WO2017050493A1 - Walzgerüst, walzlanlage und verfahren zum aktiven dämpfen von schwingungen in einem walzgerüst - Google Patents
Walzgerüst, walzlanlage und verfahren zum aktiven dämpfen von schwingungen in einem walzgerüst Download PDFInfo
- Publication number
- WO2017050493A1 WO2017050493A1 PCT/EP2016/069568 EP2016069568W WO2017050493A1 WO 2017050493 A1 WO2017050493 A1 WO 2017050493A1 EP 2016069568 W EP2016069568 W EP 2016069568W WO 2017050493 A1 WO2017050493 A1 WO 2017050493A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- rolling
- stand
- roll
- actuator
- vibrations
- Prior art date
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
- B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
- B21B38/008—Monitoring or detecting vibration, chatter or chatter marks
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
- B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
- B21B2013/025—Quarto, four-high stands
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
- B21B2203/44—Vibration dampers
Definitions
- the invention relates to a roll stand for rolling, preferably cold rolling, of metal products, comprising at least one actuator that is controllable for active damping of vibrations in the rolling stand, and at least one not or exclusively via an adjusting device for passline setting of the roll stand engagable roll set for supporting and / or intermediate roll of a work roll of the roll stand, wherein all the rollers is guided at the ends via a respective bearing unit on a stand of the roll stand.
- the invention further relates to a rolling mill for rolling, preferably cold rolling, of metal objects, comprising at least one rolling stand and at least one system for actively damping vibrations in the rolling stand.
- the invention relates to a method for actively damping vibrations in a roll stand for rolling, preferably cold rolling, of metal products, wherein the vibrations are detected in the roll stand and the vibrations counteracting counter vibrations are generated, the counter vibrations are generated by means of at least one actuator.
- 5th-octave chatter vibrations are usually natural modes of the rolling set of a rolling stand in the frequency range between 500 Hz and 1000 Hz, by external excitations (so-called “forcing functions"), such as speed-proportional excitation frequencies from rolling bearings or the rollers or tooth meshing frequencies These usually cause surface and / or shape defects oriented in the rolled metal product, which are oriented transversely to the product or strip running direction.
- the 3rd octave chatter vibration is a self-excited vibration mode, which can also lead to transverse to the product or strip direction oriented thickness errors and consequently at high amplitudes to tape breaks.
- the instability arises here in that a certain natural vibration form of the complete set of rolls in the roll stand is destabilized by a system inherent in the rolling process feedback.
- the chatter-relevant intrinsic vibration form of the roll stand is usually the one in which an upper and a lower set of rolls in the roll stand substantially against each other. As a result, there is a high energetic potential for the excitation of this waveform from the nip.
- the frequency of this natural mode is usually between 80 Hz and 160 Hz.
- the destabilizing feedback (positive feedback) is caused by the rolling process itself, causing changes in the run-out speed caused by changes in the runout speed due to the mass flow law fluctuations of the intake train, which in turn affect the rolling force (so-called Wegenstein für) and so in turn affect the outlet thickness.
- the first two approaches have the disadvantage that hereby the Chatter limit speed, ie the rolling speed at which the stability limit for the self-excited 3rd octave chatter oscillation is reached, as a rule only comparatively small amounts, for example 50 m / min - 200 m / min, increase.
- the maximum possible system speed can not be achieved with these approaches in many cases.
- EP 2 052 796 A1 discloses such a method according to which pressure changes are generated directly in a pressure space adjacent to a piston of a hydraulic cylinder adjusting the roll gap.
- a plurality of small pistons are axially movably guided on the piston, which can be actuated via linear actuators.
- WO 2015/092775 A1 discloses another method for actively damping vibrations in a rolling stand.
- hydraulic actuators are used, which act for active vibration damping on bearing units of rollers over which the rollers are guided on a stand of the rolling stand.
- a piezoelectric injector is arranged, which is inserted directly into the pressure chamber of the hydraulic actuator.
- the damping effect is generated by a high-pressure oil injection in the hydraulic actuators.
- a roll stand for rolling, preferably cold rolling, of metal products comprises at least one actuator controllable for active damping of vibrations in the roll stand, and at least one support roll which can not or exclusively be adjusted by wedge adjustment of the roll stand for supporting a work roll or intermediate roll of the roll stand.
- the support roller is guided on the end side via a respective bearing unit on a stand of the roll stand.
- the support roller is supported on at least one bearing unit on the actuator and the actuator is supported either directly or indirectly via at least one adjusting device for passport adjustment, z.
- active damping allows to reduce maintenance effort and intervals as it reduces the effects of the above external stimuli on product quality. Ie. With active damping, a worse system condition with regard to excitation amplitudes is permissible for consistent product quality than without.
- the invention is a simple, inexpensive, easy to integrate and retrofit solution, especially when the actuator is placed on the rolling mill at the installation of a conventional load cell. There are then virtually no structural changes to a rolling stand for the integration of the actuator required. Therefore, the invention can be realized both in the course of retrofitting existing rolling stands as well as new rolling stands. In contrast, the proposed EP 2 052 796 A1 solution is relatively expensive, expensive and maintenance-intensive.
- the rolling mill according to the invention may also have two or more corresponding actuators, which are jointly or individually controllable for the active damping of the vibrations in the rolling stand.
- the control of the actuator or the actuators can be done for example electrically.
- the back-up roll can either not be adjustable or can only be adjusted by means of an adjusting device for the passline adjustment of the roll stand.
- the wedge adjustment is used to adjust the adjustment of the support roller and the working roller supported therewith, which is characterized by a transversely directed displacement of the Anstellkeils the wedge adjustment is achieved.
- the work roll optionally supported by the support roll via the intermediate roll cooperates with another work roll of the roll stand, wherein a roll gap is present between these work rolls.
- the further work roll and optionally intermediate roll can also be supported by a further support roll and be guided together with this to adjust the roll gap by means of at least one, in particular mechanical or hydraulic, adjusting means displaceable on the stand.
- the back-up rolls and the work rolls and, if appropriate, the intermediate roll are each guided at the ends via a respective bearing unit on the upright.
- the support roller which can not be set up exclusively or via the wedge setting of the roll stand, is supported on the actuator via an end-side storage unit or both end-side storage units. If the support roller can not be adjusted, the actuator is preferably supported directly on the section of the upright. If the back-up roll can be adjusted exclusively by means of the wedge setting of the roll stand, the actuator preferably supports itself indirectly via at least one adjusting wedge of the wedge setting on a section of the stand.
- the actuator is a piezo-mechanical actuator or a piezo-hydraulic actuator.
- the actuator is preferably designed as a compact or space-saving module that is optionally equipped with a piezo-mechanical actuator or a piezo-hydraulic actuator.
- the piezo-mechanical actuators are based on piezoceramic transducers, which are integrated directly into the mechanical structure of the oscillatory system, where they initiate dynamic forces directly.
- the piezoceramic transducer of a piezo-hydraulic actuator act indirectly on additional hydraulic converter to the system. In both cases, the required mechanical actuating amplitude (force / displacement) is generated via an electrical control of the piezoceramic transducer.
- the installation location according to the invention between a bearing unit of the support roller and the section of the stator is particularly suitable for the use of piezoactuators, because here a high efficiency with regard to the active damping of the 3rd octave chatter vibrations in combination with a relatively small actuator volume is given ,
- the actuator can be arranged between a lower stator crosshead and a bearing unit of the support roller.
- an existing load cell can be replaced by the actuator. It can then be dispensed with conventional load cells in the installation area, since the actuator takes over the measurement function of a load cell.
- a measuring principle for the force measurement comes either the force measurement on the piezoelectric elements used as an actuator or the force measurement via a separately to be integrated into the actuator unit force measurement, eg. B. via strain gages into consideration.
- a load cell or load cell is usually between the setting of the passline serving adjuster, z. B. a wedge adjustment and a bearing unit of a support roller.
- the rolling stand comprises at least two corresponding actuators, wherein the bearing units of the support roller are supported on one actuator and the two actuators each supported either directly or indirectly via at least one adjusting device for passport adjustment on a portion of the stand.
- the roll stand has at least one arranged on the stator vibration sensor for detecting the vibrations of the rolling stand.
- the vibration sensor may be configured to detect vibrations in the vertical direction.
- the 3rd octave and 5th octave chatter vibrations can be detected with the vibration sensor.
- the rolling mill can also have two or more vibration sensors. The use of two vibration sensors per roll stand is sufficient to detect the vibration phenomena described sufficiently accurately and to provide corresponding vibration signals.
- the vibration sensor is disposed on a portion of the stand opposite to the portion of the stand on which the actuator or abutment wedge is supported.
- the vibration sensor may, for example, be mounted on an upper stator crosshead of the stand of the rolling stand.
- the roll stand may have two stand spaced apart from one another in the transverse direction, on whose respective stator crosshead a respective vibration sensor is arranged.
- the vibration sensor is arranged to detect vibrations in a frequency range of about 0.5 Hz to about 2000 Hz.
- a rolling mill according to the invention for rolling, preferably cold rolling, of metal objects comprises at least one rolling stand and at least one system for actively damping vibrations in the rolling stand, wherein the rolling stand is formed according to one of the aforementioned embodiments or any combination thereof.
- the system comprises at least one control electronics signal-technically connected to the vibration sensor and the actuator, with the vibration signals generated by the vibration sensor for generating control signals can be evaluated and which is adapted to control the actuator for introducing counter vibrations into the rolling stand with the respective control signals.
- the rolling mill can also have two or more corresponding rolling stands, each of which is assigned its own system for actively damping vibrations in the rolling stand.
- the rolling stands may be associated with a single common system for actively dampening vibrations in the rolling stand.
- the rolling mill may in particular be a single or multi-stand steel or aluminum cold rolling mill.
- the system may include a control system and a signal amplifier connected thereto signal amplifier for amplifying the control signals.
- the active vibration damping can thus at least one vibration sensor, via which the vibrations in the roll stand can be measured, at least one actuator, which imposes a counter vibration on the rolling mill to be damped at a suitable location and include a control system, which for extinguishing the vibrations at the place of interest Roll stand required counter vibration in frequency, amplitude and Calculated phase and prepared for the activation of the actuator. From a control engineering point of view, the reduction of the vibration amplitude via the application of a countervibration can also be interpreted as a (controlled) increase of the damping, which is why one speaks of "active damping".
- control electronics for online monitoring of the vibrations of the rolling mill, for online visualization of vibration levels of the vibrations of the rolling mill, for automatically starting at least a low-vibration rolling speed and / or automatically reducing a current rolling speed depending on the currently detected vibrations of the rolling mill set ,
- the monitoring and visualization of the vibrations in the mill enables visual inspection and eventual operator intervention.
- the automatic start of suitable, low-vibration rolling speed ranges serves to improve the rolling result or the product quality.
- the automatic reduction of a current rolling speed as a function of the currently detected vibrations of the rolling stand serves in particular to avoid band breaks when third octave chatter vibrations occur.
- the control electronics can also consist of several separate modules that are put together individually
- the control electronics is set up to determine frequencies, amplitudes and / or phase angles of the countervibrations to be generated.
- the control electronics can process the vibration signals of the vibration sensor or of the vibration sensors in order to calculate an optimum signal shape, that is to say the frequency and the amplitude, as well as the phase position of one or more countervibrations which are required in each case in order to correspond to the corresponding unwanted vibrations in the rolling stand extinguish.
- the control electronics is set up to generate the control signals taking into account a transmission behavior of the vibration sensor, the actuator and / or a rolling stand of the rolling mill. As a result, the targeted introduction of the counter vibrations in the rolling stand can be improved.
- control electronics is set up to respond to changes in the characteristics of the actuator and / or an applied controlled system over time.
- the control electronics is thus based on an adaptive control, so that the control can automatically adapt to changing conditions and circumstances in order to optimize the targeted introduction of counter-vibrations in the rolling stand.
- the vibrations in the roll stand are detected and the vibrations counteracting vibrations generated, the counter vibrations are generated by means of at least one actuator, the counter vibrations in at least one not or exclusively via a wedge adjustment of the rolling stand engagable support roller for supporting a work roll or intermediate roll of the rolling mill are introduced, which is supported on at least one bearing unit, via which it is guided on a stand of the roll stand on the actuator, and wherein the actuator either directly or indirectly via an adjusting device for passline adjustment is supported on a portion of the stand.
- the rolling stand or the rolling mill can be used to carry out the method.
- Advantageous embodiments of the roll stand and the rolling mill, if they contain process features are advantageous embodiments of the method, even if this is not explicitly described.
- the actuator is used for detecting rolling forces.
- the advantages mentioned above with respect to the corresponding embodiment of the roll stand are connected accordingly.
- FIG. 2 shows a schematic and perspective detail of FIG
- Figure 1 shows a schematic and perspective view of an embodiment of a rolling mill 1 according to the invention for rolling, in particular cold rolling, of metal objects.
- the rolling mill 1 comprises a rolling stand 2 and a system 3 for actively damping vibrations in the rolling stand 2.
- the rolling stand 2 comprises an upper work roll 4 and a cooperating lower work roll 5, between which a roll gap 6 is formed.
- the work rolls 4 and 5 are guided in each case at the ends via a respective bearing unit 7 to a respective stand 8 of the roll stand 2.
- the roll stand 2 comprises a top working roll 4 supporting upper support roller 9 and a lower work roll 5 supporting the lower support roller 10.
- the support rollers 9 and 10 are each end over a respective storage unit 1 1 guided to a respective stand 8 of the rolling stand 2.
- the roll stand 2 also comprises two arranged on each stand 8 Anstelleinnism 12 for hiring the upper work roll 4 together with the upper support roller 9 and for adjusting the height of the roll gap 6.
- the Anstellein opposition 12 serve to generate the respective rolling forces.
- the roll stand 2 comprises a wedge setting 13 arranged on the uprights 8 with a setting wedge 14 and a setting device 15 which actuates the setting wedge 14.
- the roll stand 2 comprises two actuators 16 which can be activated for the active damping of vibrations in the roll stand 2. Furthermore, the roll stand 2 comprises, as stated above, the lower back-up roll 10, which can be set exclusively via the wedge setting 13 of the roll stand 2, for supporting the lower work roll 5 of the roll stand 2.
- the lower support roll 10 is supported on the storage units 1 1 on one of the two Actuators 16 off.
- the actuators 16 are supported indirectly via the Anstellkeil 14 of the wedge adjustment 13 at a portion 17 of the respective stator 8, wherein it is at the respective section 17 to a lower stator crosshead.
- the actuators 16 are each designed as a piezo-mechanical actuator or as a piezo-hydraulic actuator.
- the actuators 16 can be set up to detect rolling forces, which makes it possible to dispense with conventional load cells.
- the roll stand 2 further comprises two vibration sensors 18 arranged on a respective stand 8 for detecting the vibrations of the roll stand 2.
- Each vibration sensor 18 is in contact with the roll gap 6 a portion 19 of the respective stator 8, which is arranged opposite to the portion 17 of the respective stator 8, on which the Anstellkeil 14 is supported.
- the section 19 is formed by an upper stator crosshead of the respective stator 8.
- Each vibration sensor 18 may be configured to detect vibrations in a frequency range of about 0.5 Hz to about 2000 Hz.
- Each vibration sensor 18 may be an acceleration sensor.
- the system 3 comprises a control electronics 20 which is signal-technically connected to the vibration sensors 18 and the actuators 16, with which the vibration signals generated by the vibration sensors 18 can be evaluated to generate control signals and which is set up, the actuators 16 for introducing countervibrations into the rolling stand 2 with the to control the respective actuating signals. Furthermore, the system 3 comprises a signal amplifier 21 for amplifying the actuating signals to be supplied to the actuators 16.
- the control electronics 20 may be used for online monitoring of the vibrations of the rolling stand 2, for on-line visualization of vibration levels of the vibrations of the rolling stand 2, for automatically starting at least a low-vibration rolling speed and / or automatically reducing a current rolling speed depending on the currently detected vibrations of the rolling stand 2 be set up. Furthermore, the control electronics 20 may be configured to determine necessary frequencies, amplitudes and / or phase angles of the countervibrations to be generated. In addition, the control electronics 20 may be configured to generate the control signals taking into account a transmission behavior of the vibration sensors 18, the actuators 16 and / or a rolling mill of the rolling stand 2 formed by the rollers 4, 5, 9 and 10.
- FIG. 2 shows a schematic and perspective detailed representation of the roll stand 2 of the rolling plant shown in FIG.
- the arrangement of the actuators 16 on the Anstellkeil 14 of the wedge adjustment 13 can be better seen, which is supported on the lower portions 17 of the stator 8.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vibration Prevention Devices (AREA)
- Control Of Metal Rolling (AREA)
- Metal Rolling (AREA)
Abstract
Description
Claims
Priority Applications (9)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US15/762,199 US11123781B2 (en) | 2015-09-23 | 2016-08-18 | Roll stand, rolling system and method for actively damping vibrations in a roll stand |
KR1020187009376A KR102057562B1 (ko) | 2015-09-23 | 2016-08-18 | 롤 스탠드, 압연 시스템 및 롤 스탠드 내 진동의 능동적 감쇠 방법 |
RU2018114127A RU2697116C1 (ru) | 2015-09-23 | 2016-08-18 | Прокатная клеть, прокатная установка и способ активного гашения колебаний в прокатной клети |
BR112018005756-8A BR112018005756B1 (pt) | 2015-09-23 | 2016-08-18 | Laminador, equipamento de laminação e método para amortecimento ativo de vibrações em um laminador |
JP2018534001A JP6608538B2 (ja) | 2015-09-23 | 2016-08-18 | ロールスタンド内の振動を減衰させるためのロールスタンド、圧延設備及び方法 |
EP16753391.8A EP3352921B1 (de) | 2015-09-23 | 2016-08-18 | Walzgerüst, walzlanlage und verfahren zum aktiven dämpfen von schwingungen in einem walzgerüst |
CN201680054942.5A CN108136459B (zh) | 2015-09-23 | 2016-08-18 | 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 |
ZA2018/01688A ZA201801688B (en) | 2015-09-23 | 2018-03-12 | Roll stand, rolling system and method for actively damping vibrations in a roll stand |
SA518391175A SA518391175B1 (ar) | 2015-09-23 | 2018-03-22 | حامل دلفنة، نظام دلفنة وطريقة لإخماد الاهتزازات في حامل دلفنة بشكل فعال |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015218251.7 | 2015-09-23 | ||
DE102015218251 | 2015-09-23 | ||
DE102015223516.5A DE102015223516A1 (de) | 2015-09-23 | 2015-11-27 | Walzgerüst, Walzlanlage und Verfahren zum aktiven Dämpfen von Schwingungen in einem Walzgerüst |
DE102015223516.5 | 2015-11-27 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2017050493A1 true WO2017050493A1 (de) | 2017-03-30 |
Family
ID=58224522
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2016/069568 WO2017050493A1 (de) | 2015-09-23 | 2016-08-18 | Walzgerüst, walzlanlage und verfahren zum aktiven dämpfen von schwingungen in einem walzgerüst |
Country Status (10)
Country | Link |
---|---|
US (1) | US11123781B2 (de) |
EP (1) | EP3352921B1 (de) |
JP (1) | JP6608538B2 (de) |
KR (1) | KR102057562B1 (de) |
CN (1) | CN108136459B (de) |
DE (1) | DE102015223516A1 (de) |
RU (1) | RU2697116C1 (de) |
SA (1) | SA518391175B1 (de) |
WO (1) | WO2017050493A1 (de) |
ZA (1) | ZA201801688B (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN109290373A (zh) * | 2018-12-10 | 2019-02-01 | 重庆邓氏厨具制造有限公司 | 数控轧机 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017109713A1 (de) | 2017-05-05 | 2018-11-08 | Data M Sheet Metal Solutions Gmbh | Rollformanlage mit Sensor-Rollformgerüst |
CN110756593B (zh) * | 2018-07-26 | 2020-10-27 | 宝山钢铁股份有限公司 | 一种抑制冷连轧机组振动的张力制度优化方法 |
CN117921499B (zh) * | 2024-03-25 | 2024-06-21 | 燕山大学 | 一种在役高温轧辊表面修磨再役装置及方法 |
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WO2001000346A1 (en) * | 1999-06-25 | 2001-01-04 | Industrial Automation Services Pty Ltd | Vibration damping apparatus |
EP1457274A2 (de) * | 2003-03-10 | 2004-09-15 | Voest-Alpine Industrieanlagenbau GmbH & Co. | Verfahren und Vorrichtung zur Vermeidung von Schwingungen |
EP1961992A2 (de) * | 2007-02-10 | 2008-08-27 | Winkler + Dünnebier AG | Vorrichtung und Verfahren zur aktiven Schwingungsdämpfung bei gegenläufig rotierenden Walzen |
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2015
- 2015-11-27 DE DE102015223516.5A patent/DE102015223516A1/de not_active Withdrawn
-
2016
- 2016-08-18 CN CN201680054942.5A patent/CN108136459B/zh active Active
- 2016-08-18 WO PCT/EP2016/069568 patent/WO2017050493A1/de active Application Filing
- 2016-08-18 US US15/762,199 patent/US11123781B2/en active Active
- 2016-08-18 KR KR1020187009376A patent/KR102057562B1/ko active IP Right Grant
- 2016-08-18 RU RU2018114127A patent/RU2697116C1/ru active
- 2016-08-18 EP EP16753391.8A patent/EP3352921B1/de active Active
- 2016-08-18 JP JP2018534001A patent/JP6608538B2/ja active Active
-
2018
- 2018-03-12 ZA ZA2018/01688A patent/ZA201801688B/en unknown
- 2018-03-22 SA SA518391175A patent/SA518391175B1/ar unknown
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WO2001000346A1 (en) * | 1999-06-25 | 2001-01-04 | Industrial Automation Services Pty Ltd | Vibration damping apparatus |
EP1457274A2 (de) * | 2003-03-10 | 2004-09-15 | Voest-Alpine Industrieanlagenbau GmbH & Co. | Verfahren und Vorrichtung zur Vermeidung von Schwingungen |
EP1961992A2 (de) * | 2007-02-10 | 2008-08-27 | Winkler + Dünnebier AG | Vorrichtung und Verfahren zur aktiven Schwingungsdämpfung bei gegenläufig rotierenden Walzen |
EP2052796A1 (de) | 2007-10-23 | 2009-04-29 | Eras Entwicklung und Realisation adaptiver Systeme GmbH | Verfahren und Vorrichtung zum Unterdrücken des Ratterns von Arbeitswalzen eines Walzgerüsts |
WO2015092775A1 (en) | 2013-12-20 | 2015-06-25 | Danieli & C. Officine Meccaniche S.P.A. | Active vibration damping system of a rolling mill |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
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CN109290373A (zh) * | 2018-12-10 | 2019-02-01 | 重庆邓氏厨具制造有限公司 | 数控轧机 |
CN109290373B (zh) * | 2018-12-10 | 2023-09-05 | 重庆邓氏厨具制造有限公司 | 数控轧机 |
Also Published As
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JP2018532597A (ja) | 2018-11-08 |
KR102057562B1 (ko) | 2019-12-19 |
KR20180050356A (ko) | 2018-05-14 |
DE102015223516A1 (de) | 2017-03-23 |
CN108136459A (zh) | 2018-06-08 |
RU2697116C1 (ru) | 2019-08-12 |
ZA201801688B (en) | 2019-01-30 |
US20180290191A1 (en) | 2018-10-11 |
US11123781B2 (en) | 2021-09-21 |
SA518391175B1 (ar) | 2022-03-23 |
EP3352921B1 (de) | 2021-10-20 |
JP6608538B2 (ja) | 2019-11-20 |
BR112018005756A2 (pt) | 2018-10-09 |
EP3352921A1 (de) | 2018-08-01 |
CN108136459B (zh) | 2021-06-18 |
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