the rolling direction load difference was within a preset allowable range before rolling.
- the meandering of 12 mm or less remains. The rolling line could be passed through without causing drawing in the rolled material.
- the rolling direction load difference which is the difference between the rolling direction load on the working side and the driving side measured before rolling, is calculated, and within the allowable range based on appropriate logic,
- the cross-roll cross itself is eliminated, and the left-right asymmetric deformation of the material to be rolled caused by the thrust force caused by the cross-roll cross can be eliminated. Therefore, it is possible to stably produce a metal plate material that does not meander and camber or is extremely light in meander and camber.
- the housing liner and the chock liner were periodically exchanged without using the function of the inter-roll cross control device of the present invention, and the facilities were managed so that the inter-roll cross did not occur.
- the roll chock position was adjusted according to the processing flow shown in FIGS. 7A and 7B before rolling using the function of the inter-roll cross control device according to the second embodiment. That is, first, in the state where the roll gap was opened and the increase bending force was applied, the rolling direction load was measured while the rotation of the roll was stopped and stopped, and the positions of the upper and lower work roll chocks were controlled. Next, the roll load is measured in the kiss roll state, the roll direction load is measured while the roll is stopped and stopped, and the roll chocks of the upper and lower work rolls and the reinforcing roll are positioned so that the roll direction load difference during rotation falls within a preset allowable range. Controlled.
- Table 1 shows measured values of the occurrence of camber with respect to the number of representative rolls for the present invention and the conventional method.
- the camber results per 1 m of the tip of the material to be rolled the values immediately before the reinforcement roll replacement and the housing liner replacement are suppressed to a relatively small value of 0.12 mm / m in the present invention. I understand that.
- the camber actual value is larger than that in the case of the present invention at the time immediately before the replacement of the reinforcing roll or the replacement of the housing liner.
- the method of the present invention by calculating the rolling direction load difference before rolling and performing chock position control of each roll with respect to the reference roll so as to fall within the allowable range based on appropriate logic.
- the cross between rolls itself is eliminated, and the asymmetric deformation of the material to be rolled caused by the thrust force caused by the cross between rolls can be eliminated. Therefore, it is possible to stably produce a metal plate material that does not meander and camber or is extremely light in meander and camber.
- a drive device with a roll chock position detection function that detects the position of the work roll chock in the rolling direction
- the present invention is not limited to such an example.
- the position of the work roll chock in the rolling direction can be measured by using a servo motor with a rotation angle detection function instead of the roll chock position detection device. That is, like the upper work roll 1 and the upper work roll chock 5 shown in FIG. 16, in the rolling direction of the upper work roll chock 5, the servo with the rotation angle detection function is provided so as to face the drive device 11 with the upper work roll chock position detection function.
- a motor 34 may be provided.
- the bending device may be a device that applies a force in the rolling-down direction, and may be a hydraulic jack, for example.
- the present invention is not limited to such an example.
- the same control can be performed by omitting the first adjustment because the roll fine cross is sufficiently managed on the side without the load detecting device. Is possible.
- a four-stage rolling mill having a pair of work rolls and a pair of reinforcing rolls has been described.
- the present invention is applicable to a four-stage or more rolling mill.
- a reference roll is set as a reference in the position adjustment of the roll chock. Can be used as a reference roll.
- intermediate rolls 41 and 42 are provided between the work rolls 1 and 2 and the reinforcing rolls 3 and 4 as a plurality of rolls, respectively.
- the upper intermediate roll 41 is supported by the upper intermediate roll chock 43a on the work side and the upper intermediate roll chock 43b on the drive side (the upper intermediate roll chock 43a and 43b are collectively referred to as “upper intermediate roll chock 43”).
- the lower intermediate roll 42 is supported by the lower intermediate roll chock 44a on the work side and the lower intermediate roll chock 44b on the driving side (the lower intermediate roll chock 44a and 44b are collectively referred to as “lower intermediate roll chock 44”).
- the upper intermediate roll chock 43 and the lower intermediate roll chock 44 may also be simply referred to as roll chock.
- the roll chock position can be adjusted in the same manner as in the case of a four-high rolling mill by performing three adjustment steps as shown in FIGS. 17A to 17C.
- the roll gap of the work rolls 1 and 2 is opened, and a bending force is applied to the roll chocks 43 and 44 of the intermediate rolls 41 and 42 by a bending device.
- the positions of the roll chocks 43 and 44 of the intermediate rolls 41 and 42 and the roll chocks 43, 44, 7 and 8 of the reinforcing rolls 3 and 4 are adjusted for each of the upper roll system and the lower roll system (FIG. 17A). .
- the upper roll system is maintained in a state where the roll gaps of the work rolls 1 and 2 are maintained in an open state and a bending force is applied to the roll chocks 5 and 6 of the work rolls 1 and 2 by a bending device.
- the positions of the roll chocks 43 and 44 of the intermediate rolls 41 and 42 and the roll chocks 5 and 6 of the work rolls 1 and 2 are adjusted (FIG. 17B).
- the work rolls 1 and 2 are put into a kiss roll state, and the positions of the upper roll system and the lower roll system roll chock are adjusted (FIG. 17C).
- the position of the roll chock may be adjusted by calculating a load difference from the side load in the rolling direction and calculating a control target value.
- the work rolls 1 and 2 are rotated (forward rotation) to detect the work-side and drive-side roll-down loads for the upper roll system and the lower roll system, respectively.
- the reference value 1 (corresponding to the “first reference value” of the present invention) is calculated from the load difference from the load in the rolling direction on the side.
- the rotation direction of the work rolls 1 and 2 is reversed, and the work-side and drive-side roll-down loads are detected for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down direction are detected.
- a load difference from the load is calculated, and a first control target value is calculated from a deviation between the load difference and the reference value 1.
- Either the roll chock 43 of the intermediate roll 41 or the roll chock 7 of the reinforcing roll 3 is moved in the rolling direction to adjust the position of the roll chock.
- the first adjustment may be, for example, when the work rolls 1 and 2 on the upper right in FIG. 17A are stopped and when the work rolls 1 and 2 on the lower side in FIG.
- the position of the roll chock may be adjusted by calculating a load difference from the driving-side load on the driving side and calculating a control target value.
- the roll-down load on the work side and the drive-side load are detected for the upper roll system and the lower roll system, respectively.
- the reference value 1 is calculated from the load difference with the rolling reduction load on the side, and the first control target value is set based on the reference value 1.
- the work rolls 1 and 2 are rotated to detect the work-side and drive-side roll-down loads for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down load are detected.
- the load difference is calculated.
- the reference roll, the roll chock 44 of the intermediate roll 42 on the lower reinforcing roll 4 side in FIG. 17A, and the roll on the opposite side to the reference roll so that the load difference becomes a value within the allowable range of the first control target value.
- Either the roll chock 43 of the intermediate roll 41 or the roll chock 7 of the reinforcing roll 3 is moved in the rolling direction to adjust the position of the roll chock.
- the second adjustment is the same as the first adjustment, for example, when the work rolls 1 and 2 on the upper left in FIG. 17B are rotated forward and when the work rolls 1 and 2 on the lower side in FIG. It is also possible to adjust the position of the roll chock by calculating the load difference between the load in the rolling direction and the load in the driving direction on the driving side, and calculating the control target value.
- the work rolls 1 and 2 are rotated (forward rotation) to detect the work-side and drive-side roll-down loads for the upper roll system and the lower roll system, respectively.
- the reference value 2 (corresponding to the “second reference value” of the present invention) is calculated from the load difference from the load in the rolling direction on the side.
- the rotation direction of the work rolls 1 and 2 is reversed, and the work-side and drive-side roll-down loads are detected for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down direction are detected.
- a load difference from the load is calculated, and a second control target value is calculated from a deviation between the load difference and the reference value 2.
- the roll chock 6 of the work roll 2 on the lower reinforcing roll 4 side that is the reference roll and the roll system on the opposite side of the reference roll so that the load difference becomes a value within the allowable range of the second control target value.
- Either the roll chock 5 of the work roll 1 or the intermediate roll 41 and the roll chock 7 or 43 of the reinforcing roll 3 are moved in the rolling direction to adjust the position of the roll chock.
- the second adjustment may be, for example, when the work rolls 1 and 2 on the upper right in FIG. 17B are stopped and when the work rolls 1 and 2 on the lower side in FIG.
- the position of the roll chock may be adjusted by calculating a load difference from the driving-side load on the driving side and calculating a control target value.
- the roll-down load on the work side and the drive-side load are detected for the upper roll system and the lower roll system, respectively.
- the reference value 2 is calculated from the load difference with the rolling reduction load on the side, and the second control target value is set based on the reference value 2.
- the work rolls 1 and 2 are rotated to detect the work-side and drive-side roll-down loads for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down load are detected.
- the load difference is calculated.
- the roll chock 6 of the work roll 2 on the lower reinforcing roll 4 side that is the reference roll and the roll system on the opposite side of the reference roll so that the load difference becomes a value within the allowable range of the second control target value.
- Either the roll chock 5 of the work roll 1 or the intermediate roll 41 and the roll chock 43 or 7 of the reinforcing roll 3 are moved in the rolling direction to adjust the position of the roll chock.
- a bending device for the intermediate rolls 41 and 42 is used, a load is applied between the intermediate rolls 41 and 42 and the reinforcing rolls 3 and 4, and the bending devices for the work rolls 1 and 2 are zero or Apply a force that balances the weight of the roll.
- the chock position of the intermediate roll having the bending device or the reinforcing roll on the side opposite to the reference roll Move to adjust.
- the bending device for the intermediate rolls 41 and 42 applies a force that balances zero or the weight of the roll, and uses the bending device for the work roll as in the case of the four-high rolling mill.
- the work rolls 1 and 2 are put into a kiss roll state, and the position of the roll chock of the entire rolling mill is adjusted.
- the position of the roll chock may be adjusted when the work rolls 1 and 2 at the upper left of FIG. 17C are rotated forward and when the work rolls 1 and 2 at the lower side of FIG.
- the rolls 1 and 2 are rotated (forward rotation), and the work-side and drive-side roll-down loads are detected for the upper roll system and the lower roll system, respectively.
- the reference value 3 (corresponding to the “third reference value” of the present invention) is calculated from the load difference from the rolling direction load.
- the rotation direction of the work rolls 1 and 2 is reversed, and the work-side and drive-side roll-down loads are detected for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down direction are detected.
- a load difference from the load is calculated, and a third control target value is calculated from a deviation between the load difference and the reference value 3.
- the lower roll system is set as the reference roll system so that the load difference becomes a value within the allowable range of the third control target value.
- the position of the roll chock is adjusted by controlling the roll chock of each roll simultaneously and in the same direction while maintaining the relative position between the roll chock.
- the position of the roll chock is adjusted when the work rolls 1 and 2 in the upper right of FIG. 17C are stopped and when the work rolls 1 and 2 in the lower part of FIG. 17C are rotated. Also good.
- the roll-down load on the work side and the drive-side load are detected for the upper roll system and the lower roll system, respectively.
- the reference value 3 is calculated from the load difference with the rolling reduction load on the side, and the third control target value is set based on the reference value 3.
- the work rolls 1 and 2 are rotated to detect the work-side and drive-side roll-down loads for the upper roll system and the lower roll system, respectively, and the work-side roll-down load and the drive-side roll-down load are detected.
- the load difference is calculated.
- the upper roll system or the lower roll system, in FIG. 17C the lower roll system is set as the reference roll system so that the load difference becomes a value within the allowable range of the third control target value.
- the position of the roll chock is adjusted by controlling the roll chock of each roll simultaneously and in the same direction while maintaining the relative position between the roll chock.
- the first adjustment, the second adjustment, and the third adjustment can be determined independently from each other.
- the first adjustment is performed by normal rotation and reverse rotation of the work rolls 1 and 2
- the second adjustment is performed. May be performed by stopping and rotating the work rolls 1 and 2.
- the present invention can be applied not only to a 4-high rolling mill but also to a 6-high rolling mill.
- the present invention can be similarly applied to other than the four-high mill and the six-high mill, and can be applied to, for example, an eight-high mill or a five-high mill.
- the reference value 1, the first control target value, the reference value 2, the second control target value, the reference value 3, and the third control target value in the 5-high rolling mill and the 6-high rolling mill are expressed by the equation (1).
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Abstract
Description
本発明の実施形態に係る圧延機と当該圧延機の圧延機の設定方法では、ロール間に発生するスラスト力をなくし、蛇行及びキャンバーのない、あるいは蛇行及びキャンバーが極めて軽微な製品を安定して製造することを目的とする。図1に、被圧延材Sの圧延時において圧延機のロール間に発生するスラスト力及びスラスト反力を説明するための、圧延機の概略側面図及び概略正面図を示す。以下では、図1に示すように、ロール胴長方向の作業側をWS(Work Side)、駆動側をDS(Drive Side)と表す。
図2~図4Bに基づいて、本発明の第1の実施形態に係る圧延機及び当該圧延機を制御するための装置の構成と、圧延機の設定方法について説明する。第1の実施形態は、圧下位置零点調整前または圧延開始前に、基準とする補強ロールと他のロールとのロール間クロス角をゼロにするように調整し、スラスト力の発生しない圧延を実現するものである。本実施形態に係る圧延機は、圧延機にスラスト反力を測定するスラスト反力測定装置が設けられておらず、ロールにかかるスラスト反力を測定できない場合にもロール間クロスの調整が可能である。
まず、図2に基づいて、本実施形態に係る圧延機と、当該圧延機を制御するための装置とを説明する。図2は、本実施形態に係る圧延機と、当該圧延機を制御するための装置との構成を示す説明図である。なお、図2に示す圧延機は、ロール胴長方向の作業側から見た状態を示しており、圧延方向は紙面左から右に向かっているとする。また、図2では、下補強ロールを基準ロールとした場合の構成を示す。なお、本実施形態に係る発明では、圧下方向に配列された各ロールのうちいずれか1つのロールを基準ロールとして設定すればよい。基準ロールは、チョックとハウジングとの接触面積が大きく、位置が安定する最下部または最上部に位置するロールが好ましい。
以下、図3A~図6に基づいて、本実施形態に係る圧延機の設定方法について、説明する。図3A及び図3Bは、本実施形態に係るロール正転時とロール逆転時との圧下方向荷重に基づきロールチョック位置調整を行う圧延機の設定方法を説明するフローチャートである。図4Aは、本実施形態に係る圧延機の設定方法におけるロールチョック位置調整の手順を示す説明図であって、ロールギャップ開状態での位置調整を示す。図4Bは、本実施形態に係る圧延機の設定方法におけるロールチョック位置調整の手順を示す説明図であって、キスロール状態での位置調整を示す。なお、図4A、Bにおいては、ロール間に作用する荷重分布の記載を省略している。図5は、ロール間クロス角同定時の圧延機の状態の駆動状態の一例を示す概略側面図及び概略正面図である。なお、図5において、ロールの正逆転時に、下作業ロール2と下補強ロール4との間のスラスト力の方向の変化に伴い荷重分布も変化するが僅かな変化であるため、ここではその違いを明記していない。図6は、図5の状態の圧延機において、下側のロールを正転させた場合と逆転させた場合とで取得された圧下方向荷重の差を示す説明図である。本例では、下補強ロール4を基準ロールとして説明するが、基準ロールは圧下方向において最上部又は最下部にあるロールのいずれか一方とすればよく、上補強ロール3が基準ロールとなる場合もある。
ロールギャップ開状態での位置調整を行う第1調整では、上作業ロールと下作業ロールとを開状態にしてインクリースベンディング力を加え、作業ロール-補強ロール間に荷重を与え、その状態で当該ロール間のスラスト力によって発生する圧下方向荷重の差が所定の目標値になるように上下の作業ロールチョック位置を制御する。まず、図3Aに示すように、ロール間クロス制御装置23は、圧下装置27に対して、上作業ロール1と下作業ロール2とのロールギャップが所定の間隙を有する開状態となるように、圧下方向におけるロール位置を調整させる(S100)。圧下装置27は、当該指示に基づきロールに対して所定の負荷を与え、作業ロール1、2のロールギャップを開状態とする。
ここで、基準値1及び第1の制御目標値の算出について、図4Aに基づき詳細に説明する。まず、図4A上側に示すように、ロールギャップ開状態において、上作業ロール1と上補強ロール3とからなる上ロール系と、下作業ロール2と下補強ロール4とからなる下ロール系とで、それぞれロールを正転させる。このとき、上作業ロール1と下作業ロール2とは離隔されているので、各ロール系は独立した状態である。このロール正転状態において、上ロール系の作業側の圧下方向荷重と駆動側の圧下方向荷重、及び、下ロール系の作業側の圧下方向荷重と駆動側の圧下方向荷重が測定される。そして、これらの測定値より、上ロール系及び下ロール系それぞれについて、作業側の圧下方向荷重と駆動側の圧下方向荷重との差である圧下方向荷重差が算出される(図4AのP11、P12)。各ロール系の圧下方向荷重差は、下記式(1)より演算される。
フローチャートの説明に戻り、図3Aに示したロールギャップが開状態における位置調整を終了すると、次に、ロール間クロス制御装置23は、図3Bに示すように、圧下装置27に対して、上作業ロール1と下作業ロール2とのロールギャップが所定のキスロール状態となるように、圧下方向におけるロール位置を調整させる(S118)。圧下装置27は、当該指示に基づきロールに対して所定の負荷を与え、作業ロール1、2を接触させ、キスロール状態とする。
ここで、基準値2及び第2の制御目標値の算出について、図4Bに基づき詳細に説明する。第2調整においては、上下作業ロールを接触させたキスロール状態で締め込み荷重を加え、その状態での上下作業ロール間のスラスト力によって発生する圧下方向荷重差が所定の目標値となるように、基準ロールと反対側の作業ロールおよび補強ロールチョック位置を制御する。
以上、本発明の第1の実施形態に係る圧延機と当該圧延機の設定方法について説明した。本実施形態によれば、ロール正転時とロール逆転時とでは圧下方向荷重差の大きさは略同一であるがその向きが反対となることを利用して、圧下方向荷重差からロール間クロス角をゼロとするための制御目標値を演算して設定し、圧下位置零点調整前または圧延開始前に上記第1調整及び第2調整を行う。これにより、ロール間クロス角をなくした状態で被圧延材の圧延が行われるため、被圧延材の蛇行及びキャンバーの発生を抑制することができる。
次に、図7A~図8Bに基づいて、本発明の第2の実施形態に係る圧延機の設定方法について説明する。本実施形態は、第1の実施形態と同様、圧下位置零点調整前または圧延開始前に、基準とする補強ロールと他のロールとのロール間クロス角をゼロにするように調整し、スラスト力の発生しない圧延を実現するものである。本実施形態に係る圧延機も、第1の実施形態と同様、スラスト反力を測定できない場合にもロール間クロスの調整が可能である。なお、本実施形態に係る圧延機及び当該圧延機を制御するための装置は、図2に示した第1の実施形態に係る圧延機及びその制御装置と同様に構成することができる。このため、本実施形態ではこれらについての詳細な説明は省略する。
図7A及び図7Bは、本実施形態に係る圧延機の設定方法を説明するフローチャートであって、ロール停止時とロール回転時との圧下方向荷重に基づき位置調整を行う場合の例を示す。図8Aは、本実施形態に係る圧延機の設定方法におけるロールチョック位置調整の手順を示す説明図であって、ロールギャップ開状態での位置調整を示す。図8Bは、本実施形態に係る圧延機の設定方法におけるロールチョック位置調整の手順を示す説明図であって、キスロール状態での位置調整を示す。なお、図7A、Bにおいては、ロール間に作用する荷重分布の記載を省略している。また、本例では、下補強ロール4を基準ロールとして説明するが、基準ロールは圧下方向において最上部又は最下部にあるロールのいずれか一方とすればよく、上補強ロール3が基準ロールとなる場合もある。
ロールギャップ開状態での位置調整を行う第1調整では、上作業ロールと下作業ロールとを開状態にしてインクリースベンディング力を加え、作業ロール-補強ロール間に荷重を与え、その状態で当該ロール間のスラスト力によって発生する圧下方向荷重の差が所定の目標値になるように上下の作業ロールチョック位置を制御する。まず、図7Aに示すように、ロール間クロス制御装置23は、圧下装置27に対して、上作業ロール1と下作業ロール2とのロールギャップが所定の間隙を有する開状態となるように、圧下方向におけるロール位置を調整させる(S200)。圧下装置27は、当該指示に基づきロールに対して所定の負荷を与え、作業ロール1、2のロールギャップを開状態とする。
ここで、基準値1及び第1の制御目標値の算出について、図8Aに基づき詳細に説明する。まず、図8A上側に示すように、ロールギャップ開状態において、上作業ロール1と上補強ロール3とからなる上ロール系と、下作業ロール2と下補強ロール4とからなる下ロール系とで、それぞれロールの回転を停止させる。このとき、上作業ロール1と下作業ロール2とは離隔されているので、各ロール系は独立した状態である。このロール停止状態において、上ロール系の作業側の圧下方向荷重と駆動側の圧下方向荷重、及び、下ロール系の作業側の圧下方向荷重と駆動側の圧下方向荷重が測定される。そして、これらの測定値より、上ロール系及び下ロール系それぞれについて、作業側の圧下方向荷重と駆動側の圧下方向荷重との差である圧下方向荷重差が算出される(P31、P32)。各ロール系の圧下方向荷重差は、下記式(5)より演算される。
フローチャートの説明に戻り、図7Aに示したロールギャップが開状態における位置調整を終了すると、次に、ロール間クロス制御装置23は、図7Bに示すように、圧下装置27に対して、上作業ロール1と下作業ロール2とのロールギャップが所定のキスロール状態となるように、圧下方向におけるロール位置を調整させる(S216)。圧下装置27は、当該指示に基づきロールに対して所定の負荷を与え、作業ロール1、2を接触させ、キスロール状態とする。
ここで、基準値2及び第2の制御目標値の算出について、図8Bに基づき詳細に説明する。第2調整においては、上下作業ロールを接触させたキスロール状態で締め込み荷重を加え、その状態での上下作業ロール間のスラスト力によって発生する圧下方向荷重差が所定の目標値となるように、基準ロールと反対側の作業ロールおよび補強ロールチョック位置を制御する。
以上、本発明の第2の実施形態に係る圧延機の設定方法について説明した。本実施形態によれば、ロール停止時には発生しないがロール回転時に現れる圧下方向荷重差に基づいて、圧下方向荷重差からロール間クロス角をゼロとするための制御目標値を演算して設定し、圧下位置零点調整前または圧延開始前に上記第1調整及び第2調整を行う。これにより、ロール間クロス角をなくした状態で被圧延材の圧延が行われるため、被圧延材の蛇行及びキャンバーの発生を抑制することができる。
上述の第1及び第2の実施形態に係る圧延機の設定方法では、ロール間クロスをなくすために、ロール間に発生するスラスト反力がゼロまたは許容範囲内の値となるように、ロールチョックの位置制御を行っている。これは、スラスト反力とロール間クロス角との間に、以下に示すような相関があるという知見に基づいている。以下、図11~図15に基づいて、ロール間クロス角と圧下方向荷重差との関係について説明する。
まず、図11~図13に基づいて、作業ロールのロールギャップが開状態である場合での、ロール間クロスと圧下方向荷重差との関係について説明する。図11は、ロールギャップが開状態である圧延機の、作業ロール1、2及び補強ロール3、4の配置を示す説明図である。図12は、ロール間クロス角の定義を示す説明図である。図13は、作業ロール径80mmの小型圧延機において行った実験結果であり、ロールギャップ開状態での、補強ロールクロス角と圧下方向荷重差との一関係を示すグラフである。なお、図13では、上下の補強ロールの圧下方向荷重差は、補強ロールクロス角を増加方向に設定した場合と減少方向に設定した場合とについてそれぞれ測定し、増加方向での測定値と減少方向での測定値とを平均化した値を表示している。
次に、図14及び図15に基づいて、作業ロールがキスロール状態である場合での、ロールペアクロス角と圧下方向荷重差との関係について説明する。図14は、キスロール状態にされた圧延機の、作業ロール1、2及び補強ロール3、4の配置を示す説明図である。図15は、キスロール状態での、作業ロールと補強ロールとのペアクロス角と圧下方向荷重差との一関係を示すグラフである。なお、図15では、上下の補強ロールの圧下方向荷重差は、作業ロールと補強ロールとのペアクロス角を増加方向に設定した場合と減少方向に設定した場合とについてそれぞれ測定し、増加方向での測定値と減少方向での測定値とを平均化した値を表示している。
2 下作業ロール
3 上補強ロール
4 下補強ロール
5a 上作業ロールチョック(作業側)
5b 上作業ロールチョック(駆動側)
6a 下作業ロールチョック(作業側)
6b 下作業ロールチョック(駆動側)
7a 上補強ロールチョック(作業側)
7b 上補強ロールチョック(駆動側)
8a 下補強ロールチョック(作業側)
8b 下補強ロールチョック(駆動側)
9 上作業ロールチョック押圧装置
10 下作業ロールチョック押圧装置
11 上作業ロールチョック位置検出機能付駆動装置
12 下作業ロールチョック位置検出機能付駆動装置
13 上補強ロールチョック押圧装置
14 上補強ロールチョック位置検出機能付駆動装置
15 ロールチョック圧延方向力制御装置
16 ロールチョック位置制御装置
21 駆動用電動機
22 駆動用電動機制御装置
23 ロール間クロス制御装置
24a 入側上インクリースベンディング装置
24b 出側上インクリースベンディング装置
25a 入側下インクリースベンディング装置
25b 出側下インクリースベンディング装置
26 インクリースベンディング制御装置
27 圧下装置
28a 上圧下方向荷重検出装置(作業側)
28b 上圧下方向荷重検出装置(駆動側)
29a 下圧下方向荷重検出装置(作業側)
29b 下圧下方向荷重検出装置(駆動側)
30 ハウジング
30a、30b 圧下支点位置
32 上圧下方向荷重差演算部[減算器]
33 下圧下方向荷重差演算部[減算器]
34 回転角検出機能付サーボモータ
40 下補強ロールチョック押圧装置
41 上中間ロール
42 下中間ロール
43 上中間ロールチョック
43a 上中間ロールチョック(作業側)
43b 上中間ロールチョック(駆動側)
44 下中間ロールチョック
44a 下中間ロールチョック(作業側)
44b 下中間ロールチョック(駆動側)
Claims (10)
- 少なくとも一対の作業ロールと前記作業ロールを支持する一対の補強ロールとを含む、複数のロールを備える4段以上の圧延機であって、
圧下方向に配列された各ロールのうちいずれか1つのロールを基準ロールとして、
前記補強ロールの作業側及び駆動側の圧下支点位置において、前記ロールの圧下方向に作用する圧下方向荷重を検出する荷重検出装置と、
少なくとも前記基準ロール以外の前記ロールのロールチョックに対し、被圧延材の圧延方向入側または出側のいずれか一方に設けられ、前記ロールチョックを前記圧延方向に押圧する押圧装置と、
少なくとも前記基準ロール以外の前記ロールのロールチョックに対し、前記圧延方向において前記押圧装置と対向するように設けられ、前記ロールチョックを前記圧延方向に移動させる駆動装置と、
前記基準ロールのロールチョックの圧延方向位置を基準位置として固定し、作業側の前記荷重検出装置により検出された圧下方向荷重と駆動側の前記荷重検出装置により検出された圧下方向荷重との差である圧下方向荷重差が許容範囲内の値となるように、前記駆動装置を駆動して、前記基準ロール以外の前記ロールの前記ロールチョックの前記圧延方向における位置を制御する位置制御装置と、
を備える、圧延機。 - 前記複数のロールのうち圧下方向において最下部または最上部に位置するロールを前記基準ロールとする、請求項1に記載の圧延機。
- 前記ロールに対してベンディング力を加えるベンディング装置を備え、
前記位置制御装置は、前記作業ロール間のロールギャップを開状態にし、前記位置調整対象の前記ロール側の前記ロールチョックに対して、前記ベンディング装置によりベンディング力を加える、請求項1または2に記載の圧延機。 - 前記駆動装置は、ロールチョック位置検出装置を備えた油圧シリンダである、請求項1~3のいずれか1項に記載の圧延機。
- 圧延機の設定方法であって、
前記圧延機は、少なくとも一対の作業ロールと前記作業ロールを支持する一対の補強ロールとを含む複数のロールと、前記補強ロールの作業側及び駆動側の圧下支点位置において前記ロールの圧下方向に作用する圧下方向荷重を検出する荷重検出装置と、を備える4段以上の圧延機であり、
圧下位置零点調整前または圧延開始前に実施され、
圧下方向に配列された各ロールのうちいずれか1つのロールを基準ロールとして、
作業側の前記荷重検出装置により検出された圧下方向荷重と駆動側の前記荷重検出装置により検出された圧下方向荷重との差である圧下方向荷重差を算出し、
前記圧下方向荷重差が許容範囲内の値となるように、前記基準ロールのロールチョックの圧延方向位置を基準位置として固定し、かつ、前記基準ロール以外の前記ロールのロールチョックを被圧延材の圧延方向に移動させることにより、前記ロールチョックの位置を調整する、
圧延機の設定方法。 - 前記複数のロールのうち圧下方向において最下部または最上部に位置するロールを前記基準ロールとする、請求項5に記載の圧延機の設定方法。
- 4段の前記圧延機において、
前記被圧延材に対して圧下方向上側に設けられた複数のロールを上ロール系、前記被圧延材に対して圧下方向下側に設けられた複数のロールを下ロール系として、
前記作業ロールのロールギャップを開状態とし、前記作業ロールの前記ロールチョックに対してベンディング装置によりベンディング力を加えた状態で、前記上ロール系及び前記下ロール系それぞれについて、前記作業ロールの前記ロールチョックと前記補強ロールの前記ロールチョックとの位置を調整する第1のステップと、
前記第1のステップを終えた後、前記作業ロールをキスロール状態にして、前記上ロール系及び前記下ロール系の前記ロールチョックの位置を調整する第2のステップと、
を実施し、
前記第1のステップでは、
所定の回転方向に前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差に基づき第1の基準値を演算する第1の基準値演算ステップと、
前記ロールの回転方向を逆転させて、前記上ロール系及び前記下ロール系それぞれについて、それぞれ作業側及び駆動側の圧下方向荷重を検出して、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差と前記第1の基準値との偏差に基づき第1の制御目標値を演算する第1の制御目標値演算ステップと、
前記圧下方向荷重差が前記第1の制御目標値の許容範囲内の値となるように、前記基準ロール側のロール系の前記作業ロールの前記ロールチョック、または、前記基準ロールと反対側のロール系の前記作業ロールあるいは前記補強ロールの前記ロールチョックを前記圧延方向に移動させて、前記ロールチョックの位置を調整する第1の調整ステップと、
を実施し、
前記第2のステップでは、前記作業ロールをキスロール状態にして、
所定の回転方向に前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差に基づき第2の基準値を演算する第2の基準値演算ステップと、
前記ロールの回転方向を逆転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差と前記第2の基準値との偏差に基づき第2の制御目標値を演算する第2の制御目標値演算ステップと、
前記圧下方向荷重差が前記第2の制御目標値の許容範囲内の値となるように、前記上ロール系または前記下ロール系のうち一方を基準ロール系として、他方のロール系の各ロールの前記ロールチョックを、ロールチョック間の相対位置を保持しながら同時かつ同方向に制御して、前記ロールチョックの位置を調整する第2の調整ステップと、
を実施する、請求項6に記載の圧延機の設定方法。 - 前記作業ロールと前記補強ロールとの間に中間ロールをそれぞれ備える6段の前記圧延機において、
前記被圧延材に対して圧下方向上側に設けられた複数のロールを上ロール系、前記被圧延材に対して圧下方向下側に設けられた複数のロールを下ロール系として、
前記作業ロールのロールギャップを開状態とし、前記中間ロールの前記ロールチョックに対してベンディング装置によりベンディング力を加えた状態で、前記上ロール系及び前記下ロール系それぞれについて、前記中間ロールの前記ロールチョックと前記補強ロールの前記ロールチョックとの位置を調整する第1のステップと、
前記第1のステップを終えた後、前記作業ロールのロールギャップを開状態に維持して、前記作業ロールの前記ロールチョックに対してベンディング装置によりベンディング力を加えた状態で、前記上ロール系及び前記下ロール系それぞれについて、前記中間ロールの前記ロールチョックと前記作業ロールの前記ロールチョックとの位置を調整する第2のステップと、
前記第2のステップを終えた後、前記作業ロールをキスロール状態にして、前記上ロール系及び前記下ロール系の前記ロールチョックの位置を調整する第3のステップと、
を実施し、
前記第1のステップでは、
所定の回転方向に前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差に基づき第1の基準値を演算する第1の基準値演算ステップと、
前記ロールの回転方向を逆転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差と前記第1の基準値との偏差に基づき第1の制御目標値を演算する第1の制御目標値演算ステップと、
前記圧下方向荷重差が前記第1の制御目標値の許容範囲内の値となるように、前記基準ロール側のロール系の前記中間ロールの前記ロールチョック、及び、前記基準ロールと反対側のロール系の前記中間ロールの前記ロールチョックまたは前記補強ロールの前記ロールチョックのいずれかを前記圧延方向に移動させて、前記ロールチョックの位置を調整する第1の調整ステップと、
を実施し、
前記第2のステップでは、
所定の回転方向に前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差に基づき第2の基準値を演算する第2の基準値演算ステップと、
前記ロールの回転方向を逆転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差と前記第2の基準値との偏差に基づき第2の制御目標値を演算する第2の制御目標値演算ステップと、
前記圧下方向荷重差が前記第2の制御目標値の許容範囲内の値となるように、前記基準ロール側のロール系の前記作業ロールの前記ロールチョック、及び、前記基準ロールと反対側のロール系の前記作業ロールの前記ロールチョックまたは前記中間ロール及び前記補強ロールの前記ロールチョックのいずれかを前記圧延方向に移動させて、前記ロールチョックの位置を調整する第2の調整ステップと、
を実施し、
前記第3のステップでは、前記作業ロールをキスロール状態にして、
所定の回転方向に前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差に基づき第3の基準値を演算する第3の基準値演算ステップと、
前記ロールの回転方向を逆転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差と前記第3の基準値との偏差に基づき第3の制御目標値を演算する第3の制御目標値演算ステップと、
前記圧下方向荷重差が前記第3の制御目標値の許容範囲内の値となるように、前記上ロール系または前記下ロール系のうち一方を基準ロール系として、他方のロール系の各ロールの前記ロールチョックを、ロールチョック間の相対位置を保持しながら同時かつ同方向に制御して、前記ロールチョックの位置を調整する第3の調整ステップと、
を実施する、請求項6に記載の圧延機の設定方法。 - 4段の前記圧延機において、
前記被圧延材に対して圧下方向上側に設けられた複数のロールを上ロール系、前記被圧延材に対して圧下方向下側に設けられた複数のロールを下ロール系として、
前記作業ロールのロールギャップを開状態とし、前記作業ロールの前記ロールチョックに対してベンディング装置によりベンディング力を加えた状態で、前記上ロール系及び前記下ロール系それぞれについて、前記作業ロールの前記ロールチョックと前記補強ロールの前記ロールチョックとの位置を調整する第1のステップと、
前記第1のステップを終えた後、前記作業ロールをキスロール状態にして、前記上ロール系及び前記下ロール系の前記ロールチョックの位置を調整する第2のステップと、
を実施し、
前記第1のステップでは、
前記ロールの回転が停止された状態で、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差に基づき第1の基準値を演算し、前記第1の基準値に基づき第1の制御目標値を設定する第1の制御目標値演算ステップと、
前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差を演算する第1の荷重差演算ステップと、
前記圧下方向荷重差が前記第1の制御目標値の許容範囲内の値となるように、前記基準ロール側のロール系の前記作業ロールの前記ロールチョック、または、前記基準ロールと反対側のロール系の前記作業ロールあるいは前記補強ロールの前記ロールチョックを前記圧延方向に移動させて、前記ロールチョックの位置を調整する第1の調整ステップと、
を実施し、
前記第2のステップでは、前記作業ロールをキスロール状態にして、
前記ロールの回転が停止された状態で、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差から第2の基準値を演算し、前記第2の基準値に基づき第2の制御目標値を設定する第2の制御目標値演算ステップと、
前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差を演算する第2の荷重差演算ステップと、
前記圧下方向荷重差が前記第2の制御目標値の許容範囲内の値となるように、前記上ロール系または前記下ロール系のうち一方を基準ロール系として、他方のロール系の各ロールの前記ロールチョックを、ロールチョック間の相対位置を保持しながら同時かつ同方向に制御して、前記ロールチョックの位置を調整する第2の調整ステップと、
を実施する、請求項6に記載の圧延機の設定方法。 - 前記作業ロールと前記補強ロールとの間に中間ロールをそれぞれ備える6段の前記圧延機において、
前記被圧延材に対して圧下方向上側に設けられた複数のロールを上ロール系、前記被圧延材に対して圧下方向下側に設けられた複数のロールを下ロール系として、
前記作業ロールのロールギャップを開状態とし、前記中間ロールの前記ロールチョックに対してベンディング装置によりベンディング力を加えた状態で、前記上ロール系及び前記下ロール系それぞれについて、前記中間ロールの前記ロールチョックと前記補強ロールの前記ロールチョックとの位置を調整する第1のステップと、
前記第1のステップを終えた後、前記作業ロールのロールギャップを開状態に維持して、前記作業ロールの前記ロールチョックに対してベンディング装置によりベンディング力を加えた状態で、前記上ロール系及び前記下ロール系それぞれについて、前記中間ロールの前記ロールチョックと前記作業ロールの前記ロールチョックとの位置を調整する第2のステップと、
前記第2のステップを終えた後、前記作業ロールをキスロール状態にして、前記上ロール系及び前記下ロール系の前記ロールチョックの位置を調整する第3のステップと、
を実施し、
前記第1のステップでは、
前記ロールの回転が停止された状態で、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差から第1の基準値を演算し、前記第1の基準値に基づき第1の制御目標値を設定する第1の制御目標値演算ステップと、
前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差を演算する第1の荷重差演算ステップと、
前記圧下方向荷重差が前記第1の制御目標値の許容範囲内の値となるように、前記基準ロール側のロール系の前記中間ロールの前記ロールチョック、及び、前記基準ロールと反対側のロール系の前記中間ロールの前記ロールチョックまたは前記補強ロールのいずれかを前記圧延方向に移動させて、前記ロールチョックの位置を調整する第1の調整ステップと、
を実施し、
前記第2のステップでは、
前記ロールの回転が停止された状態で、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差から第2の基準値を演算し、前記第2の基準値に基づき第2の制御目標値を設定する第2の制御目標値演算ステップと、
前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差を演算する第2の荷重差演算ステップと、
前記圧下方向荷重差が前記第2の制御目標値の許容範囲内の値となるように、前記基準ロール側のロール系の前記作業ロールの前記ロールチョック、及び、前記基準ロールと反対側のロール系の前記作業ロールの前記ロールチョックまたは前記中間ロール及び前記補強ロールの前記ロールチョックのいずれかを前記圧延方向に移動させて、前記ロールチョックの位置を調整する第2の調整ステップと、
を実施し、
前記第3のステップでは、前記作業ロールをキスロール状態にして、
前記ロールの回転が停止された状態で、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差から第3の基準値を演算し、前記第3の基準値に基づき第3の制御目標値を設定する第3の制御目標値演算ステップと、
前記ロールを回転させて、前記上ロール系及び前記下ロール系それぞれについて、作業側及び駆動側の圧下方向荷重を検出し、前記作業側の圧下方向荷重と前記駆動側の圧下方向荷重との差である圧下方向荷重差を演算する第3の荷重差演算ステップと、
前記圧下方向荷重差が前記第3の制御目標値の許容範囲内の値となるように、前記上ロール系または前記下ロール系のうち一方を基準ロール系として、他方のロール系の各ロールの前記ロールチョックを、ロールチョック間の相対位置を保持しながら同時かつ同方向に制御して、前記ロールチョックの位置を調整する第3の調整ステップと、
を実施する、請求項6に記載の圧延機の設定方法。
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- 2019-05-17 EP EP19804505.6A patent/EP3797889B1/en active Active
- 2019-05-17 CN CN201980048080.9A patent/CN112437701B/zh active Active
- 2019-05-17 KR KR1020207036122A patent/KR102390362B1/ko active IP Right Grant
- 2019-05-17 US US17/056,302 patent/US11612921B2/en active Active
- 2019-05-17 WO PCT/JP2019/019809 patent/WO2019221297A1/ja unknown
- 2019-05-17 BR BR112020021879-0A patent/BR112020021879A2/pt unknown
- 2019-05-17 JP JP2020519959A patent/JP7040611B2/ja active Active
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Also Published As
Publication number | Publication date |
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EP3797889A1 (en) | 2021-03-31 |
EP3797889A4 (en) | 2022-03-16 |
US20210078059A1 (en) | 2021-03-18 |
EP3797889B1 (en) | 2024-06-19 |
KR102390362B1 (ko) | 2022-04-25 |
JP7040611B2 (ja) | 2022-03-23 |
JPWO2019221297A1 (ja) | 2021-03-18 |
CN112437701A (zh) | 2021-03-02 |
CN112437701B (zh) | 2023-01-13 |
KR20210010540A (ko) | 2021-01-27 |
US11612921B2 (en) | 2023-03-28 |
BR112020021879A2 (pt) | 2021-01-26 |
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