EP1457274A2 - Verfahren und Vorrichtung zur Vermeidung von Schwingungen - Google Patents
Verfahren und Vorrichtung zur Vermeidung von Schwingungen Download PDFInfo
- Publication number
- EP1457274A2 EP1457274A2 EP04003584A EP04003584A EP1457274A2 EP 1457274 A2 EP1457274 A2 EP 1457274A2 EP 04003584 A EP04003584 A EP 04003584A EP 04003584 A EP04003584 A EP 04003584A EP 1457274 A2 EP1457274 A2 EP 1457274A2
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- EP
- European Patent Office
- Prior art keywords
- roller
- rolling
- vibrations
- roll
- actuator
- 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.)
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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
- B21B37/007—Control for preventing or reducing vibration, chatter or chatter marks
Definitions
- the invention relates to a method and a device for avoiding Vibrations, especially 3rd and 5th octave vibrations, in a rolling mill at least one roll stand with roll adjustment and at least one roll set.
- Both types of vibration have in common that there are movements of the roller set and thus there is a deviation from the target roll gap.
- the defects on the rolling stock show different degrees of surface defects, as geometrical defects or as combinations thereof.
- Monitoring systems are known from the prior art. Watch these systems or measure the vibration condition of the rolling mill or the rolling stands and reduce the rolling speed in the event of vibrations, in order to reduce vibrations and avoid instabilities.
- a disadvantage of Procedures that use monitoring systems is a significant drop in productivity, due to a reduction in the rolling speed.
- Rolling mills with passive vibration damping systems are also known.
- the energy of an occurring vibration is reduced and by means of dampers so the risk of damage is reduced.
- these systems can have surface defects insufficiently avoid the rolling stock, so that the task of a faultless Generate rolling stock so that it is not solved.
- US 5,724,846 describes a method for combating vibrations (octave vibrations) in a rolling mill for rolling strip.
- the Rolling system imprinted a vibration component that is relative to an existing one Vibration is asynchronous to vertical vibrations of the rollers avoid.
- the solution described always goes from an existing one Vibration, which is used as the basis for the countermeasure. at This solution is not sufficient for rolling mills, because of changing operating conditions despite the countermeasure, defects still occur on the rolled strip can.
- resonating vibrations that are characterized by a negative Damping can be characterized by that described in US Pat. No. 5,724,846 Invention no solution can be found.
- a device can be found in US Pat. No. 6,387,214 B1 measured vibration by means of an actuator the vibration state of a roller being affected. The solution only offers an indication of how the vibrations be reduced, but not how they can be avoided. In the case of unstable No solution is offered to vibration conditions.
- the object is according to the inventive method according to the characterizing Part of claim 1 solved.
- the method according to the invention is the generation of vibrations that lead to malfunctions of the rolling operation or Defects in the rolling stock can be avoided and a vibration and trouble-free Operation ensured.
- a controller, a mathematical control law and submodels the Parts of the system describe, includes, is supplied, the determination is made at least one temporally variable manipulated variable in real time, the manipulated variable being Input signal for at least one actuator to act on at least one Roll of the roll set of a roll stand and / or the rolling stock is used.
- the system behavior is determined by a mathematical Description, all relevant physical influences and relationships and the material behavior of system components and rolling stock taken into account, by linear or non-linear or from combinations of linear and non-linear sub-models are described, creating one for the controlled system sufficiently accurate simulation is achieved.
- the controller takes into account the essential system nonlinearities, such as. the rolling force model, actuator etc., the energy required for Raising of the vibration leads, withdrawn or it is achieved that in the system Rolling mill stored energy takes a minimum.
- the math Control law is based on linear and / or non-linear equations and / or Differential equations and / or differential equations the manipulated variable (s) as Function of the measured variable (s) determined. A control scheme for this is shown in FIG. 1.
- the sub-models include the modules and the system behavior a hydraulic and / or a mechanical and / or a rolling force model. through of the sub-models, the rolling mill is adequately described and in the regulatory law mapped, in addition to the behavior of the system parts and the system load the behavior of the entire rolling mill is mapped with high accuracy.
- a continuous supply of the size to the controller and the determination of at least one time-variable manipulated variable in real time becomes a permanent monitoring and a permanent intervention in the plant behavior reached. Due to the application of the system via at least one Actuator, energy is continuously withdrawn from the oscillatory system, so that the formation or generation of octave vibrations is reliably prevented.
- the measured size is used as an indicator of the system condition and kept at defined values.
- the vertical is measured Acceleration of the roller set used.
- the vertical acceleration has turned out to be a good indicator of the vibration condition in the roll stand, because thereby information about the current movement situation of the rollers and thus the Load roll gap is given.
- the operating status can be determined using a simple measurement installation be recorded precisely and inexpensively.
- Another simple embodiment of the invention sees the measured variable as Use the cylinder pressure of the roller adjustment before.
- the current operating state is very good via the cylinder pressures, for example the positioning cylinder, shown, so that an exact Prediction of the system behavior and avoidance of a control intervention Octave vibrations are possible.
- the measured variable is vertical position of the piston of the roller adjustment. Because the vertical Position of the roller set or the rollers of the roller set the load roll gap define, is the vibration behavior from deviations from a position easily derivable.
- Another embodiment is through the use of the tension condition achieved in the rolling stock as the measured size.
- this also Coupling the stands of the rolling mill over the rolling stock and the overlapping ones Vibrations shown in the rolling stands.
- the Acting on the roller of the roller set in the or the directions of the Roll set we have a targeted influence the vibration behavior and thus the load roll gap reached. It is advantageous also the possibility to use the existing employment in the respective scaffolding, additional units can thus be avoided.
- the admission provides a particularly advantageous embodiment of the method at least one roller before the adjusting device of the roller set. by virtue of this feature is avoided by coupling employment and intervention of vibrations in a superimposed process a very simple and inexpensive Solution found.
- FIG Actuation of the roller via the axial roller displacement device of the roller set in front Another possible embodiment of the method according to the invention is seen in FIG Actuation of the roller via the axial roller displacement device of the roller set in front.
- the method according to the invention provides for the avoidance of 3rd and 5th octave vibrations through a permanent reduction in vibrational energy, i.e. one Continuous energy dissipation from the vibrating mill stand system, especially the roller set. Due to the continuous energy dissipation ensures that there are no oscillations or vibrations, especially those train with high energy content, which leads to significant system damage or too Errors in the rolling stock.
- a particular embodiment sees the reduction of vibrations in particular in the direction of the rollers. This simplified solution leaves vibrations with a direction other than the direction of attack. This will make it easy Solution for the procedure found that meets the requirement for safe avoidance 3rd and 5th octave vibrations.
- the device according to the invention for avoiding vibrations, e.g. Third and 5th octave vibrations, in a rolling mill with at least one rolling stand with roller adjustment and at least one roller set comprises at least one Measuring device for the permanent measurement of a size of the rolling mill, one Controller that characterizes a mathematical control law and the state of the system Includes sub-models to which the measured size can be supplied, with the help this controller can determine at least one time-variable manipulated variable in real time is, and furthermore at least one actuator to which the manipulated variable can be fed and via the at least one of the rolls of the roll set and / or the rolling stock can be acted upon.
- a Controller that characterizes a mathematical control law and the state of the system Includes sub-models to which the measured size can be supplied, with the help this controller can determine at least one time-variable manipulated variable in real time is, and furthermore at least one actuator to which the manipulated variable can be fed and via the at least one of the rolls of the roll set and
- a hydraulic is used as the actuator Control element used. Due to the combination with existing in scaffolding, other hydraulic actuators, e.g. the hydraulic roller adjustment or the axial roller displacement becomes a robust and safe solution with high Flexibility achieved regardless of the system type.
- a further special embodiment sees a piezoelectric actuating element as Actuator that is characterized by high dynamics and high energy density distinguished, so that a very high precision is achieved in the control intervention.
- the Actuator is installed in the rolling mill in such a way that it is dynamic, not but static loads can act on the piezoelectric actuator. This ensures that overloads do not damage the piezo-electric actuator being able to lead.
- the combination makes a particularly advantageous embodiment of the device achieved by different actuators because of the different Characteristics of the actuators partial frequencies are very well covered can.
- Oscillations or vibrations represent a disruptive effect for rolling processes that appears as a defect in the rolling stock. Usually surface defects occur in particular and thickness deviations on the rolling stock.
- Deviations from the target thickness of the rolling stock cause great costs because they are always a minimum thickness must be guaranteed by the manufacturer. All positive thickness deviations that is, thicknesses greater than the guaranteed minimum thickness a very significant cost factor as this affects the total production quantity of the rolling mill must be moved. A reduction in thickness deviations, tighter thickness tolerances means a lot for the mill operator high savings potential. For many processing steps cause too large thickness deviations on the rolling stock, especially when forming, do not acceptable disturbances, so that larger thickness deviations an elimination of the Make rolling good necessary. This leads to very high reject costs.
- Rolling processes for the production of rolling stock is in addition to avoiding damage an overall more stable rolling process on the system and defects on the rolling stock reached. This allows tighter thickness tolerances on the rolling stock to be maintained and failures can be avoided by surface defects. Thickness tolerance is understood those rolling stock thicknesses that are a permissible deviation from a target thickness represent, i.e. do not exceed certain predefined deviations.
- usual Information is given as a percentage of the rolling stock thickness or in absolute terms of the permissible deviations in ⁇ amount from the nominal thickness, the information being frequent in ⁇ m.
- Tab. 1 shows typical thickness tolerances of a tandem cold rolling mill. These thickness tolerances apply to strip-shaped rolling stock with the exception of short sections at the strip head and at the strip foot, whereby the lengths of these sections are defined by guarantee formulations that take into account the specific characteristics of a system and can therefore vary.
- Figure 1 shows the basic structure of the controlled system, but not here Controller mathematics or the sub-models is discussed.
- Sizes 2 are measured using sensors or the sensors 1 required for this Rolling system recorded. These measured variables 2 are fed to a controller 3.
- the Controller 3 contains a mathematical control law and the system status characterizing sub-models. With the help of the controller 3 is at least in real time a time-variable manipulated variable 4 is determined and fed to the actuator system 5.
- the actuator system 5 is applied to the rolling system (section) 6, whereby the vibration state of the rolling mill 6 is influenced in a targeted manner.
- acting Disturbance variables 7 are taken into account via the measured variables 2.
- Fig. 2 is a frame of a rolling mill 6 with the schematically indicated main components shown. Via a controller 3 and a servo valve 12 an actuator 5, indicated here as a hydraulic cylinder, is acted upon. So that is done in addition to the positioning movement also the application to avoid Vibrations. Signals of a path or Position measurement 9, a pressure measurement 10 or an acceleration measurement 11 indicated with an accelerometer 13. In addition, you can Input variables that affect the rolling stock, e.g. Stress conditions in the rolling stock 14.15 or combinations of these sizes are used. to Determination of the stress conditions in the rolling stock can e.g. not shown here Measuring devices that measure touching the rolling stock are used. Actuators for application e.g. of the hydraulic cylinder are not closer here shown, their corresponding arrangement represents for the expert due to his Knowing, however, is not a problem. In a possible embodiment, as here shown, the hydraulic cylinder for roller adjustment is also used Avoidance of vibrations.
- the hydraulic cylinder for roller adjustment is also used Avoidance of vibration
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Control Of Metal Rolling (AREA)
- Processing And Handling Of Plastics And Other Materials For Molding In General (AREA)
- Vibration Prevention Devices (AREA)
- Lift-Guide Devices, And Elevator Ropes And Cables (AREA)
- Diaphragms For Electromechanical Transducers (AREA)
Abstract
Description
- Kailath T.: "Linear Systems", Prentice Hall, 1980.
- Franklin G., Powell D., Emami-Naeini A.: "Feedback Control of Dynamic Systems", Fourth Edition, Prentice Hall, 2002.
- Vidyasagar M.: "Nonlinear Systems Analysis", Second Edition, Prentice Hall, 1993.
- Kugi A.: "Nonlinear Control Based on Physical Models", Lecture Notes in Control and Information Sciences 260, Springer, 2000.
- Merritt H. E.: "Hydraulic Control Systems", John Wiley & Sons 1967.
- Kugi A., Schlacher K., Keintzel G.: "Position Control and Active Eccentricity compensation in Rolling Mills", at - Automatisierungstechnik S. 342-349, Oldenbourg, 1999.
- Grabmair G., Schlacher K., Kugi A.: "Coupling effects in multi stand rolling mills", Metal Forming 2000, pp. 295-301, 2000.
- Bland D., Ford H., Ellis F.: "Cold rolling with strip tension", Part I, Journal of the Iron and Steel Institute, pp. 57-72, 1951.
- Bland D., Ford H., Ellis F.: "Cold rolling with strip tension", Part II, Journal of the Iron and Steel Institute, pp. 239-245, 1952.
- Bland D., Ford H.: "Cold rolling with strip tension", Part III, Journal of the Iron and Steel Institute, pp. 245-249, 1952.
- Jortner D., Osterle J., Zorowski C.: "An analysis of cold strip rolling", Int. J. Mech. Sci., Vol.2, pp. 179-194, 1960.
Banddicke | Toleranz |
0,25 - 0,50 mm | ± 1,2 % |
0,50 - 0,89 mm | ± 1,0 % |
0,89 - 1,60 mm | ± 0,9 % |
1,60 - 2,54 mm | ± 0,8 % |
Claims (19)
- Verfahren zur Vermeidung von Schwingungen, insbesondere 3. und 5. Oktav-Schwingungen, in einer Walzanlage mit zumindest einem Walzgerüst mit Walzenanstellung und zumindest einem Walzensatz, dadurch gekennzeichnet, dass wenigstens eine permanent gemessene Größe der Walzanlage einem Regler (3), der ein mathematisches Regelgesetz und den Anlagenzustand charakterisierende Teilmodelle umfasst, zugeführt, mit Hilfe dieses Reglers (3) in Echtzeit zumindest eine zeitlich veränderliche Stellgröße (4) ermittelt, zumindest einem Aktuator (5) zugeführt und durch den Aktuator (5) mindestens eine der Walzen des Walzensatzes und/ oder das Walzgut beaufschlagt wird, wobei die Regelgrößen bei definierten Sollwerten gehalten werden.
- Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass lineare und/ oder nichtlineare Teilmodelle Einsatz finden.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Teilmodelle ein hydraulisches Modell und/ oder ein mechanisches Modell und/ oder ein Walzkraftmodell umfassen.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass als gemessene Größe die vertikale Beschleunigung des Walzensatzes herangezogen wird.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass als gemessene Größe der Zylinderdruck der Walzenanstellung herangezogen wird.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass als gemessene Größe die Kolbenposition der Walzenanstellung herangezogen wird.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass als gemessene Größe der Zugspannungszustand im Walzgut herangezogen wird.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass als gemessene Größen Kombinationen der vertikalen Beschleunigung und/ oder des Zylinderdrucks der Walzenanstellung und/ oder der vertikalen Position des Walzensatzes und/ oder des Zugspannungszustands herangezogen werden.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Beaufschlagung der Walze des Walzensatzes in Anstellrichtung erfolgt.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Beaufschlagung der Walze des Walzensatzes in mehreren Richtungen erfolgt.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Beaufschlagung der Walze über die Anstellvorrichtung des Walzensatzes erfolgt.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Beaufschlagung der Walze über eine axiale Walzenverschiebevorrichtung des Walzensatzes erfolgt.
- Verfahren nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass durch die Beaufschlagung der Walze der Energieinhalt von Schwingungen in Anstellrichtung reduziert und/ oder eliminiert wird.
- Vorrichtung zur Vermeidung von Schwingungen, insbesondere 3. und 5. Oktav-Schwingungen, in einer Walzanlage mit zumindest einem Walzgerüst mit Walzenanstellung und zumindest einem Walzensatz zur Durchführung des Verfahrens nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass wenigstens eine Messeinrichtung (9,10,11), zum permanenten Messen einer Größe der Walzanlage, und ein Regler (3), der ein mathematisches Regelgesetz und den Anlagenzustand charakterisierende Teilmodelle umfasst, dem die gemessene Größe (2) zuführbar ist, vorgesehen sind und mit Hilfe dieses Reglers (3) in Echtzeit zumindest eine zeitlich veränderliche Stellgröße (4) ermittelbar ist, und weiters zumindest einen Aktuator (5) umfasst, dem die Stellgröße (4) zuführbar ist und über den mindestens eine der Walzen des Walzensatzes und/ oder das Walzgut beaufschlagbar ist/ sind.
- Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, dass der Aktuator (5) als hydraulisches und/ oder servo-hydraulisches Stellelement ausgebildet ist.
- Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, dass der Aktuator als piezo-elektrisches Stellelement ausgebildet ist.
- Vorrichtung nach Anspruch 14 bis 16, dadurch gekennzeichnet, dass der Aktuator Kombinationen von verschiedenen Stellelementen umfasst.
- Verfahren zur Herstellung von Walzgut nach einem Verfahren entsprechend einem der Ansprüche 1 bis 13.
- Bandförmiges Walzgut hergestellt nach einem Verfahren, charakterisiert nach zumindest einem der Ansprüche 1 bis 14 und Anspruch 18, dadurch gekennzeichnet, dass das Walzgut Dickenabweichungen aufweist, die zumindest 20% geringer als die folgenden Dickentoleranzen sind.
Banddicke Toleranz 0,25 - 0,50 mm ± 1,2 % 0,50 - 0,89 mm ±1,0% 0,89 - 1,60 mm ± 0,9 % 1,60 - 2,54 mm ± 0,8 %
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT3642003 | 2003-03-10 | ||
AT0036403A AT500766B1 (de) | 2003-03-10 | 2003-03-10 | Verfahren und vorrichtung zur vermeidung von schwingungen |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1457274A2 true EP1457274A2 (de) | 2004-09-15 |
EP1457274A3 EP1457274A3 (de) | 2006-03-22 |
EP1457274B1 EP1457274B1 (de) | 2008-05-07 |
Family
ID=32739108
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP04003584A Revoked EP1457274B1 (de) | 2003-03-10 | 2004-02-18 | Verfahren und Vorrichtung zur Vermeidung von Schwingungen |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP1457274B1 (de) |
AT (2) | AT500766B1 (de) |
DE (1) | DE502004007020D1 (de) |
ES (1) | ES2306929T3 (de) |
Cited By (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1657003A1 (de) * | 2004-11-12 | 2006-05-17 | Vai Clecim | Verfahren zur Erkennung von Vibrationen eines Walzgerüstes |
DE102007006683A1 (de) * | 2007-02-10 | 2008-08-28 | WINKLER + DüNNEBIER AG | Vorrichtung und Verfahren zur aktiven Schwingungsdämpfung bei gegenläufig rotierenden Walzen |
WO2009153101A1 (de) * | 2008-06-18 | 2009-12-23 | Siemens Vai Metals Technologies Gmbh & Co | Verfahren und vorrichtung zur unterdrückung von schwingungen in einer walzanlage |
WO2010063664A1 (de) * | 2008-12-05 | 2010-06-10 | Siemens Vai Metals Technologies Gmbh & Co | Verfahren und vorrichtung zur semi-aktiven reduktion von druckschwingungen in einem hydrauliksystem |
WO2010063661A2 (de) * | 2008-12-05 | 2010-06-10 | Siemens Vai Metals Technologies Gmbh & Co | Verfahren und vorrichtung zur aktiven unterdrückung von druckschwingungen in einem hydrauliksystem |
CN104204552A (zh) * | 2012-03-26 | 2014-12-10 | 丹尼尔和科菲森梅克尼齐有限公司 | 借助于液压致动系统的振动阻尼系统 |
WO2016014316A1 (en) * | 2014-07-25 | 2016-01-28 | Novelis Inc. | Rolling mill third octave chatter control by process damping |
WO2017050493A1 (de) * | 2015-09-23 | 2017-03-30 | Sms Group Gmbh | Walzgerüst, walzlanlage und verfahren zum aktiven dämpfen von schwingungen in einem walzgerüst |
US10166584B2 (en) | 2014-07-15 | 2019-01-01 | Novelis Inc. | Process damping of self-excited third octave mill vibration |
WO2020239589A1 (de) | 2019-05-24 | 2020-12-03 | Primetals Technologies Austria GmbH | Industrieanlage mit einem dämpfungssystem zum dämpfen von schwingungen |
CN114226472A (zh) * | 2021-11-24 | 2022-03-25 | 首钢京唐钢铁联合有限责任公司 | 一种压下系统震荡检测方法和装置 |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102016202367A1 (de) * | 2016-02-16 | 2017-08-17 | Sms Group Gmbh | Vorrichtung zum Unterdrücken von Ratterschwingungen mit beschichteten Rollen in einer Walzstraße |
DE102018007847A1 (de) * | 2018-10-04 | 2020-04-09 | Carl Krafft & Söhne GmbH & Co. KG | Verfahren zum Erfassen von Nutzungsdaten von Walzen |
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US5724846A (en) * | 1996-01-31 | 1998-03-10 | Aluminum Company Of America | Interruption of rolling mill chatter by induced vibrations |
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TW476679B (en) * | 1999-05-26 | 2002-02-21 | Shinko Electric Co Ltd | Device for suppressing the vibration of a steel plate |
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2003
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-
2004
- 2004-02-18 ES ES04003584T patent/ES2306929T3/es not_active Expired - Lifetime
- 2004-02-18 DE DE502004007020T patent/DE502004007020D1/de not_active Expired - Lifetime
- 2004-02-18 EP EP04003584A patent/EP1457274B1/de not_active Revoked
- 2004-02-18 AT AT04003584T patent/ATE394176T1/de active
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EP0978589A2 (de) * | 1998-08-06 | 2000-02-09 | Voith Sulzer Papiertechnik Patent GmbH | Vorrichtung zum aktiven Schwächen unerwünschter Schwingungen einer rotierenden Walze; Vorrichtung zum Behandeln einer Materialbahn, insbesondere aus Papier oder Karton; Walze |
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Cited By (31)
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FR2877862A1 (fr) * | 2004-11-12 | 2006-05-19 | Vai Clecim Soc Par Actions Sim | Procede de detection des vibrations d'une cage de laminoir |
US7188496B2 (en) | 2004-11-12 | 2007-03-13 | Vai Clecim | Method for detecting the vibrations of a roll stand |
CN1330437C (zh) * | 2004-11-12 | 2007-08-08 | 韦克莱奇姆公司 | 检测轧辊机架的振动的方法 |
EP1657003A1 (de) * | 2004-11-12 | 2006-05-17 | Vai Clecim | Verfahren zur Erkennung von Vibrationen eines Walzgerüstes |
DE102007006683A1 (de) * | 2007-02-10 | 2008-08-28 | WINKLER + DüNNEBIER AG | Vorrichtung und Verfahren zur aktiven Schwingungsdämpfung bei gegenläufig rotierenden Walzen |
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CN108136459B (zh) * | 2015-09-23 | 2021-06-18 | Sms集团有限公司 | 轧机机架、轧制设备和用于主动地减弱轧机机架中的振动的方法 |
US11123781B2 (en) | 2015-09-23 | 2021-09-21 | Sms Group Gmbh | Roll stand, rolling system and method for actively damping vibrations in a roll stand |
WO2020239589A1 (de) | 2019-05-24 | 2020-12-03 | Primetals Technologies Austria GmbH | Industrieanlage mit einem dämpfungssystem zum dämpfen von schwingungen |
CN114226472A (zh) * | 2021-11-24 | 2022-03-25 | 首钢京唐钢铁联合有限责任公司 | 一种压下系统震荡检测方法和装置 |
CN114226472B (zh) * | 2021-11-24 | 2024-05-10 | 首钢京唐钢铁联合有限责任公司 | 一种压下系统震荡检测方法和装置 |
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Publication number | Publication date |
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ATE394176T1 (de) | 2008-05-15 |
EP1457274B1 (de) | 2008-05-07 |
AT500766A1 (de) | 2006-03-15 |
AT500766B1 (de) | 2008-06-15 |
ES2306929T3 (es) | 2008-11-16 |
EP1457274A3 (de) | 2006-03-22 |
DE502004007020D1 (de) | 2008-06-19 |
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