EP0130231A1 - Arrangement de circuits pour la régulation de la force de traction transmise entre les cages de cylindres d'un train de laminoir à cages multiples - Google Patents

Arrangement de circuits pour la régulation de la force de traction transmise entre les cages de cylindres d'un train de laminoir à cages multiples Download PDF

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Publication number
EP0130231A1
EP0130231A1 EP83106518A EP83106518A EP0130231A1 EP 0130231 A1 EP0130231 A1 EP 0130231A1 EP 83106518 A EP83106518 A EP 83106518A EP 83106518 A EP83106518 A EP 83106518A EP 0130231 A1 EP0130231 A1 EP 0130231A1
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EP
European Patent Office
Prior art keywords
speed
correction
setpoint
value
theoretical
Prior art date
Legal status (The legal status 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 status listed.)
Granted
Application number
EP83106518A
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German (de)
English (en)
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EP0130231B1 (fr
Inventor
Roland Dipl.-Ing. Weber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
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Siemens AG
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Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP83106518A priority Critical patent/EP0130231B1/fr
Priority to AT83106518T priority patent/ATE25013T1/de
Priority to DE8383106518T priority patent/DE3369256D1/de
Priority to JP59138865A priority patent/JPS6037207A/ja
Publication of EP0130231A1 publication Critical patent/EP0130231A1/fr
Application granted granted Critical
Publication of EP0130231B1 publication Critical patent/EP0130231B1/fr
Expired legal-status Critical Current

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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
    • B21B37/48—Tension control; Compression control
    • B21B37/52—Tension control; Compression control by drive motor control

Definitions

  • the invention relates to a circuit arrangement of the type specified in the preamble of claim 1.
  • DE-A-25 41 071 describes a method and a device of the aforementioned type, with the aid of which it should be possible to set the speed ratios required for a defined tensile stress in the rolling stock in a short time and in a simple manner.
  • the tension in front of and behind each stand, to which a tension difference control device is assigned is determined from the drive torque, the acceleration torque and the deformation torque in the roll gap.
  • One of the stands takes on the function of a guide stand, which essentially determines the rolling speed in the street.
  • the use of this method does not rule out that deviations from the setpoint in front of and behind the control tower Tensile stresses occur that result from the sum of the moment errors of the other stands. These deviations become clearer the greater the number of stands of such a rolling mill.
  • EP-PS 0 008 037 describes a device for regulating the tensile force transmitted in the rolling stock in a rolling mill containing m stands, in which speed controllers are also assigned to the stand drives, their setpoints using Tension difference control devices are corrected according to the parameters of a minimum tension control.
  • the previous scaffolding should also be provided with such a control device. This initially avoids that the torque errors of the other stands on the guide stand add up and that there are changing tensions within the rolling stock.
  • a further improvement in the control behavior while saving a separate control circuit can be achieved by the invention specified in claim 1. This ensures that a change in speed does not first have to occur in the reference stand in order to carry out a tension correction, but that the tension change in the last stand itself and directly forms the correction value for the other stands in the manner described.
  • the rolling speed of the road remains absolutely constant because of the speed control of the last stand, which was uncorrected during the throughput phase.
  • circuit arrangement according to claim 2 results in an overall smoother control process and thus a largely balanced behavior of the rolling mill.
  • Fig. 1 the work rolls 5 of a roll stand, not shown, including the associated DC drive motor 6 and a speed control arrangement 7 with the speed controller 8 and the actuator 9 are shown schematically.
  • a tachometer generator 10 coupled to the drive motor 6 supplies an output signal which is proportional to the speed and which is compared with a setpoint value n.
  • an additional speed setpoint ⁇ * is fed to the comparison point 11.
  • a current transformer 12, which supplies a voltage proportional to the armature current i a , and a sensor 13 are provided, the output voltage of which is proportional to the flux 1 in the field winding 14 of the drive motor.
  • F E denotes the tensile force acting in the rolling stock 15 in the rolling direction on the entry side of the stand and F, the tensile force on the exit side.
  • a control circuit shown in FIG. 2 This consists of an actual value Computer 16, a setpoint computer 17, a comparator 18 and a correction controller 19 (minimum tension controller).
  • the drive torque Ma F - i a is composed of the acceleration torque Mb and the rolling torque Mw, which in turn is the sum of the deformation moments Mh and Mv of the horizontal and vertical rollers, and the torque Mz caused by the tensile stress.
  • the acceleration torque Mb can be derived from the speed n and the deformation moments Mh and Mv result from the rolling forces Fh and Fv measured by means of rolling force transducers by multiplication by a factor Kh or Kv corresponding to the lever arm of the rolling forces.
  • the factor Kh can be determined for universal stands based on the roll gap geometry and is specified by the operator.
  • the lever arm factor Kh is calculated in a balancing circuit for duo scaffolds.
  • the factor Kv is dependent on various influencing variables that cannot be determined theoretically and is therefore also determined with the aid of the adjustment circuit and then stored.
  • the actual value computer 16 accordingly receives the measured values i a , ⁇ , n and Fh and, if appropriate, the variables Fv and Kh.
  • the differential voltage at the output of the summing element 21, which is proportional to the moment Mz, is fed to a comparison point 25. If the scaffolding is a duo, switches 26 and 27 assume the position shown in dashed lines.
  • an integrator 28 connected downstream of the comparison point 25 changes the lever arm factor until the product Fh.
  • Kh and the product ⁇ ⁇ i a minus the acceleration torque Mb are of the same magnitude.
  • the lever arm factor Kh calculated in this way is saved for the rest of the stitch in the second stand before the tapping.
  • the switches 26 and 27 assume the position shown for determining the lever arm factor Kv.
  • the automatic adjustment of the lever arm factor Kh for duo or Kv for universal stands with subsequent storage takes place in the same way, but with additional consideration of the train F E on the entry side.
  • the associated input-side train-related torque Mg supplied to the comparison point 25 in FIG. 2 corresponds to the output in the adjusted state Share of the tensile force setpoint, which is given to the preceding control device and thus the preceding stand, multiplied by the roller radius of the stand for which the lever arm factor is being calculated. In any case, the calculation runs so fast that it ends before the rolling stock enters the next stand.
  • the difference between the output signal Mz of the summing element 21 and a torque setpoint Mz is fed to the minimum tension controller 19.
  • the torque setpoint is determined by means of the setpoint calculator 17 from the specific train specified by the operator * the rolling stock cross-sections A, the roll diameter dw and a correction value are determined.
  • the speed correction setpoint value ⁇ n * delivered by the minimum tension controller 19 is during the tapping phase of each stand of the speed control device of the following or all subsequent drives - in the example shown as ⁇ n * 2 'of the speed control on stand 2 - and after tapping in the following stand via a reversing amplifier 29 the speed control device of the own drive - in the example as ⁇ n * 1 'of the speed control device on stand 1 - supplied.
  • a switch 30 is provided for switching, which must briefly assume the intermediate position shown so that the output signal of the minimum train controller is reset to zero.
  • the actuation signal for the switch 30 is expediently determined with the aid of a known and therefore not shown rolling stock replica.
  • the control circuit shown and described in FIGS. 1 and 2 is assigned to each individual scaffold drive with the exception of the last one.
  • the control circuit assigned to the last scaffold differs from that described above essentially in that the minimum tension controller 19 does not generate a speed correction variable, but rather a correction setpoint K * for the specific tensile setpoints of all scaffolds, which is formed from the target actual value deviation of the tensile stress Mz of the last scaffold.
  • This control circuit assigned to the control tower is shown in FIGS. 3 and 4. Identical function elements are provided with the same reference symbols.
  • the control element 7 shown in FIG. 3 differs from that according to FIG. 1 in that no correction value is supplied to its comparison point 31 during the through phase.
  • the correction setpoint ⁇ n * shown in dashed lines during the tapping phase remains unaffected.
  • the speed control therefore works autonomously during the run-through phase and always keeps the drive at the speed value determined during the tapping phase.
  • the actual value calculator 16 shown in FIG. 4, like the target value calculator 17, is identical to that according to FIG. 2.
  • the correction controller 32 differs from the minimum tension controller 19 of FIG. 2 in that it does not have a speed correction setpoint, but rather a correction setpoint formed from the tension deviation A Mz arising at the comparison point 18 K * generated as manipulated variable.
  • a four-stand roller mill is shown schematically.
  • the stands including the drive are indicated by the rollers 1 to 4.
  • Each scaffold is a control circuit in the form of an actual value calculator 16, a setpoint calculator 17, a minimum Switzerlandreglers 19 and a speed control element 7 assigned, which are designated in this figure according to the assignment to the respective scaffold with 1.7 to 4.7, with 1.16 to 4.16, with 1.17 to 4.17 and with 1.19 to 3.19.
  • the correction controller 32 of the last stand generates the manipulated variable * K , which is not used to correct the speed of the drive of the last scaffolding.
  • the speed of the last stand is regulated by the speed control element 4.7 to a constant speed value n determined during the tapping phase with the aid of ⁇ n * 4 'as soon as the tapping phase has ended.
  • the manipulated variable generated by the correction element 32 * K is a variable formed from the deviation of the pulling torque Mz4 from the setpoint Mz 4, which corresponds to the specified setpoints of the specific output trains * A1 to * A3 is fed directly to the corresponding comparison points 1.33 to 3.33 and the setpoint calculator 4.17 of the last stand.
  • the specific tensile stress setpoints experience a correction that counteracts the deviation of the tensile torque Mz4 of the last stand from its setpoint Mz 4.
  • the individual mill stand drives are involved in error compensation in absolute proportion to the respective cross-section of the rolling stock. This has the desired consequence that experience is taken into account that the probability of the occurrence of errors is greatest where the greatest moments of deformation have to be applied.
  • the error compensation is weighted so that the effect is greatest where the least disadvantageous consequences are to be feared, namely towards the large roll cross sections.
  • the circuit arrangement according to the present invention has the advantage that, as can be seen from a comparison of FIGS. 1 and 3 or 2 and 4, largely identical control elements can be used in all scaffolds including the guide scaffold.
  • the manipulated variable may * K only act on one side, ie only affect the exit moments. If it also had an influence on the moments of entry, both effects in terms of error compensation would cancel each other out.
  • the determination of the lever arm factor is complete as soon as the tensile torque from the scaffold 1 M z1 of the actual value calculator 1.16 has become equal to the associated setpoint (for scaffold 1 before the scaffold 2 is tapped) it has become zero.
  • the lever arm factor is saved for the rest of the stitch. The determination of the lever arm factor must be completed before tapping the scaffold 2.
  • the minimum tension controller 1.19 With the tapping in stand 2 (FIG. 7), the minimum tension controller 1.19 becomes effective, at the actual value input of which the train-dependent torque M z1 of the actual value calculator 1.16 is applied and whose setpoint input receives an initially constant setpoint M z 1.
  • the proportional element 1.33 is switched to "save", the output signal of the minimum tension controller 1.19 is briefly set to zero and the output of the proportional element 2.33 (FIG. 8) is then via the reversing amplifier 29 (FIG. 2) switched as ⁇ n * 1 to speed controller 1.7 on scaffold 1 (self-adjustment for scaffold 1).
  • the additional speed setpoint .DELTA.n * 2 is still given to the speed controller 2.7 on the frame 2 from the memory 1.33. This additional speed setpoint remains additively superimposed if, according to FIG.
  • the correction controller 2.19 is switched to self-adjustment and specifies the additional speed setpoint ⁇ n * 3 '.
  • the additional speed setpoint .DELTA.n * 3 'of the correction controller 2.19 (FIG. 5), which acted on the speed controller 3.7 of the tower 3 until it tapped into the tower 4, is also further given to the tower 3 as a stored value .DELTA.n * 3, while rend the output of 2.19 is switched to the speed controller of stand 2 after the previous zero setting with the opposite sign as ⁇ n * 2. This procedure guarantees a smooth transition to self-adjustment.
  • the processes described in connection with the scaffold 2 are repeated on all other scaffolds.
  • the sequence on the scaffold 4 or on the last scaffold m differs from these processes in that this scaffold is not switched to self-adjustment, but is operated at constant speed after adjustment by the proportional member 3.33 (FIG. 5) and completed lever arm calculation by 4.16.
  • the manipulated variable calculated by the correction controller (32) K * as a correction value for the specific tensile stresses on the outlet side A1 * ... A * (m-1) of the other scaffolds used.
  • the additional speed setpoint is expediently not only fed to the speed controller of the following stand (shown in dashed lines), but to the speed controllers of all subordinate stands during the tapping phase.
  • speed errors of a stand can be taken into account by presetting all the stands still directly involved in the rolling process, which leads to a significant shortening of the control process in the later tapping in these stands.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Machine Tool Units (AREA)
  • Crushing And Grinding (AREA)
  • Disintegrating Or Milling (AREA)
EP83106518A 1983-07-04 1983-07-04 Arrangement de circuits pour la régulation de la force de traction transmise entre les cages de cylindres d'un train de laminoir à cages multiples Expired EP0130231B1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP83106518A EP0130231B1 (fr) 1983-07-04 1983-07-04 Arrangement de circuits pour la régulation de la force de traction transmise entre les cages de cylindres d'un train de laminoir à cages multiples
AT83106518T ATE25013T1 (de) 1983-07-04 1983-07-04 Schaltungsanordnung zur regelung der im walzgut uebertragenen zugkraefte zwischen den geruesten in einer mehrgeruestigen walzstrasse.
DE8383106518T DE3369256D1 (en) 1983-07-04 1983-07-04 Circuit arrangement to regulate the tensile force transferred between the housings of a multiple housing mill train
JP59138865A JPS6037207A (ja) 1983-07-04 1984-07-04 圧延ミル調節用回路装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP83106518A EP0130231B1 (fr) 1983-07-04 1983-07-04 Arrangement de circuits pour la régulation de la force de traction transmise entre les cages de cylindres d'un train de laminoir à cages multiples

Publications (2)

Publication Number Publication Date
EP0130231A1 true EP0130231A1 (fr) 1985-01-09
EP0130231B1 EP0130231B1 (fr) 1987-01-21

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EP83106518A Expired EP0130231B1 (fr) 1983-07-04 1983-07-04 Arrangement de circuits pour la régulation de la force de traction transmise entre les cages de cylindres d'un train de laminoir à cages multiples

Country Status (4)

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EP (1) EP0130231B1 (fr)
JP (1) JPS6037207A (fr)
AT (1) ATE25013T1 (fr)
DE (1) DE3369256D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0439663A1 (fr) * 1990-02-02 1991-08-07 Siemens Aktiengesellschaft Procédé de commande d'un laminoir continu à plusieurs cages
EP0698572A1 (fr) * 1994-08-27 1996-02-28 Licentia Patent-Verwaltungs-GmbH Méthode de contrÔle des vitesses de bandes de matériau dans un dispositif de transport ou de tirage d'une bande de matériau

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2620424C2 (ru) * 2015-10-21 2017-05-25 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Магнитогорский государственный технический университет им. Г.И. Носова" (ФГБОУ ВПО "МГТУ") Способ автоматического регулирования скорости горизонтальных и вертикальных валков универсальной клети стана горячей прокатки

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2721973A1 (de) * 1977-05-14 1978-11-23 Schloemann Siemag Ag Walzung von warmband in einer kontinuierlichen walzenstrasse
EP0008037A1 (fr) * 1978-08-03 1980-02-20 Siemens Aktiengesellschaft Dispositif de commande de la tension dans un laminoir continu

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5226316A (en) * 1975-08-25 1977-02-26 Naniwa Seisakusho Kk Turntable reciprocative rotation type twoostation greensand mold
JPS5298663A (en) * 1976-02-16 1977-08-18 Nippon Kokan Kk Device for controlling tension in tandem rolling machine

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2721973A1 (de) * 1977-05-14 1978-11-23 Schloemann Siemag Ag Walzung von warmband in einer kontinuierlichen walzenstrasse
EP0008037A1 (fr) * 1978-08-03 1980-02-20 Siemens Aktiengesellschaft Dispositif de commande de la tension dans un laminoir continu

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
TECHN. MITT. AEG-TELEFUNKEN, Band 66, Nr. 6, Juni 1976, Seiten 255-261, Berlin, DE. *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0439663A1 (fr) * 1990-02-02 1991-08-07 Siemens Aktiengesellschaft Procédé de commande d'un laminoir continu à plusieurs cages
EP0698572A1 (fr) * 1994-08-27 1996-02-28 Licentia Patent-Verwaltungs-GmbH Méthode de contrÔle des vitesses de bandes de matériau dans un dispositif de transport ou de tirage d'une bande de matériau

Also Published As

Publication number Publication date
EP0130231B1 (fr) 1987-01-21
JPS6037207A (ja) 1985-02-26
ATE25013T1 (de) 1987-02-15
DE3369256D1 (en) 1987-02-26

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