WO2022152779A1 - Réduction des changements d'épaisseur dus à la tension lors du laminage - Google Patents

Réduction des changements d'épaisseur dus à la tension lors du laminage Download PDF

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Publication number
WO2022152779A1
WO2022152779A1 PCT/EP2022/050608 EP2022050608W WO2022152779A1 WO 2022152779 A1 WO2022152779 A1 WO 2022152779A1 EP 2022050608 W EP2022050608 W EP 2022050608W WO 2022152779 A1 WO2022152779 A1 WO 2022152779A1
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WO
WIPO (PCT)
Prior art keywords
soapy
rolling
tension
outlet
actual
Prior art date
Application number
PCT/EP2022/050608
Other languages
German (de)
English (en)
Inventor
Andreas Hollaus
Matthias Kurz
Original Assignee
Primetals Technologies Germany Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Primetals Technologies Germany Gmbh filed Critical Primetals Technologies Germany Gmbh
Priority to EP22700614.5A priority Critical patent/EP4277757A1/fr
Priority to MX2023008387A priority patent/MX2023008387A/es
Priority to US18/261,938 priority patent/US20240075509A1/en
Priority to CN202280010624.4A priority patent/CN116783009A/zh
Priority to JP2023543045A priority patent/JP2024503870A/ja
Publication of WO2022152779A1 publication Critical patent/WO2022152779A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/58—Roll-force control; Roll-gap control
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/16—Control of thickness, width, diameter or other transverse dimensions
    • B21B37/18—Automatic gauge control
    • 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
    • B21B38/06—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring tension or compression
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2265/00—Forming parameters
    • B21B2265/02—Tension

Definitions

  • the present invention is based on an operating method for a rolling stand for rolling flat metal stock.
  • the resulting base reference value is determined as the sum of an initial base reference value and an additional reference value.
  • the resulting position setpoint is identical to the resulting base setpoint.
  • the initial basic target value is generally independent of the soapy draft entering and the soapy draft leaving.
  • the present invention is also based on a control system for a rolling stand for rolling flat metal stock, the control system being designed by hardware blocks and/or software programming in such a way that such an operating method is implemented during operation - sated .
  • the present invention is also based on a rolling unit for rolling a flat rolling stock made of metal, wherein the rolling unit has a roll stand for rolling the flat rolled stock and such a control system.
  • one of the elementary requirements of the rolling process is to produce a flat stock whose thickness corresponds as closely as possible to a predetermined nominal thickness.
  • the thickness of the rolling stock leaving the roll stand is set in particular via the roll gap.
  • the size of the roll gap is adjusted to a specific position by appropriately adjusting the actuator.
  • the size of the roll gap and thus the thickness of the emerging rolling stock is not determined solely by the position of the actuator. Rather, in addition to wear, thermal crowning, roll displacement and possibly other influences, the deflection of the roll stand must also be taken into account. The deflection results from the rolling force and other forces acting on the roll stand, for example the bending force.
  • roll stands are operated with roll gap control.
  • a run-out soapy thickness is first determined in a pass plan, to which the rolling stock is to be rolled in the roll stand.
  • an associated expected rolling force is determined taking into account parameters of the rolling stock (for example its width, its thickness on the inlet side, its temperature and other variables).
  • the associated deflection of the rolling stand is determined using a spring model of the rolling stand.
  • a desired position value for the actuator is then determined, taking into account the deflection of the roll stand and other variables such as crowning caused by wear and/or temperature.
  • the actual rolling force is recorded directly or determined using recorded variables.
  • the correction value is determined by means of an AGC (automatic gauge control). The correction value is determined within the AGC using a spring model of the roll stand.
  • the rolling of flat metal stock is often done such that while the stock is being rolled in the mill stand, it is clamped in front of the mill stand in an upstream facility and/or behind the mill stand in a downstream facility.
  • the rolling stock can be subjected to an inlet soapy draw before the roll stand or an outlet soapy draw after the roll stand.
  • a respective loop lifter can be arranged in front of and/or behind the roll stand in order to keep the soapy draft on the inlet side or outlet more constant. If the rolling stand is part of a multi-stand rolling train, but is not the front rolling stand of the rolling train, the upstream device can also be another rolling stand of the multi-stand rolling train.
  • the downstream device can also be a further rolling stand of the multi-stand rolling train.
  • the upstream and/or downstream device can also be a reel, for example in a Steckel mill. Other refinements are also possible.
  • the compensation by the AGC is often only taken into account to a limited extent, since otherwise there is a risk that the simultaneous correction of the adjustment by the AGC and the tracking of the trains by train control will lead to oscillations and instabilities.
  • the correction value determined by the AGC is often incorrect, for example due to friction effects in the roll stand or due to dead bands.
  • the change in the thickness to which the rolling stock is rolled in the rolling stand caused by the changed deflection of the rolling stand is not or only insufficiently corrected during the tapping phase.
  • an additional adjustment target value is determined by means of a tension controller, which regulates the actual tension on the input side to a target tension on the input side, which is switched to the actual adjustment target value.
  • the actual adjustment target value is a roll gap target value.
  • An operating method of the type mentioned at the outset is also known from JP 2003-164 906 A.
  • an additional adjustment target value is determined by means of a tension controller, which regulates the actual tension on the output side to a target tension on the output side, which is switched to the actual adjustment target value.
  • the actual adjustment target value is a roll gap target value.
  • EP 2 620 233 A1 also discloses an operating method for a roll stand for rolling flat metal stock. With this operating method, a mass flow control is implemented, which in turn acts on the adjustment system of the roll stand. This adjusts the thickness of the rolling stock leaving the roll stand. In this operating method, a tension controller, which regulates the actual tension on the input side to a desired tension on the input side, acts on the adjustment system of the roll stand. Summary of the Invention
  • the object of the present invention is to create possibilities by means of which better compliance with the thickness of the rolling stock can be guaranteed on the outlet side of the roll stand.
  • an operating method of the type mentioned at the outset is designed in that
  • soapy reference draw on the inlet is a size different from the target draw on the inlet side and/or the reference draw on the outlet side is a size different from a target soapy draw on the outlet.
  • the soapy actual draw inflow and/or the actual soapy draw outflow can be measured actual values or values determined on the basis of measured values. It is possible to use the actual values or the setpoints as an alternative, because the tension controls generally have a sufficiently high level of dynamics and quality and the actual values and the setpoints therefore correspond to a sufficient extent.
  • the roll stand is operated with roll gap control.
  • the incoming soapy tension control usually acts on a peripheral roll speed with which the flat Rolling stock is rolled in the rolling stand, and/or to a feed speed at which the flat rolling stock runs out of a device upstream of the rolling stand.
  • the soapy tension control at the outlet acts as a rule on the circumferential roll speed and/or on a discharge speed at which the flat rolling stock enters a device downstream of the roll stand.
  • the tension controls only act on one device at a time, i.e. either the upstream device or the rolling stand or either the rolling stand or the downstream device.
  • the additional target value is dependent on the intake-side draft state (target or actual)
  • the additional target value is preferably determined by the determination element using the product of an incoming soapy sensitivity and the difference between the incoming soapy actual draft or the corresponding target draft and the incoming soapy reference draft .
  • the additional target value is determined by the determination element preferably based on the product of the outlet soapy sensitivity with the difference between the outlet soapy actual draft or the corresponding setpoint draft and the outlet soapy reference draft, provided that there is a dependency of the additional setpoint value on the outlet soapy draft state. This makes it particularly easy to determine the additional setpoint and thus the resulting base setpoint.
  • the additional target value is preferably determined by the determination element based on the product of a soapy sensitivity and the difference between the actual soapy intake tension or the corresponding target tension and the soapy reference intake intake and/or using the product of the soapy sensitivity by the The difference between the soapy actual draw or the corresponding setpoint draw and the soapy reference draw that is discharged is determined. In this way, the additional setpoint can be determined in a particularly simple and reliable manner.
  • the sensitivity on the inlet side and/or the sensitivity on the outlet side are preferably specified for the determination element by a higher-level control device.
  • the corresponding sensitivities can be stored within the superordinate control device in the form of tables or the like.
  • the corresponding sensitivities depending on the geometry and other properties of the rolled stock e.g. its chemical composition and temperature
  • it is preferred if the sensitivity on the inlet side and/or the sensitivity on the outlet side are determined by the higher-level control device as part of a pass schedule calculation using an evaluation of a rolling model.
  • the rolling model is based on mathematical and physical equations that describe the rolling process in the rolling stand. This enables a "precise" determination of the incoming soapy sensitivity and/or the outgoing soapy sensitivity. If necessary, the roller model can be adapted again and again.
  • the mathematical-physical equations of the rolling model are usually differential equations and/or algebraic equations. Such models are well known to those skilled in the art. Purely by way of example, reference may be made to the technical paper "On the theory of rolling" by J.M. Alexander, published in the Proceedings of the Royal Society London, A. 326, pages 553 to 563, 1972.
  • the reference train on the inlet side and/or the reference train on the outlet side can also be specified for the determination element by a higher-level control device.
  • the corresponding reference trains can be determined or set by the higher-level control device as part of a pass schedule calculation.
  • the operating method is preferably designed in such a way that the higher-level control device - for example as part of the pass schedule calculation -
  • the initial base target value and the soapy target draw at the inlet and/or the soapy target draw at the outlet are determined
  • the resulting desired position value is preferably determined at least during the rolling of a center piece of the rolling stock using a correction value determined using an actual rolling force. So an AGC is implemented. It is therefore possible to combine the operating method according to the invention with the AGC.
  • the resulting basic setpoint value is preferably taken into account when determining the correction value. As a result, the dynamics when determining the correction value can be improved.
  • the resulting desired position value is preferably determined at least during the rolling of a rolling stock head and/or a rolling stock foot without utilizing an actual rolling force.
  • tension changes and the resulting changes in rolling force are compensated even when the AGC is not active.
  • the latter procedure can in particular also be combined with the procedure that the AGC is active during the rolling of a center piece of the rolling stock.
  • the AGC can alternatively be switched on during the transition from rolling the rolled stock head to rolling the center piece.
  • the AGC can be switched off (freezing or limiting changes) during the transition from rolling the center piece to rolling the foot of the rolled stock.
  • the resultant desired position value is preferably determined using the deviation of a thickness of the rolling stock from a desired thickness, which is detected on the exit side of the roll stand. This allows any residual errors to be corrected.
  • control system having the features of claim 13.
  • the control system implements an operating method according to the invention through the hardware blocks and/or software programming during operation.
  • the control system is designed as a control system according to the invention.
  • FIG. 3 shows the roller arrangement from FIG. 2 in a second operating state
  • 4 shows the roller arrangement from FIG. 2 in a third operating state
  • FIG. 8 shows a modification of the addition to FIG. 7,
  • FIG. 10 shows an embodiment of the control unit of FIG. 5.
  • a rolling stock 2 is to be rolled in a roll stand 1 .
  • FIG. 1 shows only the work rolls of the roll stand 1 .
  • the roll stand 1 has at least back-up rolls (four-high stand) in addition to the work rolls, optionally also intermediate rolls in addition to the back-up rolls, which are arranged between the work rolls and the back-up rolls (six-high stand).
  • the rolling stock 2 consists of metal, often steel, in some cases aluminum, in rare cases another metal such as copper.
  • the rolling stock 2 is also a flat rolling stock, i.e. a strip (normal case) or a heavy plate (exception).
  • the roll stand 1 is generally operated with roll gap control. Furthermore, the rolling stock 2 is rolled in the roll stand 1 with a circumferential roll speed vU. The associated drives and their controls are not shown.
  • the rolling stock 2 can be held in a device 3 arranged upstream of the rolling stand 1 while it is being rolled in the rolling stand 1 .
  • the rolling stock 2 runs out of the upstream device 3 at a feed speed vZ.
  • the rolling stock 2 is acted upon on the inlet side of the roll stand 1 by an inlet soapy actual tension ZE.
  • a be arranged looper Between the upstream device 3 and the roll stand 1, a be arranged looper.
  • the looper is not shown.
  • the upstream device 3 can be designed in particular as a further roll stand. However, it can also be designed differently, for example as a reel or as a set of driving rollers.
  • the feed speed vZ is shown in FIGS. 2 and 3 as a peripheral speed. If the upstream device 3 is a roll stand, the lead must also be taken into account.
  • the incoming soapy actual tension ZE is generally regulated to a corresponding target tension ZE* by means of an appropriate tension control.
  • the incoming soapy actual draw ZE and the incoming soapy desired draw ZE* are supplied to a front draw controller 24 .
  • the front tension controller 24 determines a front manipulated variable 5vE, which is applied to an actuator, using the actual soapy tension ZE on the inlet and the nominal tension ZE* on the inlet side—usually using the difference between the two mentioned tensions ZE, ZE* that the incoming soapy actual tension ZE is adjusted or at least approximated to the incoming soapy target tension ZE*.
  • the front manipulated variable 5vE can in particular be an additional speed setpoint which acts on the circumferential roller speed vU or—with the opposite sign—acts on the feed speed vZ.
  • the rolling stock 2 can be held in a device 4 downstream of the rolling stand 1 while it is being rolled in the rolling stand 1, as shown in FIGS.
  • the rolling stock 2 enters the downstream device 4 at a discharge speed vA.
  • the rolling stock 2 is acted upon on the outlet side of the roll stand 1 by an outlet soapy actual tension ZA.
  • a looper can also be arranged between the roll stand 1 and the downstream device 4 . This looper is also not shown.
  • the downstream device 4 can, in accordance with the illustration in FIGS. be trained. However, it can also be designed differently, for example as a reel or as a set of driving rollers.
  • the discharge speed vA is shown in FIGS. 3 and 4 as a circumferential speed. If the downstream device 4 is a roll stand, the lag must also be taken into account.
  • the outlet soapy actual tension ZA is generally regulated to a corresponding target tension ZA* by means of an appropriate tension control.
  • the soapy actual tension ZA that is exiting and the soapy setpoint tension ZA* that is exiting are fed to a rear tension controller 25 .
  • the rear tension controller 25 determines a rear manipulated variable övA, which is applied to an actuator, using the outlet soapy actual tension ZA and the outlet-side desired tension ZA*—usually using the difference between the two mentioned tensions ZA, ZA* that the outlet actual soapy draft ZA is adjusted or at least approximated to the outlet soapy setpoint draft ZA*.
  • the rear manipulated variable övA can in particular be an additional speed setpoint which acts on the roll peripheral speed vU or—with the opposite sign—acts on the discharge speed vA.
  • the roll stand 1 generally has a large number of actuators, by means of which the rolling process is influenced.
  • actuators are a bending system, by means of which a roll bend is set, a sliding device, by means of which a pair of rolls can be axially displaced in opposite directions, roll cooling, roll gap lubrication and others.
  • an actuator 5 see FIG. 5
  • this actuator 5 and its control will be discussed in more detail.
  • a resulting position setpoint value s* is specified for a position controller 6 of a control unit 7.
  • the position controller 6 is further an actual value s of the actuator 5 is supplied. Depending on these two variables s*, s, the position controller 6 determines a manipulated variable q for the actuator 5 and controls the actuator 5 accordingly.
  • the control unit 7 is an essential part of a control system according to the invention.
  • the actuator 5 is designed as a hydraulic cylinder unit as shown in FIG.
  • the manipulated variable q can be, for example, a hydraulic flow to be delivered.
  • the position controller 6 can be designed as a proportional controller (P controller) as shown in FIG.
  • P controller proportional controller
  • the position controller 6 is often designed as a proportional-integral controller (PI controller).
  • the resultant position setpoint s* is determined using a resulting base setpoint sl*.
  • the resulting position setpoint s* is identical to the resulting base setpoint s1*.
  • other variables can also be included in the resulting setpoint position value s*. This will become clear from later explanations.
  • the resulting base setpoint value s l * is determined using the actual actual draft ZE and/or the actual actual draft ZA that is soapy at the outlet.
  • the resulting base reference value s1* is determined in a node 11 as the sum of an initial base reference value s0* and an additional reference value ⁇ s1*.
  • the initial base setpoint s O * is - at least as a rule - from the incoming soapy actual draft ZE and from outlet-side actual train ZA independently.
  • the additional setpoint value ⁇ sl* is dependent on the actual tension ZE on the inlet side and on the actual tension ZA on the outlet side.
  • the additional setpoint value ⁇ s1* is determined by the determination element 13 using an actual train ZE on the entry side and a reference train ZER on the entry side.
  • the additional setpoint value ⁇ s1* can be determined by the determination element 13 using the actual train ZA on the outlet side and a reference train ZAR on the outlet side.
  • a determination block 12 of the determination element 13 can be supplied with the soapy actual tension ZE that is fed in.
  • an inlet soapy component ⁇ s1E* of the additional desired value ⁇ s1* is determined in the determination block 12 using the actual tension ZE on the inlet side and the reference tension ZER on the inlet side.
  • the running-in soapy component ⁇ slE* according to the representation in FIG. 6 according to the relationship be determined.
  • SE is an input-side sensitivity.
  • the input-side reference train ZER can optionally have the value 0. In individual cases, it can even vary over time. In this case, it is usually also necessary to change the initial base setpoint s0* to a corresponding extent.
  • the sensitivity SE on the input side and the reference train ZER on the input side can be specified for the determination element 13 by a higher-level control device 14, for example in accordance with the illustration in FIG. If present, the control device 14 is another essential part of the control system.
  • a The actual train ZA on the outlet side is supplied to a determination block 15 of the determination element 13 .
  • an outlet-side component ⁇ s1A* of the additional desired value ⁇ s1* is determined in the determination block 15 by utilizing the actual soapy draw ZA at the outlet and the soapy reference draw at the outlet ZAR.
  • SA is an output-side sensitivity.
  • the sensitivity SA on the outlet side and the reference train ZAR on the outlet side can also be specified for the determination element 13 by the higher-level control device 14 in accordance with the illustration in FIG.
  • the input-side reference train ZAR can optionally have the value 0. In individual cases, it can even vary over time. Analogous to changing the incoming soapy reference train ZER, it may be necessary at the end of the outgoing soapy reference train ZAR to change the initial basic setpoint value sO* to a corresponding extent.
  • the additional setpoint ⁇ sl* is identical to the corresponding component ⁇ slE*, ⁇ slA*.
  • both trains ZE, ZA are used.
  • the determination element 13 has a node 16 in which the additional desired value ⁇ s1* is determined as the sum of the two components ⁇ s1E*, ⁇ s1A*.
  • the target tensions ZE*, ZA*, ie the target values ZE*, ZA* supplied to the associated tension controllers 24, 25 and thus valid for the tension controls, are different variables from the reference tensions ZER, ZAR.
  • the concrete values can be temporarily the same. However, this is not systematic and is always the case.
  • the target tensions ZE*, ZA* can be specified by an operator (not shown) or for the operator to be able to vary them during the rolling of the flat rolled stock 2 .
  • the reference trains ZER, ZAR cannot be changed by the operator.
  • the higher-level control device 14 it is possible for the higher-level control device 14 to vary the reference trains ZE*, ZA* over time for technological reasons, while the reference trains ZER, ZAR are retained. This is explained in more detail below using an example. In the context of this example, it is assumed that the upstream device 3 and the downstream device 4 are roll stands and that the upstream device 3 is also preceded by a roll stand and the downstream device 4 is also followed by a roll stand.
  • a rolled stock head 20 of the rolled stock 2 (see FIG. 2) reaches the roll stand 1 at a point in time t1, the downstream device 4 at a point in time t2 and the roll stand downstream of the downstream device 4 at a point in time t3.
  • a rolling stock foot 21 of the rolling stock 2 (see FIG. 4) reaches the roll stand upstream of the upstream device 3 at a point in time t4, the upstream device 3 at a point in time t5, and the roll stand 1 at a point in time t6
  • Time t4 is generally after time t3.
  • FIG. 4 shows the rolling process during the rolling of the rolling stock 2 at time t6.
  • the outflowing soapy actual tension ZA can just about be applied. After time t6, however, this is not possible. After the point in time t6, the soapy actual tension ZA at the outlet is therefore necessarily 0.
  • the actual soapy tension ZE at the inlet is also 0, because there is already no more rolling stock 2 on the inlet side of the roll stand 1 and the rolling stock 2 has long since left the upstream device 3 has expired.
  • FIG. 3 shows the rolling process during rolling of the rolling stock 2 between times t1 and t6, more precisely between times t2 and t5.
  • the rolling stock 2 is subjected to the respective actual tension ZE, ZA at least on one side (ie on the inlet side or outlet side), and during part of this period of time even on both sides (ie on the inlet side and outlet side).
  • the rear tension controller 25 cannot be active in principle in the time period between the time t1 and the time t2. This is because the rolling stock 2 cannot be subjected to the soapy actual tension ZA on the outlet side of the roll stand 1 .
  • the determination of the leaking soapy component ⁇ slA* of the additional target value ⁇ sl* is also possible during this period.
  • the front tension controller 24 cannot be active due to the principle. This is because the rolling stock 2 cannot be subjected to the incoming soapy actual tension ZE on the entry side of the rolling stand 1 .
  • the incoming soapy component ⁇ s IE* of the additional target value ⁇ s 1* can also be determined during this period.
  • the rear tension controller 25 can be active during this period.
  • the incoming soapy sensitivity SE and/or the outgoing soapy sensitivity SA and optionally also other values such as the reference draws ZER and/or ZAR and/or the initial basic setpoint value s O* can be provided by the higher-level control device 14 .
  • the controllers implement real-time control while the rolled stock is being rolled.
  • the entirety of the controllers is usually referred to as an L1 system in specialist circles.
  • the higher-level control device 14 thus functions as a unit which is usually referred to as the L2 system in specialist circles.
  • the superordinate control device 14 includes, among other things, a rolling model 17 in which the rolling process in the rolling stand 1 is modeled.
  • the rolling model 17 is based on mathematical and physical equations that describe the rolling process.
  • the higher-level control device 14 determines the specified variables SE and/or SA and/or ZER and/or ZAR and/or sO* and, if necessary, also other variables by evaluating the rolling model 17 .
  • the higher-level control device 14 carries out a pass schedule calculation in which it determines these values and—if necessary—other values. The values determined are made available by the superordinate control device 14 to subordinate controllers (for example the position controller 6 of the control unit 7). In particular, as part of the pass schedule calculation, the higher-level control device 14 determines a target thickness d* (see FIG. 1) with which the flat rolled stock 2 should exit the roll stand 1 and the soapy reference train ZER and/or or the outlet soapy reference draft ZAR the initial base target value s O* and the inlet soapy nominal draft ZE* and/or the exit soapy nominal draft ZA*.
  • the target thickness d* can be specified for the higher-level control device 14 or can be independently determined by the higher-level control device 14 .
  • the reference trains ZER, ZAR are generally used by the higher-level control device 14 . Based on these values d*, ZER, ZAR, the superordinate control device 14 determines the required rolling force and the required adjustment.
  • the required rolling force corresponds to a reference rolling force FR, the required adjustment to the initial base sis setpoint sO* .
  • the superordinate control device 14 of the control unit 7 specifies the initial basic setpoint value s O* .
  • the superordinate control device 14 also specifies the target tension ZE* on the inlet side to the front tension controller 24 and the target tension ZA* on the outlet side to the rear tension controller 25 .
  • the higher-level control device 14 can determine the incoming soapy sensitivity SE, for example, by determining the effect of the change in the incoming soapy tension ZE on an actual rolling force F for the intended operating point of the roll stand 1 and also the effect of the Change in the rolling force F on the deflection of the rolling stand 1 is determined.
  • the product of the two mentioned effects gives the run-in soapy sensitivity SE .
  • the higher-level control device 14 can determine the outlet-side sensitivity SA by determining the effect of the change in the soapy tension ZA on the rolling force F for the intended operating point of the rolling stand 1 and also the effect the change in the rolling force F on the deflection of the rolling stand 1 is determined.
  • the product of the two mentioned effects gives the outlet-side sensitivity SA.
  • the determination element 13 can determine the sensitivities SE, SA itself. Furthermore, in this case, the determination element 13 is in particular also able to determine a change ⁇ F in the expected rolling force that corresponds to changes in the trains ZE, ZA.
  • the resulting position setpoint s* is not identical to the resulting base setpoint sl*, but is determined using other correction variables. It is thus possible, for example, according to the representation in FIG. 7, for the resultant position setpoint value s* to be determined using a correction value ⁇ s2* determined using the rolling force F.
  • the resulting position setpoint s* can be determined in a node 18 as the sum of the resulting base setpoint s1* and a correction value ⁇ s2*.
  • the correction value ⁇ s2* is determined in a determination block 19 using the actual rolling force F.
  • the determination block 19 thus implements an AGC in which an additional springing up of the roll stand 1 is (at least largely) compensated for.
  • FIG. 7 only shows the additional parts of the control unit 7 .
  • FIGS. 5 and 6 should also be consulted for the basic configuration of the control unit 7 .
  • the determination block 19 In the simplest case, only the actual rolling force F and the reference rolling force FR are fed to the determination block 19 as input variables.
  • the reference rolling force FR is made available to the determination block 19 by the higher-level control device 14 as shown in FIG.
  • the determination block 19 in addition to the actual rolling force F, is also supplied with a value which, apart from the correction value ⁇ s2* determined by the determination block 19, already corresponds to the resulting setpoint position value s*.
  • the determination block 19 can be supplied with the resulting basic setpoint value s1*. In this case, the determination block 19 also takes into account the resulting basic setpoint value s1* as part of the determination of the correction value ⁇ s2*.
  • the determination element 13 also determines the associated expected change ⁇ F in the reference rolling force FR in addition to the additional setpoint value ⁇ s 1 *.
  • the expected change ⁇ F in the reference rolling force FR is taken into account by the determination block 19 when determining the correction value ⁇ s2*. sighted.
  • the determination block 19 can optionally also be supplied with the actual position value s.
  • FIG. 8 starts from the control unit 7 of FIG. 7.
  • an activation signal A and a reset signal R can be supplied to the determination block 19.
  • the activation signal A has the value 0 or the value 1.
  • a value of the activation signal A of 1 causes the determination block 19 to be activated.
  • the determination block 19 determines the respectively valid correction value ⁇ s2* using the rolling force F.
  • the resultant position setpoint value s* is obtained using the rolling force F determined.
  • a value of the activation signal A of 0 deactivates the determination block 19.
  • the determination block 19 outputs the correction value ⁇ s2* determined last, but does not update the correction value ⁇ s2* any further.
  • the reset signal R is only supplied to the determination block 19 if no rolling stock is being rolled in the roll stand 1 . Supplying the reset signal R causes the correction value ⁇ s2* last determined to be reset to 0.
  • the activation signal A varies as a function of time t. Activation signal A has the value 0 up to point in time t1. The activation signal A then rises—usually abruptly—to the value 1. At time t 6 the activation signal A drops to the value 0—usually abruptly again. At a point in time t7, which according to FIG. 9 is after point in time t.sub.6, the reset signal R is (briefly) specified.
  • FIG. 10 shows a further embodiment of the control unit 7 from FIG.
  • the embodiment of FIG. 10 could also be based on the embodiment of the control unit 7 of FIGS. 7 and 8 without further ado.
  • a thickness d of the rolling stock 2 ie its actual value, is recorded on the outlet side of the roll stand 2 by means of a corresponding measuring device 22.
  • the thickness d is compared to a target thickness d*.
  • a correction value ⁇ s3* is determined in the determination block 23 on the basis of the deviation of the thickness d of the rolled stock 2 from the target thickness d*.
  • the correction quantity ⁇ s3* is fed to the node 18 .
  • the resulting position setpoint s* is determined using the correction variable ⁇ s3*. Residual errors of all kinds can be compensated for by this procedure.
  • the present invention has many advantages. If and as long as the AGG is active - i.e. in particular when rolling the middle piece of the rolling stock 2 - the AGG and also any thickness control based on the measurement of the thickness d no longer have to compensate for the entire error caused by the change in the rolling force F in the Compensate for the adjustment of the roll stand 1, since a partial compensation is already effected by the train-dependent determination of the resulting desired position value s*, ie by the correction based on the trains ZE, ZA. If and as long as the AGG is inactive - i.e.
  • the tension-dependent determination of the resulting position setpoint s* can at least partially correct thickness errors that could not otherwise be corrected at all.
  • this can the initial section and/or the end section of the rolling stock 2, the thickness d of which deviates by more than the permissible tolerance from the target thickness d*, can be significantly shortened, often to approx. the half .
  • the structure of the sling regulation will also be improved immediately after the tapping.
  • R Reset signal s Pos it ions actual value s* Resulting position setpoint sO*, sl* Basic setpoints t Time tl to t7 points in time vA, vU, vZ Speeds
  • ZAR, ZER reference trains ⁇ sl* additional target value ⁇ slA*, ⁇ slE* components ⁇ s2 * correction value ⁇ s3* correction of large ⁇ vA, övE manipulated variables

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)

Abstract

L'invention concerne un produit laminé plat (2) en métal laminé dans une cage de laminoir. Un système de positionnement (6) destiné au réglage de la mise en marche d'un actionneur (5), qui permet de régler une emprise de la cage de laminoir (1), assure la détermination d'une grandeur de réglage (q) pour l'actionneur (5) en fonction d'une valeur de position de consigne (s *) résultante et d'une valeur de position réelle (s) de l'actionneur (5), et la commande de l'actionneur (5) de manière correspondante. La valeur de position de consigne (s *) résultante est déterminée en ayant recours à une valeur de base de consigne (s1 *) résultante. La valeur de base de consigne (s1 *) résultante est déterminée comme la somme d'une valeur de base de consigne (s0 *) initiale et d'une valeur de consigne supplémentaire (δs1 *). La valeur de consigne supplémentaire (δs1 *) est déterminée par un élément de détermination (13) en ayant recours à une tension réelle (ZE) côté entrée et à une tension de référence (ZER) côté entrée et/ou en ayant recours à une tension réelle (ZA) côté sortie et à une tension de référence (ZAR) côté sortie. Au lieu des tensions réelles (ZE, ZA), on peut également utiliser les tensions de consigne (ZE *, ZA *) correspondantes de régulations de tension correspondantes. Toutefois, dans les deux cas, les tensions de référence (ZER, ZAR) et les tensions de consigne (ZE *, ZA *) sont des grandeurs différentes.
PCT/EP2022/050608 2021-01-18 2022-01-13 Réduction des changements d'épaisseur dus à la tension lors du laminage WO2022152779A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP22700614.5A EP4277757A1 (fr) 2021-01-18 2022-01-13 Réduction des changements d'épaisseur dus à la tension lors du laminage
MX2023008387A MX2023008387A (es) 2021-01-18 2022-01-13 Reduccion de cambios de espesor inducidos por la fuerza de traccion durante el laminado.
US18/261,938 US20240075509A1 (en) 2021-01-18 2022-01-13 Reducing tensile force-induced changes in thickness during rolling
CN202280010624.4A CN116783009A (zh) 2021-01-18 2022-01-13 在轧制时由拉力引起的厚度变化的减少
JP2023543045A JP2024503870A (ja) 2021-01-18 2022-01-13 圧延中の厚さの張力誘導変化の減少

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP21152130 2021-01-18
EP21152130.7 2021-01-18

Publications (1)

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WO2022152779A1 true WO2022152779A1 (fr) 2022-07-21

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PCT/EP2022/050608 WO2022152779A1 (fr) 2021-01-18 2022-01-13 Réduction des changements d'épaisseur dus à la tension lors du laminage

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US (1) US20240075509A1 (fr)
EP (1) EP4277757A1 (fr)
JP (1) JP2024503870A (fr)
CN (1) CN116783009A (fr)
MX (1) MX2023008387A (fr)
WO (1) WO2022152779A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003164906A (ja) 2001-11-29 2003-06-10 Toshiba Ge Automation Systems Corp 圧延機の制御方法
EP2620233A1 (fr) 2012-01-24 2013-07-31 Siemens Aktiengesellschaft Procédé de traitement de produits laminés dans un laminoir
EP3231522A1 (fr) 2016-04-14 2017-10-18 Primetals Technologies Germany GmbH Controle de tension robuste

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003164906A (ja) 2001-11-29 2003-06-10 Toshiba Ge Automation Systems Corp 圧延機の制御方法
EP2620233A1 (fr) 2012-01-24 2013-07-31 Siemens Aktiengesellschaft Procédé de traitement de produits laminés dans un laminoir
EP3231522A1 (fr) 2016-04-14 2017-10-18 Primetals Technologies Germany GmbH Controle de tension robuste

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
VON J. M. ALEXANDER: "On the theorie of rolling", PROCEEDINGS DER ROYAL SOCIETY LONDON, vol. 326, 1972, pages 553 - 563

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MX2023008387A (es) 2023-07-31
US20240075509A1 (en) 2024-03-07
JP2024503870A (ja) 2024-01-29
EP4277757A1 (fr) 2023-11-22
CN116783009A (zh) 2023-09-19

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