EP0222231B1 - Dispositif de commande des mouvements de levage et de serrage des rouleaux presseurs d'enrouleurs de bandes à chaud - Google Patents

Dispositif de commande des mouvements de levage et de serrage des rouleaux presseurs d'enrouleurs de bandes à chaud Download PDF

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Publication number
EP0222231B1
EP0222231B1 EP86114743A EP86114743A EP0222231B1 EP 0222231 B1 EP0222231 B1 EP 0222231B1 EP 86114743 A EP86114743 A EP 86114743A EP 86114743 A EP86114743 A EP 86114743A EP 0222231 B1 EP0222231 B1 EP 0222231B1
Authority
EP
European Patent Office
Prior art keywords
pressure
force
lifting
control
movement
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.)
Expired - Lifetime
Application number
EP86114743A
Other languages
German (de)
English (en)
Other versions
EP0222231A2 (fr
EP0222231A3 (en
Inventor
Jürgen Dr. Klöckner
Dieter Rosenthal
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.)
SMS Siemag AG
Original Assignee
SMS Schloemann Siemag AG
Schloemann Siemag AG
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 SMS Schloemann Siemag AG, Schloemann Siemag AG filed Critical SMS Schloemann Siemag AG
Priority to AT86114743T priority Critical patent/ATE102092T1/de
Publication of EP0222231A2 publication Critical patent/EP0222231A2/fr
Publication of EP0222231A3 publication Critical patent/EP0222231A3/de
Application granted granted Critical
Publication of EP0222231B1 publication Critical patent/EP0222231B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • B21C47/00—Winding-up, coiling or winding-off metal wire, metal band or other flexible metal material characterised by features relevant to metal processing only
    • B21C47/02—Winding-up or coiling
    • B21C47/04—Winding-up or coiling on or in reels or drums, without using a moving guide
    • B21C47/06—Winding-up or coiling on or in reels or drums, without using a moving guide with loaded rollers, bolts, or equivalent means holding the material on the reel or drum
    • B21C47/063—Winding-up or coiling on or in reels or drums, without using a moving guide with loaded rollers, bolts, or equivalent means holding the material on the reel or drum with pressure rollers only

Definitions

  • the invention relates to a device for controlling the lifting and pressing movements of the band pressure rollers of hot rolled coils with a rotating reel mandrel as a function of signals which indicate the respective position of the reel mandrel on the circumferential front edge of the rolled strip, by means of electrohydraulic positioning of piston cylinder units which actuate the band pressure rollers with simultaneous force control.
  • a known control device DE-AS 21 58 721
  • the pinch rollers are raised during the winding process by the amount of the strip thickness, ie the size of the radial increase, which has caused the front strip edge, if this increase passes under them.
  • a pulse generator which is coupled to the reel mandrel, which influences a pulse counter which, via control logic, generates signals for the control device, on the basis of which the latter causes the actuation of the piston-cylinder units connected to the respective pressure roller, through the pressure area of which the radial one Increase in the resulting band waistband.
  • the path of the strip edge of the rolled strip running onto the coiler mandrel is detected by contactless sensors during the formation of the first turn and is tracked and recorded with the aid of electronic recording devices.
  • the positioning of the pressure rollers is then controlled with the aid of the recording devices and these downstream evaluation devices.
  • the up and down movements of the actuating elements of the piston-cylinder units, which bring about the lifting and pressing movements of the band pressure rollers, are controlled by two known control devices and, as also described in JP-A-59 179, via two independent electro-hydraulic control circuits, namely a position control circuit and a force control loop.
  • the lifting movement of the belt pressure roller is effected and controlled in each case by specifying the corresponding position value via the position control loop, while the pressure movement and the subsequent pressing is also effected by specifying a force setpoint via the force control loop. Remains during position control the force control loop is opened, ie it is derived from the signals from the belt tracking, depending on the process, continuously switched between the position and force control for each tape opening roller.
  • this type of control has the further disadvantage that the rapid switching causes shocks which impair the dynamic behavior of the elements involved in the movement sequence.
  • a further difficulty arises with these known controls if, due to a malfunction, they receive no or incorrect positioning signals or no switching signals or those at the wrong time, because in the one case the piston-cylinder unit has the position in which it is no longer changing and the necessary evasive movement is no longer being carried out and, in the other case, the belt pressure rollers are held at maximum force when the position is controlled.
  • this type of control has the disadvantage that the fast Switching causes shocks that affect the dynamic behavior of the elements involved in the movement.
  • the position control there is a further difficulty with these known controls if they receive no or incorrect positioning signals due to a fault, since in this case the piston-cylinder unit no longer changes the position in which it is currently located and the z. B. no longer performs the necessary evasive movement. Additional overload protection devices must therefore be provided.
  • the invention has for its object to improve the generic control devices so that these disadvantages and difficulties are eliminated and, if necessary, the arrangement of special overload protection devices can be dispensed with.
  • This object is achieved in that the positioning during the lifting and the pressing movement by position control with subordinate force control with closed position and pressure control loops by specifying a position setpoint corresponding to the respective pressing or lifting position of the band pressure rollers and specifying limited force setpoints is effected for both directions of movement.
  • the limitation of the desired force value for the increase can be the same as the maximum value that can be set for the pressure control circuit.
  • a slope limiter is arranged downstream of the force controller as the invention provides.
  • the control reacts like an overload protection because the subordinate force control loop always regulates the actual force value to the set limit setpoint. Since the control system acts like an overload safety device, there is no need to equip the individual piston cylinder units with special overload safety devices, such as pneumatic support cylinders. Finally, there is a further advantage that the previously necessary mounting of the pressure rollers in a support pivotable against the actual carrier carrying out the lifting and pressing movements and elastically supported against this support lever can be dispensed with, since the mode of operation of the control according to the invention not only provides such a cushioning makes unnecessary.
  • the pressure roller 3 which is only reproduced on its own for the sake of clarity, is supported for the mandrel 2 of the (not shown) rolled strip heating reel in a shell carrier 1 which is articulated via the piston rod 4 to the piston cylinder unit 5 which is mounted in a fixed position.
  • the piston 5a of this piston-cylinder unit 5 can be pressurized on both sides via the hydraulic lines 6 and 7 with the aid of a control valve 18 and thus moves the pressure roller 3.
  • a displacement sensor 8 is attached to the piston rod 4, with which the actual position Sist of the pressure roller 3 is measured.
  • the output side 9 of the position sensor leads via line 10 and its branches 10a, 10b to a computer system 11 and to a position controller 12, which is likewise connected to the computer system via line 13.
  • the computer 11 specifies the outer position control loop setpoints S des.
  • the position controller 12 is followed by a force setpoint limiter 14 that is adjustable for both directions of movement.
  • the output side of the force setpoint limiter 14 supplies the force setpoints Fset for the inner force control loop.
  • the actual force value Fist is determined by means of the pressure transmitters 19 and 20.
  • the force controller 16, which is followed by a steepness limiter 17, receives as input the difference between the actual force value Fist and the desired force value Fset and controls the control valve 18.
  • the actual force value Fist is always regulated to the force setpoint Fsetpoint specified by the outer position control loop. Both control loops are constantly closed.
  • Fig. 2 it follows that both movements, the lifting movement for rapid retraction of the pressure roller 3 by the amount of radial increase in the growing band band before it reaches the area of the pressure roller 3 and that then pressing band B shortly after the radial increase has passed through the area in position control with subordinate force control.
  • the position control loop is first given the setpoint 1, which is dependent on the strip thickness and the kinematics of the pressure roller system. After passing the front belt edge at time t 1, the position setpoint is changed so that the direction of movement is reversed.
  • the pressure roller 3 lies on the belt B. Since the position setpoint 13 has been set so high that a constant value is constantly present as the force setpoint 15, the inner force control loop regulates the actual force value 21 to this constant value.
  • the band B is thus pressed in the direction of the mandrel 2 with a defined force, the size of which can be determined as a function of the respective dimensions and the deformation resistance of the band B.
  • the position setpoint is then changed with reference to the added belt effect and the next lifting movement is initiated. To do this, it is necessary to track the current actual position value already during the pressing movement, since the change in position is derived from the current actual position.
  • the computer 11 carries out calculation and specification of these changing position setpoints. The other settings at times t3, t4 and t5 are made accordingly.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Winding, Rewinding, Material Storage Devices (AREA)
  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
  • Replacement Of Web Rolls (AREA)
  • Winding Of Webs (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)

Claims (3)

  1. Dispositif pour la commande de mouvements de levage et de serrage de rouleaux de serrage (3) de bobineuses à chaud pour des bandes laminées, comportant un mandrin de bobineuse rotatif en fonction de signaux, qui indiquent la position du côté avant de la bande laminée qui tourne avec le mandrin (2) de bobineuse, par un positionnement électro-hydraulique d'appareils à cylindre à piston (5, 5a) actionnant les rouleaux de serrage (3) des bandes en réglant simultanément la force, caractérisé en ce que le positionnement lors du mouvement de levage et du mouvement de serrage est provoqué par la régulation de position comportant une régulation en cascade de la force lorsque les circuits de régulation de la force et du positionnement restent fermés en indiquant une valeur de référence (13) de la position correspondant à chaque position de levage et de serrage des rouleaux de serrage (5, 5a) et en fixant des valeurs de référence limites (15) de la force pour les deux directions de mouvement.
  2. Dispositif selon la revendication 1, caractérisé en ce que la limite de la valeur de référence de la force pour le mouvement de levage est égale à la valeur maximale pouvant être réglée dans le circuit de réglage de la force.
  3. Dispositif selon une ou plusieurs des revendications 1 et 2, caractérisé par un limiteur de pente (17) dépendant de la direction, disposé dans le circuit de réglage du serrage après le régulateur de la force (16).
EP86114743A 1985-11-11 1986-10-23 Dispositif de commande des mouvements de levage et de serrage des rouleaux presseurs d'enrouleurs de bandes à chaud Expired - Lifetime EP0222231B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86114743T ATE102092T1 (de) 1985-11-11 1986-10-23 Vorrichtung zur steuerung der anhebe- und andruckbewegungen der bandandruckrollen von walzbandwarmhaspeln.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19853539900 DE3539900A1 (de) 1985-11-11 1985-11-11 Vorrichtung zur steuerung der anhebe- und andruckbewegungen der bandandruckrollen von walzbandwarmhaspeln
DE3539900 1985-11-11

Publications (3)

Publication Number Publication Date
EP0222231A2 EP0222231A2 (fr) 1987-05-20
EP0222231A3 EP0222231A3 (en) 1989-03-15
EP0222231B1 true EP0222231B1 (fr) 1994-03-02

Family

ID=6285647

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86114743A Expired - Lifetime EP0222231B1 (fr) 1985-11-11 1986-10-23 Dispositif de commande des mouvements de levage et de serrage des rouleaux presseurs d'enrouleurs de bandes à chaud

Country Status (9)

Country Link
US (1) US4736605A (fr)
EP (1) EP0222231B1 (fr)
JP (1) JP2898282B2 (fr)
KR (1) KR930008913B1 (fr)
CN (1) CN86107620A (fr)
AT (1) ATE102092T1 (fr)
DE (2) DE3539900A1 (fr)
ES (1) ES2050099T3 (fr)
SU (1) SU1558292A3 (fr)

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US4964587A (en) * 1986-12-25 1990-10-23 Mitsubishi Jukogyo Kabushiki Kaisha Coiler
DE3910991A1 (de) * 1989-04-05 1990-10-11 Schloemann Siemag Ag Verfahren zum anwickeln von baendern in haspelanlagen
JP3266935B2 (ja) * 1991-08-28 2002-03-18 住友金属工業株式会社 巻取り心棒ならびに巻取り装置および方法
IT238735Y1 (it) * 1995-04-21 2000-11-13 Perini Fabio Spa Svolgitore per bobine di materiale nastriforme con sistema dicontrollo della pressione di svolgimento
US5713534A (en) * 1995-06-22 1998-02-03 Imd Corporation Continuous web winding apparatus
US5829708A (en) * 1996-10-02 1998-11-03 Memtec America Corporation Apparatus and method for making melt-blown nonwoven sheets
US5957404A (en) * 1998-04-20 1999-09-28 Kvaerner Metals Ironing roll with cam for following coil/strip tangent point
GB0020160D0 (en) * 2000-08-17 2000-10-04 Vai Ind Uk Ltd Steckel furnace coiler and apparatus therefor
EP1197272B1 (fr) * 2000-10-12 2006-08-02 Elpatronic Ag Machine à cintrer à deux rouleaux ainsi que procédé pour cintrer des tôles
US6588245B2 (en) * 2001-08-15 2003-07-08 General Electric Co. Roll gap control for coiler
KR100792846B1 (ko) * 2006-12-19 2008-01-14 주식회사 포스코 전기로의 스크랩 다짐장치
DE102007002218A1 (de) * 2007-01-10 2008-07-17 Sms Demag Ag Wickelvorrichtung zum Wickeln von Bändern
KR200446432Y1 (ko) * 2007-11-08 2009-10-28 현대제철 주식회사 루퍼 장치의 작동 실린더 구조체
CN103223420B (zh) * 2012-01-29 2014-12-24 宝山钢铁股份有限公司 一种控制热轧钢卷内圈压痕的方法和系统
CN102615332B (zh) * 2012-03-30 2014-08-27 郑州市华驰薄板科技有限公司 冷轧带钢纵剪生产线
CN102615104B (zh) * 2012-03-30 2015-04-08 郑州市华驰薄板科技有限公司 冷轧带钢废边卷取机
CN103436681A (zh) * 2013-09-06 2013-12-11 无锡嘉联不锈钢有限公司 退火炉前的压辊装置
KR101477104B1 (ko) * 2013-10-30 2014-12-29 현대제철 주식회사 압연 코일용 권취 장치
IT201600108463A1 (it) * 2016-10-27 2018-04-27 Celli Nonwovens Spa Macchina e metodo per l'avvolgimento di strisce di materiale nastriforme con mezzi per il taglio trasversale delle strisce a fine avvolgimento
CN107552576B (zh) * 2017-08-22 2019-04-02 安徽马钢重型机械制造有限公司 一种冷轧卷取机芯轴空间位置尺寸在线检测方法
CN109051952B (zh) * 2018-10-19 2019-09-10 常州市新创智能科技有限公司 一种拉挤复合材料可调张力收卷装置及其使用方法
RU2735286C1 (ru) * 2020-02-27 2020-10-29 Акционерное общество "Пермский завод "Машиностроитель" Устройство для регулирования усилия прижима прикатного ролика к оправке
CN113695439B (zh) * 2021-10-28 2022-01-07 佛山市阿玛达机械科技有限公司 一种可以调节弯折角度的冷弯成型机及其工作方法

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US3028114A (en) * 1959-09-21 1962-04-03 Kloeckner Werke Ag Arrangement for coiling metal strip material
JPS579531A (en) * 1980-06-18 1982-01-19 Hitachi Ltd Wrapper roller control device for down coiler
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JPS5992118A (ja) * 1982-11-15 1984-05-28 Mitsubishi Heavy Ind Ltd 巻取装置のストリツプ先端回避制御装置
JPS59156514A (ja) * 1983-02-26 1984-09-05 Ishikawajima Harima Heavy Ind Co Ltd コイラにおけるラツパ−ロ−ル制御方法
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Also Published As

Publication number Publication date
ATE102092T1 (de) 1994-03-15
DE3689682D1 (de) 1994-04-07
SU1558292A3 (ru) 1990-04-15
KR870004742A (ko) 1987-06-01
EP0222231A2 (fr) 1987-05-20
JP2898282B2 (ja) 1999-05-31
CN86107620A (zh) 1987-05-20
US4736605A (en) 1988-04-12
EP0222231A3 (en) 1989-03-15
ES2050099T3 (es) 1994-05-16
KR930008913B1 (ko) 1993-09-17
DE3539900A1 (de) 1987-05-14
JPS62114723A (ja) 1987-05-26

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