EP2489445B1 - Dispositif doté d'une multitude d'installations de laminage à froid - Google Patents

Dispositif doté d'une multitude d'installations de laminage à froid Download PDF

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Publication number
EP2489445B1
EP2489445B1 EP12154869.7A EP12154869A EP2489445B1 EP 2489445 B1 EP2489445 B1 EP 2489445B1 EP 12154869 A EP12154869 A EP 12154869A EP 2489445 B1 EP2489445 B1 EP 2489445B1
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EP
European Patent Office
Prior art keywords
roll stand
electric motor
rolling
measuring signal
set forth
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.)
Not-in-force
Application number
EP12154869.7A
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German (de)
English (en)
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EP2489445A1 (fr
Inventor
Thomas FROBÖSE
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.)
Alleima GmbH
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Sandvik Materials Technology Deutschland GmbH
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Publication of EP2489445A1 publication Critical patent/EP2489445A1/fr
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    • 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
    • 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
    • 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
    • B21B37/78—Control of tube rolling

Definitions

  • the present invention relates to a device having a plurality of cold rolling mills, each having a rolling stand movable along a linear path with at least one roller rotatably mounted on the rolling stand, a drive connected to the rolling stand with an electric motor so arranged that the rolling stand is drivable in an oscillating movement along the linear path, and having a feed tension slide for advancing a blank.
  • the invention further relates to a method for controlling a device having a plurality of cold rolling mills, each having a rolling mill movable along a linear path with at least one roller rotatably mounted on the rolling stand, a drive connected to the rolling stand with an electric motor is arranged so that the rolling mill is drivable in an oscillating movement along the linear path, and having a feed tension slide for advancing a blank.
  • a corresponding device and a corresponding method according to the preambles of claims 1 and 10 are known from GB 1195140 known.
  • an extended hollow cylindrical blank is reduced by compressive stresses.
  • the blank is formed into a tube with a defined reduced outer diameter and a defined wall thickness.
  • the most common pipe reduction method is known as cold pilgering, the blank being called a billet.
  • the billet is in the fully cooled state during rolling over a calibrated, d. H. the inner diameter of the finished tube having, rolling mandrel pushed while calibrated from the outside of two, d. H. comprising the outer diameter of the finished tube defining rollers and rolled in the longitudinal direction over the rolling mandrel.
  • the billet progressively advances toward and over the mandrel while rotating the rolls horizontally over the mandrel and thus the billet.
  • the horizontal movement of the rollers is predetermined by a rolling stand on which the rollers are rotatably mounted.
  • the rollers are given their rotational movement by a toothed rack fixed relative to the roll stand, in which gear wheels fixedly connected to the roll axes engage.
  • the feeding of the billet over the mandrel is carried out by means of a feed clamping step, which translates a movement in one Direction parallel to the axis of the rolling mandrel allows.
  • the linear feed of the feed tension slide in the known cold pilger rolling mills is achieved by means of a ball screw or a linear motor.
  • the superimposed conically calibrated rollers in the rolling stand rotate counter to the feed direction of the feed tension slide.
  • the so-called Pilgrim mouth formed by the rollers captures the billet and the rollers press from the outside from a small material shaft, which is stretched by the smoothing caliber of the rollers and the mandrel to the intended wall thickness until the idling caliber of the rollers releases the finished tube.
  • the roll stand moves with the rolls attached thereto against the feed direction of the billet.
  • the billet is advanced by a further step onto the rolling mandrel, while the rolls with the rolling stand return to their horizontal starting position.
  • the billet undergoes a rotation about its axis to achieve a uniform shape of the finished tube in the circumferential direction.
  • crank mechanism conventionally consists of a transmission, a flywheel, a push rod and corresponding lubrication, wherein the crank mechanism is driven by an electric motor.
  • the electric motor is connected via a clutch to the transmission and via a further clutch to the flywheel.
  • At a first end of the push rod is connected by means of a bearing with the flywheel.
  • the bearing is arranged eccentrically to the axis of rotation of the flywheel.
  • the second end of the push rod is also connected by means of a bearing with the rolling stand, so that the rotational movement of the flywheel is converted into a translational movement of the rolling mill.
  • the translation direction of the roll stand is predetermined by guide rails and substantially parallel to the feed direction of the billet.
  • a typical rolling stand for a cold pilger rolling mill has a mass of about 150 tons that must be moved back and forth during operation of the cold pilger rolling mill. Due to the periodically repeating acceleration and deceleration of the mass of the rolling stand, the system transmits large forces in the form of oscillations on their base plate and through this further on the building in which the cold pilger rolling mill is located. This applies to a greater extent when in a single building, in particular a workshop, a plurality operated by cold pilger rolling mills at the same time, as is common in modern production plants. In the worst case, the forces transmitted to the building of the individual cold pilger rolling mills and the transmitted vibrations can lead to damage to the building itself or other machines arranged in the workshop.
  • a device is proposed according to the invention with a plurality of cold rolling plants, each of which is movable along a linear path rolling stand with at least one roller which is rotatably mounted on the rolling mill, connected to the rolling mill drive with an electric motor, the so arranged in that the rolling stand is drivable in an oscillating movement along the linear path, and having a feed slide for advancing a blank, the device having an electrical control with at least two control outputs, each control output being connected to the electric motor of the drive of a rolling mill and wherein the controller is arranged to operate the electric motors during operation of the apparatus to drive at least two of the stands with an adjustable phase shift between the oscillatory movements of the stands.
  • An adjustment of the phase shift between the rolling stands of two cold rolling plants makes it possible to reduce the forces and moments transmitted by the plants to the base plate or the building surrounding the rolling plants.
  • the pilger rolling mill is a cold pilger rolling mill.
  • phase shift between the oscillating movements of two rolling stands of the arrangement according to the invention is mentioned, then it is assumed that these perform the translational movements with the same frequency. Without phase shift, the rolling stands then move in common mode. Ie. they reach both their front and rear reversal points simultaneously.
  • a phase shift of 180 ° means that when one of the rolling stands reaches its front turning point, the other one is just reaching its rear turning point and vice versa.
  • the control is set up so that it controls the electric motors during operation of the arrangement in such a way that the oscillating movements the two rolling mills of the cold rolling mills have a phase shift to one another in a range of 75 ° to 105 °, but preferably of 90 °.
  • the preferred phase shift between the oscillating movements of the two rolling mills is in a range from 165 ° to 195 °, but preferably at 180 °.
  • the electric motor of the drive of the roll stand is an electromechanical linear motor.
  • the drive of the rolling stand comprises a flywheel on a drive shaft, which is rotatably mounted about a rotation axis, and a push rod with a first or second end, wherein the first end of the push rod at a radial distance from the axis of rotation on the flywheel is attached and wherein the second end of the push rod is attached to the rolling stand, so that during operation of the system, a rotational movement of the flywheel is converted in a translational movement of the rolling mill.
  • the electric motor has a motor shaft, wherein the motor shaft of the drive motor and the drive shaft are coupled together so that a rotational movement of the motor shaft leads to a rotational movement of the drive shaft and so the drive motor drives the flywheel.
  • the electric motor is a torque motor.
  • a torque motor has the advantage that it can drive the flywheel directly and makes the transmission, which is provided in the prior art between the electric motor and the flywheel, superfluous. Frictional losses and wear are reduced in this way. Furthermore, the number of mechanical components is significantly reduced, which among other things reduces the costs incurred by stocking spare parts costs. The downtime of the system due to possible repairs is limited.
  • a torque motor provides high torque at low speed and compact size.
  • the torque motor used here can be realized both as a synchronous and as an asynchronous motor.
  • such torque motors have the additional advantage that they are very precisely controlled, so that a phase shift between the movements of the rolling stands is precisely adjustable. In particular, eliminates the use of such a direct drive each clutch or transmission game.
  • the motor shaft and the drive shaft are interconnected so that a full revolution of the motor shaft causes a full revolution of the drive shaft.
  • a coupling can be done for example via a coupling between the motor shaft and the drive shaft of the flywheel.
  • the motor shaft and the shaft, which forms the axis of rotation of the flywheel are made in one piece.
  • the controller has a first signal input for a first measurement signal and a second signal input for a second measurement signal, wherein the controller is set so that during operation of the device, the phase shift between the oscillating movement of a first stand and the oscillating movement of a second rolling stand in response to the first measurement signal and the second measurement signal sets.
  • the first signal input receives a first measurement signal which is a measure of the instantaneous phase position of the oscillating motion of the first rolling mill
  • the second signal input receives a second measurement signal which is a measure of the instantaneous phase position of the oscillating one Movement of the second rolling stand
  • the controller is set so that it determines an actual value of the phase shift between the first and the second rolling mill in the operation of the device from the first measurement signal and the second measurement signal, the actual value of the phase shift with a compares the predetermined target value of the phase shift and controls the first electric motor and the second electric motor so that the deviation between the actual value of the phase shift and the desired value of the phase shift does not exceed a predetermined threshold value.
  • the control is now designed so that it calculates the phase difference between the rolling stands of two cold rolling plants from the detected torques and compares this instantaneous phase position as the actual value with a predetermined target value of the phase difference. If the actual value and setpoint value deviate more than a predetermined value from one another, then the controller changes the phase shift between the two considered rolling stands.
  • the instantaneous torque of two electric motors of the rolling stands of two cold rolling mills is detected. From the torque of the drive motor for the mill stand of a cold rolling mill can be the position of the mill along determine its path in the oscillating translation movement and thus the phase position of the oscillatory motion.
  • the speed of the rolling stand follows along the linear displacement in the oscillatory movement of the rolling stand in approximately a sinusoidal course, if one plots the current speed of the roll stand over time.
  • d. H At the front and at the rear end of the linear displacement, the speed is zero and reaches a maximum approximately in the middle of the path of translational movement of the rolling stand.
  • a correspondingly sinusoidal course has the idle from the moving mass of the rolling mill on the push rod transmitted to the electric motor torque. This is absorbed by the engine's bearings on the building or part and transmitted to the building.
  • this torque transmitted to the engine and thus the torque of the engine is maximum, while reaching a minimum between the turning points.
  • the controller is set up in such a way that it minimizes the moment transmitted overall by the two rolling stands considered to the building or a part thereof. Such minimization is achieved, in particular, when the two rolling mills have a phase shift of 90 ° to one another. With a phase shift of 0 °, the forces transmitted to the building or a part thereof in one direction are particularly large, while at a phase shift of 180 ° between the movements of two rolling stands at least in a part of the building particularly large shear forces occur.
  • the first signal input is connected to the first electric motor and during operation of the device, the first signal input receives a first measurement signal which is a measure of the instantaneous torque of the first electric motor
  • the second signal input is connected to the second electric motor and during operation of the device, the second signal input receives a second measurement signal which is a measure of the instantaneous torque of the second electric motor.
  • Such an embodiment has the advantage that it can do without an additional sensor for detecting the phase position of the rolling stands.
  • the first signal input is connected to a sensor for detecting the phase position of the first rolling stand
  • the second signal input is connected to a sensor for detecting the phase position of the second rolling stand.
  • Examples of such sensors are, for example, a torque sensor which detects the torque of the electric motor.
  • the senor may be an optical sensor that detects the position of the rolling stand. It is also possible to detect the phase position of the oscillating movement of a roll stand with a vibration sensor which is attached to the cold rolling mill, in particular to the roll stand.
  • At least one of the sensors is a sensor which detects the bearing forces of the electric motor.
  • All of these sensors are suitable for determining the current phase position of a rolling mill, so that the actual value of the phase difference between the rolling stands of the cold rolling mill can be determined from two measured values for two different rolling plants and compared with a predetermined target value of the phase shift.
  • the vibrations transmitted to the building housing the rolling mills or parts thereof are detected and the phase shift between the oscillating movements of two mills is set such that the transmitted vibrations are minimal ,
  • the controller has a signal input for a measurement signal, wherein the signal input with a vibration sensor for detecting the vibration transmitted from the plurality of cold rolling mills to a surrounding building or a part thereof, and wherein the controller is adapted to during operation of the device controls the electric motors of the cold rolling mill so that the vibrations transmitted to the building are minimal.
  • the above object is also achieved by a method of controlling a device having a plurality of cold rolling mills, each having a rolling stand movable along a linear path with at least one roller rotatably mounted on the rolling stand, a drive connected to the rolling stand with an electric motor adapted to drive the rolling mill in an oscillating motion along the linear path and having a feed chuck for advancing a blank, the method comprising the steps of: controlling the electric motor of a first mill drive and controlling the electric motor of one Drive for a second rolling stand, so that during operation of the device the oscillating movement of the first rolling stand and the oscillating movement of the second rolling stand have a selectable and adjustable phase shift.
  • the instantaneous phase positions of the oscillating movements of the first rolling stand and the second rolling stand are detected in a first embodiment and from these an actual value for the phase shift between the oscillating movements of the first and second second rolling mill determined. Subsequently, this actual value is compared with a predetermined setpoint value and the instantaneous phase shift is changed by driving the motors, if the deviation between the actual value and the setpoint value of the phase shift exceeds a predetermined threshold value.
  • the method according to the invention additionally comprises the steps of detecting a first measuring signal, detecting a second measuring signal and adjusting the phase shift of the oscillating movements of the first and second rolling stands as a function of the first and second measuring signals.
  • the first measurement signal is a measure of the instantaneous phase position of the oscillating motion of the first rolling stand
  • the second measurement signal is a measure of the instantaneous phase position of the oscillating motion of the second rolling stand
  • the method further comprising the steps of: determining a Actual value of the phase shift in the oscillating movements of the first rolling mill and the second rolling mill of the first measurement signal and the second measurement signal, comparing the actual value of the phase shift with a predetermined target value of the phase shift and controlling the first and second electric motors, so that a deviation between actual value and desired value of the phase shift does not exceed a predetermined threshold value.
  • the first measurement signal is a measure of the instantaneous torque of the first electric motor and the second measurement signal is a measure of the instantaneous torque of the second electric motor.
  • the instantaneous phase position of the oscillating movement of each cold rolling mill is not detected, but the vibrations transmitted overall by the plurality of cold rolling plants to the surrounding building or a part thereof are detected and adjusted by adjusting the phase difference between the oscillating movements of the Rolling mills of the individual cold rolling mills minimized.
  • FIG. 1 schematically the construction of a cold pilger rolling mill in a side view, as provided in a plurality in the inventive arrangement is shown.
  • the rolling mill consists of a rolling stand 1 with rollers 2, 3, a calibrated rolling mandrel 4 and a drive for the roll stand 1.
  • the drive for the roll stand 1 has a push rod 6, a drive motor 9 and a flywheel 10.
  • a first end 16 of the push rod 6 is mounted eccentrically to the axis of rotation 18 of the drive shaft 8 on the flywheel 10.
  • the axis of rotation of the motor shaft coincides with the axis of rotation 18 of the drive shaft 8 of the flywheel 10.
  • the rolling mill 11 undergoes a step-by-step advance in the direction of the rolling mandrel 4 toward or beyond it, while the rolls 2, 3 are rotationally reciprocated horizontally over the mandrel and thus over the billet 11.
  • the horizontal movement of the rollers 2, 3 of the roll stand 1 is predetermined, by the rollers 2, 3 are rotatably mounted.
  • the rolling stand 1 is reciprocated in a direction parallel to the rolling mandrel 4, while the rollers 2, 3 themselves receive their rotary motion through a rack fixed relative to the rolling stand 1, in which gears fixedly connected to the rollers engage.
  • the feed of the billet 11 over the mandrel 4 is effected by means of a feed tension slide 5, which allows a translational movement in a direction parallel to the axis of the rolling mandrel 4.
  • the superimposed in the roll stand 1 conically calibrated rollers 2, 3 rotate counter to the feed direction of the feed tension slide 5.
  • the so-called vocational mouth formed by the rollers 2, 3 detects the billet 11 and the rollers 2, 3 press from the outside a small material shaft from is extended from a smoothing caliber of the rollers 2, 3 and the rolling mandrel 4 to the intended wall thickness until an idling caliber of the rollers 2, 3 releases the finished tube.
  • the roll stand 1 moves with rollers 2, 3 attached thereto against the feed direction of the billet 11.
  • the billet With the aid of the feed tension slide 5, the billet is advanced after reaching the idling caliber of the rolls 2, 3 by a further step on the rolling mandrel 4 , while the rollers 2, 3 return to the rolling mill 1 in its horizontal starting position. At the same time, the billet 11 undergoes a rotation about its axis to achieve a uniform shape of the finished pipe.
  • a uniform wall thickness and roundness of the tube and uniform inner and outer diameter can be achieved.
  • the large mass of the rolling stand 1 is reciprocated at a high frequency.
  • the rolling stand has a mass of about 10 tons, while the direct drive acting on the flywheel with a torque motor generates 280 revolutions per minute.
  • the large mass of the roll stand 1 must be completely decelerated at the reversal points of its translation path and then accelerated again in the opposite direction. The forces occurring are exclusively absorbed by the electric motor 9 and from this via its storage points in a surrounding the cold pilger rolling mill building or part thereof, in the illustrated embodiment, the base plate of the cold pilger rolling plants, initiated.
  • the drive motors of the rolling mills are coupled to each other via an electronic shaft.
  • each of the cold pilger rolling mill 20, 21 has a structure as shown schematically in FIG FIG. 1 is shown.
  • the drive of each roll stand 1 consists of a connected at one end 17 to the roll stand 1 push rod 6, connected to the other end 16 of the push rod 6 crank mechanism 10 with a balancing mass 12 and a directly connected to the axis of the crank mechanism electric motor.
  • FIG. 2 schematically illustrated electric motors 9 for driving the crank mechanisms 10 and thus the rolling stands 1 are coupled to each other via an electronic shaft 23.
  • FIG. 3 shows a schematic view of a first embodiment of the "electronic shaft” 23 from FIG. 2 .
  • Essential element of the electronic shaft 23 is an electrical control 50 with two control outputs 51, 52, wherein the first control output 51 is connected to the electric motor 9 of the first cold pilger rolling mill 20 and the second control output 52 to the electric motor 9 of the second cold pilger rolling mill 21.
  • the controller 50 is set up so that it operates both electric motors 9 of the cold pilger rolling mills 21, 22 at the same angular frequency during operation of the plant, so that the rolling mills perform an oscillating translational movement also with the same frequency.
  • the controller 50 operates the two motors 9 so that the rolling stands have a phase shift of 90 °. Ie. While the rolling stand of the first rolling mill 20 just reached a reversal point of its translational movement, the rolling stand of the second cold pilger rolling mill 21 is just between the two reversal points of its translational movement, d. H. it moves at maximum speed.
  • the two rolling plants 20, 21 run in master-slave operation, wherein the first rolling mill 20 represents the master and the second rolling mill 21, the slave.
  • the electric motor 9 is operated to drive the rolling mill of the first rolling mill 20 with a constant frequency and phase, while the phase angle of the electric motor 9 of the second rolling mill 21 is controlled so that the phase difference between the oscillating movements of the rolling stands of the two rolling plants 20, 21 always exactly 90 °.
  • the controller 50 is provided with two signal inputs 53, 54. These signal inputs 53, 54 serve to detect the actual value of the phase positions of the oscillating movements of the rolling stands of each rolling mill 20, 21.
  • the signal input 53 to the motor 9 of the first rolling mill and the second signal input 54 to the motor 9 of the second rolling mill connected.
  • the instantaneous torque which the motor 9 applies for driving the roll stand of the rolling mill 20, 21 serves as the measuring signal. This is a direct measure of the instantaneous phase position of the oscillating translational movement of the roll stand.
  • the instantaneous torque of each electric motor 9 of the two rolling plants 20, 21, when plotted over time follows a sinusoidal course with maximum torques contemporaneous with the reversal of the direction of movement of the rolling stands.
  • the torque at idle (ie, without a pitch) of the electric motors 9 is twice the frequency modulated as the oscillation of the rolling stands themselves. Due to the doubling of the frequency of oscillation of the torque compared to the time compared to the oscillation frequency of the rolling stands corresponds to a phase shift of 90 ° for the Oszillationsterrorismen the rolling stands of a phase shift of 180 ° for the torques.
  • the phase shift of the oscillating movements of the rolling stands of the two rolling mills 20, 21 can be calculated. If this instantaneous actual value of the phase shift is not equal to a predetermined desired value, in the present case 90 °, then the controller 50 controls the electric motor 9 of the slave system 21 so that the desired value of 90 ° is reached again. For this purpose, the rotational frequency of the motor 9 of the slave system 21 is briefly varied.
  • FIG. 4 An alternative embodiment of the electronic shaft 23 from FIG. 2 is in FIG. 4 shown.
  • the central element of the electronic shaft 23 is a controller 50. As previously, it is connected via two control outputs 51, 52 to the electric motors 9 of the rolling stand drives of the rolling mills 20, 21.
  • the controller 50 in the embodiment FIG. 4 only an additional signal input 55 for a measurement signal.
  • This signal input 55 is connected to a vibration sensor 56.
  • This vibration sensor 56 is attached to the foundation 22 of the two rolling mills 20, 21 and detects all the vibrations which are transmitted from the two rolling mills 20, 21 to the foundation 22 and thus possibly also to other parts of the building surrounding the rolling mills 20, 21.
  • the controller 50 is configured to control the phase shift between the oscillatory motions of the two rolling stands of the two rolling mills 20, 21 so as to minimize the vibrations sensed by the sensor 56 and introduced into the foundation 22. For this purpose, with the same rotational frequency of the motors 9 of the two rolling plants 20, 21 whose phase shift is varied until the vibrations in the foundation are minimal. Also in the embodiment FIG. 4 In an optional embodiment, the controller 50 may have the signal inputs 51, 52 which are connected to the electric motors 9 of the rolling mills 20, 21, so that a detection of the actual value of the phase shift between the two oscillating movements of the rolling mills of the two rolling mills in addition is possible.

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Claims (14)

  1. Dispositif comprenant
    une pluralité d'installations de laminage à froid qui présentent chacune une cage de laminoir (1) pouvant se déplacer le long d'un trajet linéaire et possédant au moins un cylindre qui est fixé à la cage de laminoir (1) de façon rotative,
    un entraînement doté d'un moteur électrique (9), relié à la cage de laminoir (1), qui est agencé de manière que la cage de laminoir (1) puisse être entrainée en un mouvement oscillant le long du trajet linéaire, et
    un chariot d'avance à serrage servant à faire avancer une ébauche,
    caractérisé en ce que
    le dispositif présente une commande électrique (50) possédant au moins deux sorties de commande (51, 52), chaque sortie de commande étant connectée au moteur électrique (9) de l'entraînement d'une cage de laminoir (1) et la commande (50) étant agencée de manière à commander les moteurs électriques (9) de manière qu'ils entraînent au moins deux des cages de laminoir (1) avec un déphasage réglable entre les mouvements oscillants des cages de laminoir (1) dans le fonctionnement du dispositif.
  2. Dispositif selon la revendication 1, caractérisé en ce que la commande (50) présente une première entrée de signal pour un premier signal de mesure et une seconde entrée de signal pour un second signal de mesure, la commande (50) étant agencée de manière à régler le déphasage entre le mouvement oscillant d'une première cage de laminoir (1) et le mouvement oscillant d'une seconde cage de laminoir (1) en fonction du premier signal de mesure et du second signal de mesure dans le fonctionnement du dispositif.
  3. Dispositif selon la revendication 2, caractérisé en ce que, dans le fonctionnement du dispositif, la première entrée de signal reçoit un premier signal de mesure qui est une mesure de la position de phase instantanée du mouvement oscillant de la première cage de laminoir (1) et la seconde entrée de signal reçoit un second signal de mesure qui est une mesure de la position de phase instantanée du mouvement oscillant de la seconde cage de laminoir (1), la commande (50) étant agencée de manière que, dans le fonctionnement du dispositif, elle détermine, d'après le premier signal de mesure et le second signal de mesure, une valeur réelle du déphasage entre la première et la seconde cage de laminoir (1), compare la valeur réelle du déphasage à une valeur de consigne du déphasage prédéterminée et commande le premier moteur électrique (9) et le second moteur électrique (9) de manière que l'écart entre la valeur réelle du déphasage et la valeur de consigne du déphasage n'excède pas une valeur seuil prédéterminée.
  4. Dispositif selon la revendication 3, caractérisé en ce que la première entrée de signal est connectée au premier moteur électrique (9) et, dans le fonctionnement du dispositif, la première entrée de signal reçoit un premier signal de mesure qui est une mesure du couple instantané du premier moteur électrique (9), la seconde entrée de signal est connectée au second moteur électrique (9) et, dans le fonctionnement du dispositif, la seconde entrée de signal reçoit un second signal de mesure qui est une mesure du couple instantané du second moteur électrique (9).
  5. Dispositif selon la revendication 3, caractérisé en ce que la première entrée de signal est connectée à un capteur servant à détecter la position de phase de la première cage de laminoir (1) et la seconde entrée de signal est connectée à un capteur servant à détecter la position de phase de la seconde cage de laminoir (1).
  6. Dispositif selon la revendication 5, caractérisé en ce qu'au moins un des capteurs est un capteur de couple qui détecte le couple du moteur électrique (9).
  7. Dispositif selon la revendication 5 ou 6, caractérisé en ce qu'au moins un des capteurs est un capteur optique qui détecte la position de la cage de laminoir (1).
  8. Dispositif selon l'une des revendications 5 à 7, caractérisé en ce qu'au moins un des capteurs est un capteur de vibrations (56) monté sur l'installation de laminage à froid (20, 21).
  9. Dispositif selon l'une des revendications 1 à 8, caractérisé en ce que la commande (50) présente une entrée de signal pour un signal de mesure, l'entrée de signal étant connectée à un capteur de vibrations (56) servant à détecter les vibrations transmises par la pluralité d'installations de laminage à froid (20, 21) à un bâtiment qui les entoure ou à une partie de ce bâtiment, et la commande (50) étant agencée de manière à commander les moteurs électriques (9) des installations de laminage à froid (20, 21) dans le fonctionnement du dispositif de manière que les vibrations transmises au bâtiment soient minimes.
  10. Procédé pour commander un dispositif comportant une pluralité d'installations de laminage à froid (20, 21) qui présentent chacune une cage de laminoir (1) pouvant se déplacer le long d'un trajet linéaire et possédant au moins un cylindre qui est fixé à la cage de laminoir (1) de façon rotative, un entraînement doté d'un moteur électrique (9), relié à la cage de laminoir (1), qui est agencé de manière que la cage de laminoir (1) puisse être entraînée en un mouvement oscillant le long du trajet linéaire, et un chariot d'avance à serrage servant à faire avancer une ébauche,
    caractérisé en ce qu'il est comprend les étapes suivantes :
    commande du moteur électrique (9) d'un entraînement d'une première cage de laminoir (1) et commande du moteur électrique (9) d'un entraînement d'une seconde cage de laminoir (1) de manière que, dans le fonctionnement du dispositif, le mouvement oscillant de la première cage de laminoir (1) et le mouvement oscillant de la seconde cage de laminoir (1) présentent un déphasage réglable.
  11. Procédé selon la revendication 10, caractérisé en ce qu'il comprend en outre les étapes suivantes :
    détection d'un premier signal de mesure,
    détection d'un second signal de mesure, et
    réglage du déphasage des mouvements oscillants de la première et de la seconde cage de laminoir (1) en fonction du premier et du second signal de mesure.
  12. Procédé selon la revendication 11, caractérisé en ce que le premier signal de mesure est une mesure de la position de phase instantanée du mouvement oscillant de la première cage de laminoir (1) et le second signal de mesure est une mesure de la position de phase instantanée du mouvement oscillant de la seconde cage de laminoir (1), et comprenant en outre les étapes suivantes :
    détermination d'une valeur réelle du déphasage entre les mouvements oscillants de la première et de la seconde cage de laminoir (1) d'après le premier signal de mesure et le second signal de mesure,
    comparaison de la valeur réelle du déphasage à une valeur de consigne du déphasage prédéterminée,
    commande du premier et du second moteur électrique (9) de manière que l'écart entre la valeur réelle et la valeur de consigne du déphasage n'excède pas une valeur seuil prédéterminée.
  13. Procédé selon la revendication 12, caractérisé en ce que le premier signal de mesure est une mesure du couple instantané du premier moteur électrique (9) et le second signal de mesure est une mesure du couple instantané du second moteur électrique (9).
  14. Procédé selon l'une des revendications 10 à 13, caractérisé en ce qu'il comprend en outre les étapes suivantes :
    détection d'un signal de mesure qui est une mesure des vibrations transmises par la pluralité d'installations de laminage à froid (20, 21) à un bâtiment qui les entoure ou à une partie de ce bâtiment,
    commande du premier et du second moteur électrique (9) de manière qu'à une même fréquence de rotation du premier moteur électrique (9) et du second moteur électrique (9), les vibrations transmises au bâtiment soient minimes.
EP12154869.7A 2011-02-16 2012-02-10 Dispositif doté d'une multitude d'installations de laminage à froid Not-in-force EP2489445B1 (fr)

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DE102011004203A DE102011004203A1 (de) 2011-02-16 2011-02-16 Vorrichtung mit einer Mehrzahl von Kaltwalzanlagen

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EP2489445B1 true EP2489445B1 (fr) 2014-04-02

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DE102013112371A1 (de) * 2013-11-11 2015-05-13 Sandvik Materials Technology Deutschland Gmbh Kaltpilgerwalzanlage sowie Verfahren zum Umformen einer Luppe zu einem Rohr
CN112222191B (zh) * 2020-09-19 2022-09-23 太原科技大学 一种难变形金属无缝管材六辊冷轧机

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EP2489445A1 (fr) 2012-08-22
US9649677B2 (en) 2017-05-16
US20120234072A1 (en) 2012-09-20
DE102011004203A1 (de) 2012-08-16

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