EP0513954B1 - Procédé pour la compensation de moment de torsion à un dispositif d'entraînement d'un laminoir à pas de pèlerin - Google Patents

Procédé pour la compensation de moment de torsion à un dispositif d'entraînement d'un laminoir à pas de pèlerin Download PDF

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Publication number
EP0513954B1
EP0513954B1 EP92250121A EP92250121A EP0513954B1 EP 0513954 B1 EP0513954 B1 EP 0513954B1 EP 92250121 A EP92250121 A EP 92250121A EP 92250121 A EP92250121 A EP 92250121A EP 0513954 B1 EP0513954 B1 EP 0513954B1
Authority
EP
European Patent Office
Prior art keywords
crank
torque
speed
crank mechanism
drive
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
EP92250121A
Other languages
German (de)
English (en)
Other versions
EP0513954A2 (fr
EP0513954A3 (en
Inventor
Josef Gerretz
Michael Baensch
Klaus Rehag
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.)
Vodafone GmbH
Original Assignee
Mannesmann 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 Mannesmann AG filed Critical Mannesmann AG
Publication of EP0513954A2 publication Critical patent/EP0513954A2/fr
Publication of EP0513954A3 publication Critical patent/EP0513954A3/de
Application granted granted Critical
Publication of EP0513954B1 publication Critical patent/EP0513954B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
    • B21B35/12—Toothed-wheel gearings specially adapted for metal-rolling mills; Housings or mountings therefor
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B21/00—Pilgrim-step tube-rolling, i.e. pilger mills
    • B21B21/005—Pilgrim-step tube-rolling, i.e. pilger mills with reciprocating stand, e.g. driving the stand
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S388/00—Electricity: motor control systems
    • Y10S388/923—Specific feedback condition or device
    • Y10S388/93—Load or torque

Definitions

  • the invention relates to a method for torque compensation on the drive of a rolling stand of a vocational step rolling mill, which is linearly reciprocated via a crank drive, in particular a cold pilger rolling mill.
  • German patent DE-C-10 64 461 to supplement the crank mechanism that generates the movement of the roll stand with a similar crank mechanism that is operated out of phase by 90 degrees. In this way, there is a constant exchange of kinetic energy between the two crank mechanisms.
  • this method has the advantage that the crank speeds and the crank torque, and thus also the engine speed and engine torque, are almost constant over a movement cycle, it has the disadvantage that the mechanical engineering expenditure is very great. This also applies to the space requirement, because deep foundations are generally required. Finally, higher order inertial forces are difficult to balance.
  • Another way to solve the problem provides torque compensation by interposing unevenly geared gears. If you accelerate a crank drive that moves a roll stand to a certain speed and then decouple it from the drive, the speed of the crankshaft will change periodically. In the case of freedom from friction, this statement will apply for any length of time. If you now place an unevenly geared transmission between the drive and the crankshaft, which at the constant drive speed on the output side has exactly the speed curve that the crank drive in non-driven state, the crank mechanism can also be driven at a constant engine speed and constant engine torque. The intermediate gear must convert the constant speed into a variable speed, which corresponds to the free speed curve of the crank drive. Since the speed fluctuations of the crank mechanism depend on the respective speed, the transmission behavior of the intermediate gear must be variable.
  • An intermediate gear that is actually used for torque compensation is the universal joint, which can be adapted to the speed fluctuations by changing the articulation angle in the joint (DE-A-20 30 995).
  • the last-mentioned method also has the disadvantage that a great deal of design effort is required to enable the torque compensation to be set to a specific speed.
  • the engine returns to generator mode if the torque compensation is not automatically adjusted.
  • the influence of the load on the torque compensation cannot be taken into account.
  • the speed curve of the crank drive calculated from the kinematic dimensions, the moving masses and the external loads, is specified as the target speed curve for the drive motor.
  • the invention has recognized that an optimal torque compensation can be realized if the target speed of the motor does not become lower than the current actual speed. Generator operation is safely avoided if the target speed of the drive motor always corresponds to the speed to which it is being accelerated or decelerated by the load. To ensure this, it is necessary to know the speed curve that is set. This can be calculated precisely if the kinematic dimensions, the moving masses and the external loads are known. The calculated speed curve, which a friction-free crank drive would have in the state driven with constant torque, is given to the drive motor as the desired speed curve.
  • the invention means that acceleration or braking torques no longer have to be applied by the engine.
  • the engine In the stationary area, the engine only works against friction losses and external loads. If there is no external load, the engine only works against the almost constant friction losses, the engine torque is then approximately constant.
  • the proposed system is operated with a fast computer, which calculates the crank speed depending on the respective crank position and communicates it to the drive system.
  • Systems of this type which meet the necessary control speed and control accuracy are state of the art.
  • This reduced engine torque is only a calculation variable, it should not be confused with the actual engine torque.
  • the actual engine torque will differ from the " reduced engine torque" at least by the proportion for overcoming frictional losses.
  • the starting value ⁇ 0 on the basis of which the prediction of the angular velocity curve ⁇ ( ⁇ ) is based, must be determined iteratively. To do this, change ⁇ 0 until the condition With n is met with sufficient accuracy as the predetermined speed average.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
  • Control Of Metal Rolling (AREA)
  • Transmission Devices (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)

Claims (3)

  1. Procédé pour compenser le couple sur l'entraînement d'une cage de laminoir, pouvant se déplacer en va-et-vient de façon linéaire par l'intermédiaire d'un mécanisme à manivelle, d'un laminoir à pas de pèlerin, en particulier d'un laminoir à pas de pèlerin à froid,
    caractérisé en ce que la variation de la vitesse de rotation du mécanisme à manivelle, calculée à partir des dimensions cinématiques, des masses déplacées ainsi que des charges externes, est fournie au moteur d'entraînement comme variation de la vitesse de rotation de consigne.
  2. Procédé selon la revendication 1,
    caractérisé en ce que, pour calculer les valeurs de la vitesse de rotation de consigne, le moment d'inertie de masse réduit du mécanisme à manivelle, l'énergie potentielle du mécanisme à manivelle et la charge convertie en un couple réduit sur la manivelle en tant que fonction de l'angle de manivelle, sont entrés dans un calculateur rapide et, à partir de la vitesse angulaire de la manivelle dans une position déterminée de celle-ci, les vitesses angulaires pour les angles de manivelle restants sont calculées, le résultat, traité pour former la valeur de consigne de la vitesse de rotation respective, étant communiqué au moteur du dispositif d'entraînement.
  3. Procédé selon la revendication 1,
    caractérisé en ce que la valeur de départ de la vitesse angulaire de la manivelle est déterminée de façon itérative dans la position initiale de l'angle de manivelle.
EP92250121A 1991-05-15 1992-05-13 Procédé pour la compensation de moment de torsion à un dispositif d'entraînement d'un laminoir à pas de pèlerin Expired - Lifetime EP0513954B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4116307A DE4116307C1 (fr) 1991-05-15 1991-05-15
DE4116307 1991-05-15

Publications (3)

Publication Number Publication Date
EP0513954A2 EP0513954A2 (fr) 1992-11-19
EP0513954A3 EP0513954A3 (en) 1993-01-13
EP0513954B1 true EP0513954B1 (fr) 1995-02-22

Family

ID=6431946

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92250121A Expired - Lifetime EP0513954B1 (fr) 1991-05-15 1992-05-13 Procédé pour la compensation de moment de torsion à un dispositif d'entraînement d'un laminoir à pas de pèlerin

Country Status (6)

Country Link
US (1) US5291108A (fr)
EP (1) EP0513954B1 (fr)
JP (1) JPH05154511A (fr)
KR (1) KR920021231A (fr)
DE (2) DE4116307C1 (fr)
RU (1) RU2054339C1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5761945A (en) * 1993-10-18 1998-06-09 Vandenbroucke; Jack-Eric Quick automated tool changer roll forming apparatus
AT406233B (de) * 1995-07-31 2000-03-27 Gfm Gmbh Verfahren zum regeln des walzgutdurchlaufes durch eine kontinuierliche walzstrasse
DE102011004203A1 (de) * 2011-02-16 2012-08-16 Sandvik Materials Technology Deutschland Gmbh Vorrichtung mit einer Mehrzahl von Kaltwalzanlagen

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1263664B (de) * 1959-01-09 1968-03-21 Licentia Gmbh Abbremsvorrichtung fuer Umkehrwalzwerke
JPS4937910B1 (fr) * 1970-06-18 1974-10-14
DE2335138A1 (de) * 1973-07-06 1975-01-23 Mannesmann Meer Ag Kaltpilgerwalzwerk mit einem drehzahlveraenderlichem antriebsmotor
US4052898A (en) * 1976-09-13 1977-10-11 Wean United, Inc. Crank drive system for cold pilger mills drive or the like
US4037444A (en) * 1977-01-10 1977-07-26 Wean United, Inc. Shell feed system for a cold pilger mill
SU754360A1 (ru) * 1977-01-10 1980-08-07 Anatolij D Bratus Система управления 1
DE3010526A1 (de) * 1980-03-17 1981-09-24 Mannesmann AG, 4000 Düsseldorf Pilgerschrittwalzwerk
US4478119A (en) * 1981-05-11 1984-10-23 Bethlehem Steel Corporation Adaptive control for a dividing shear
DE3302222C1 (de) * 1983-01-24 1984-05-10 Siemens AG, 1000 Berlin und 8000 München Schaltungsanordnung fuer einen Walzenantriebsmotor eines Rohrwalzwerkes
US4562713A (en) * 1983-12-14 1986-01-07 Sumitomo Metal Industries, Ltd. Cold pilger mill
JPS62238005A (ja) * 1986-04-10 1987-10-19 Sumitomo Heavy Ind Ltd ピルガ−式圧延機の慣性力バランス装置
US5076088A (en) * 1986-04-15 1991-12-31 Mannesmann Ag Drive for a pilger cold rolling mill
DE3706129C1 (de) * 1987-02-23 1988-03-10 Mannesmann Ag Antrieb fuer ein Kaltpilgerwalzwerk mit Massen- und Momentenausgleich
JPS6315692A (ja) * 1986-07-07 1988-01-22 Hitachi Ltd 電動機の速度制御装置
DE58908949D1 (de) * 1989-09-27 1995-03-09 Siemens Ag Verfahren zur numerischen Positions- oder Bahnsteuerung.

Also Published As

Publication number Publication date
DE4116307C1 (fr) 1992-10-29
JPH05154511A (ja) 1993-06-22
EP0513954A2 (fr) 1992-11-19
EP0513954A3 (en) 1993-01-13
US5291108A (en) 1994-03-01
DE59201439D1 (de) 1995-03-30
RU2054339C1 (ru) 1996-02-20
KR920021231A (ko) 1992-12-18

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