EP2794136A1 - Procédé et dispositif de refroidissement de cylindres - Google Patents

Procédé et dispositif de refroidissement de cylindres

Info

Publication number
EP2794136A1
EP2794136A1 EP12798664.4A EP12798664A EP2794136A1 EP 2794136 A1 EP2794136 A1 EP 2794136A1 EP 12798664 A EP12798664 A EP 12798664A EP 2794136 A1 EP2794136 A1 EP 2794136A1
Authority
EP
European Patent Office
Prior art keywords
pressure
coolant
gap
volume flow
cooling
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.)
Granted
Application number
EP12798664.4A
Other languages
German (de)
English (en)
Other versions
EP2794136B1 (fr
Inventor
Matthias Kipping
Ralf Seidel
Johannes Alken
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Group GmbH
Original Assignee
SMS Siemag AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SMS Siemag AG filed Critical SMS Siemag AG
Publication of EP2794136A1 publication Critical patent/EP2794136A1/fr
Application granted granted Critical
Publication of EP2794136B1 publication Critical patent/EP2794136B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/10—Lubricating, cooling or heating rolls externally
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/10—Lubricating, cooling or heating rolls externally
    • B21B2027/103—Lubricating, cooling or heating rolls externally cooling externally

Definitions

  • the present invention relates to the cooling of rolls, in particular of work rolls in a rolling mill with a cooling liquid.
  • the gap between the cooling shell and the roller must be regulated. It is desirable that cooling medium flow past the roll surface at a high speed to effectively cool the roll. To press a cooling medium through the gap, a corresponding pressure is necessary. From the general state of the art it is known that distance sensors can be used to measure the height of a gap.
  • a disadvantage of such a distance measurement is often that distance measurements in the flow between the cooling shell and the roll surface are difficult or inaccurate. If, however, the distances, for example, indirectly determined by measuring the travel of a piston for employment of the cooling shell to the roll surface, also measurement inaccuracies and thus employment errors can occur. In particular, in this case, the current position of the roller is not known, so that the control can not adequately react in the case of short-term occurring jumps of the roller.
  • Failure to place the cooling tray against the roller can result in damage from a collision of the roller with the cooling tray or overheating of the roller. Overheating the roller can damage the roller or reduce the quality of the rolled strip.
  • the object of the invention is therefore to provide an improved, in particular reliable and robust system for the employment of a cooling shell on a roll surface.
  • Another object of the invention is to overcome at least one of the above disadvantages.
  • the above object is solved by the features of claim 1, which is directed to a method for cooling a roll, in particular a work roll of a hot rolling plant.
  • the method includes feeding coolant through a nozzle into a gap between at least a portion of the roll surface and a cooling bowl engageable with the portion of the roll surface, and adjusting the gap height between the cooling shell and the roll surface.
  • the adjustment or regulation of the gap height takes place either on the basis of a measurement of the coolant pressure or a measurement of the volume flow of the supplied coolant.
  • the coolant pressure or the volume flow of the coolant is an indicator of the gap distance.
  • the method according to the invention is no longer dependent on an error-prone distance measurement between the cooling shell and the roll surface and permits an accurate determination of the gap spacing as a function of the measured coolant pressure or volume flow.
  • the method according to the invention automatically detects, in particular, a change in position of the roller.
  • the adjustment comprises an increase in the distance (the gap height) between the roller and the cooling shell when the measured coolant pressure or volume flow is above a predefinable upper limit value. This can be counteracted in particular a collision between the roller and the cooling shell. It is also possible to shut down the system if it falls below an upper limit to avoid damage and longer downtimes and production downtime.
  • the distance (the gap height) between the roller and the cooling shell is reduced when the measured coolant pressure or volume flow of the coolant is below a predefinable lower limit.
  • the adjustment of the distance or the gap height can be done by known to those skilled Anzustell listeningen, such as by (hydraulic or pneumatic) piston-cylinder units. But other electrical, mechanical or electro-mechanical Anzustell drivingen are possible.
  • the coolant is supplied with a known or defined volume flow of the nozzle (and thus the gap).
  • the adjustment or regulation of the distance between the roller and the cooling shell takes place after measurement of the coolant pressure, preferably using a previously determined pressure-distance characteristic, which corresponds to the known volume flow of the coolant.
  • the volume flow of the supplied coolant is kept constant and the measured coolant pressure is compared by means of a constant-volume flow corresponding pressure-distance characteristic with a predetermined nominal height of the gap.
  • a control difference resulting from the comparison can be used as a proviso for adjusting or adapting the gap height.
  • the pressure of the supplied coolant is kept constant and the measured volume flow of the coolant is compared with a predeterminable desired height of the gap via a volume flow / distance characteristic corresponding to the pressure maintained constant.
  • a control difference resulting from this comparison can be used as a proviso for adjusting the gap height.
  • the actual coolant pressure is measured by a pressure sensor and associated with the aid of a pressure-distance characteristic of an actual gap height.
  • the coolant volume flow is kept constant in accordance with the pressure-distance characteristic used.
  • This actual gap height is compared with a predefinable target gap height.
  • the difference from this comparison is preferably passed to a controller. In accordance with the difference, the gap distance is subsequently adjusted (by output of an adjustment value).
  • the actual coolant pressure is measured by a pressure sensor.
  • the coolant volume flow is kept constant.
  • a predefinable setpoint height is assigned to a setpoint pressure with the aid of a pressure-distance characteristic line corresponding to the constant volume flow.
  • This target pressure is compared with the measured actual coolant pressure.
  • a resulting difference is preferably directed to a controller. In accordance with the difference, the gap distance is subsequently adjusted (by output of an adjustment value).
  • the actual volume flow rate is measured by a volumetric flow meter and assigned to an actual gap height with the aid of a volume flow / distance characteristic curve.
  • the coolant pressure is kept constant in accordance with the pressure-distance characteristic used.
  • the actual gap height is compared with a predefinable target gap height. The difference from this comparison is preferably passed to a controller. This outputs a control value to a starting device, which adjusts the gap distance.
  • the actual volume flow is measured by a volumetric flow meter.
  • the coolant pressure is kept constant.
  • a predefinable desired height is held by means of a held constant Coolant pressure corresponding volume flow-distance characteristic associated with a desired volume flow.
  • This nominal volume flow is compared with the measured actual volume flow.
  • a resulting difference is preferably directed to a controller. This preferably outputs a control value to a starting device, which adjusts the gap distance. In other words, the difference serves as a proviso for the adjustment of the gap distance.
  • a characteristic curve can be determined, for example, experimentally or by means of a numerical simulation.
  • the characteristic curve in the case of the measurement of the pressure
  • the characteristic curve is determined for a multiplicity of different volume flows (at least two), in particular for at least one defined coolant pressure supplied for cooling the roller.
  • the characteristic for a plurality of different pressures (at least two), in particular for at least one defined for the cooling of the roll, defined volume flow of the coolant.
  • the characteristic is given by an allocation of coolant pressure against the gap height between the roll surface and the cooling shell. If, however, the volume flow of the coolant is measured, the characteristic is given by an allocation of volume flow against the gap height between the roll surface and the cooling shell.
  • the applied against the gap height coolant pressure or volume flow is determined or specified at the point at which the pressure or the flow rate is measured.
  • the measurement of the pressure or of the volume flow is generally carried out preferably in the region of the nozzle or in particular in the nozzle, for example in the nozzle inlet.
  • the present invention comprises a device for cooling a work roll, preferably for carrying out the method according to one of the preceding embodiments, wherein the device comprises an adjustable to the roller cooling shell, which, to a range of
  • Roll surface has substantially complementary shape and extends over at least a portion of the axial width of the roller and over at least part of the circumferential direction of the roller.
  • the device comprises a nozzle for supplying a coolant into a gap between the cooling shell and the roll surface and a pressure sensor for measuring the coolant pressure, preferably in the region of the nozzle and a (regulating) device for regulating or adjusting the gap height between the cooling shell and the roller as a function of the measured by the pressure sensor
  • the device may also have one
  • Volumetric flow meter (or -geber / -sensor) for measuring the volume flow of the coolant, preferably in the region of the nozzle and a (control) device for regulating or adjusting the gap height between the cooling shell and the roller as a function of measured by the volume flow meter
  • Volume flow include.
  • the present invention also includes a coolable rolling apparatus, preferably for carrying out the above method, comprising a roll engageable to roll a metal strip and the above-mentioned apparatus for cooling the roll.
  • the nozzle guides the coolant substantially parallel to the circumferential direction of the roller or tangentially to the roller.
  • the clear dimension of the nozzle can generally taper towards the roll surface, that is to say tapering from a nozzle inlet to a nozzle outlet.
  • the nozzle can taper from the nozzle inlet to the nozzle outlet with simultaneous deflection of the coolant flow in a direction tangential to the roller surface direction.
  • the nozzle or the nozzle outlet can generally be formed by a slot lying parallel to the roller axis. Alternatively, a plurality of nozzles may be provided parallel to the roll axis for supplying coolant into the gap.
  • the flow direction of the cooling liquid in the gap is opposite to the direction of rotation of the roller.
  • the nozzle is arranged in relation to the flow direction of the cooling liquid in the gap in an upstream end region of the cooling shell.
  • the nozzle may generally be an integral part of the cooling shell or be formed in this or else be used separately through an opening in the cooling shell.
  • the nozzle could be arranged separately on an end of the cooling shell lying in the circumferential direction of the roll.
  • the nozzle may also be formed, for example, by a pipe or a hose.
  • a scraper for stripping coolant from the roll surface is arranged at the downstream end of the cooling shell, so that less coolant passes onto a metal strip to be rolled.
  • the employment of the cooling shell to the roll surface by tilting and / or a translational movement of the cooling shell takes place.
  • the cooling shell in the circumferential direction of the roller is formed at least in two parts, wherein both parts of the cooling shell are pivotally connected to each other about an axis parallel to the axial direction of the roller axis.
  • the cooling shell is constructed in several parts in the circumferential direction and the adjacent parts (each) are pivotally connected to each other, so that an even better adaptation to the circumference of the roller is possible.
  • FIG. 1 a schematic cross section through an apparatus for cooling a roller according to an embodiment of the invention; an exemplary pressure-distance characteristic at a given volume flow of the coolant; an exemplary volumetric flow-distance characteristic at a predetermined pressure of the coolant; a control scheme for controlling the gap height and the distance between a cooling shell and a roll surface by means of a pressure-distance characteristic; Another possible control scheme for controlling the gap height and the distance between a cooling shell and a roll surface by means of a pressure-distance characteristic; a control scheme for controlling the gap height and the distance between a cooling shell and a roll surface by means of a volume flow-distance characteristic; and another possible control scheme for controlling the gap height or the distance between a cooling shell and a roll surface by means of a volume flow-distance characteristic.
  • FIG. 1 shows a device 10 according to an embodiment of the invention for cooling a work roll 1.
  • the device 10 comprises a cooling shell 9, 1 1, which has a substantially complementary shape to at least part of the calf circumference U.
  • the cooling shell 9, 1 1 can be adjusted to the roll by means of an adjusting device, not shown, and can also extend over at least a portion of the axial roll width in the axial direction of the roll 1.
  • the height h is regulated by the device 10 or adjustable.
  • the distance h between the cooling shell 9, 1 1 and the roller 1 is adjustable.
  • the gap height may be between 0.1 cm and 2.5 cm, and preferably between 0.2 cm and 1 cm.
  • the work roll 1 rotates as shown preferably in the direction of rotation D and thereby exerts a force on a to be rolled band 15. On the opposite side of the strip 15 of the work roll 1, this can be supported by at least one other role.
  • coolant 3 can be introduced into the gap 7 via a nozzle.
  • the gap 7 is almost completely traversed by coolant 3 for cooling the roller 1.
  • the nozzle 5 can be formed as shown in the body of the cooling shell 9, 1 1.
  • the nozzle 5 preferably introduces coolant 3 into the gap 7 in a direction opposite to the roller rotation direction D. This introduction preferably takes place essentially parallel or tangentially to the circumferential direction U of the roll 1.
  • the term circumferential direction is not to be understood as limiting with respect to an orientation here, but rather to describing a direction which is defined by the surface curvature of the roller 1.
  • the nozzle 5 may have a downstream tapered shape.
  • the nozzle 5 may taper from a dimension corresponding to approximately 5 to 20 times the gap height to a dimension approximately equal to 0.5 to 3 times the gap height.
  • coolant 3 is introduced into the nozzle 5 with a defined volume flow V x .
  • the pressure p of the coolant 3 can preferably still be measured in the region of the nozzle 5, that is, for example, in the tapering region of the nozzle 5 between the nozzle inlet and the nozzle outlet.
  • the pressure measurement can take place with a pressure sensor 13 known and suitable to the person skilled in the art.
  • the coolant 3 it is likewise possible for the coolant 3 to be introduced into the nozzle 5 with a defined pressure p x .
  • the volume flow of the coolant 3 can preferably be measured in the region of the nozzle 5, that is, for example, in the tapering region of the nozzle 5 between the nozzle inlet and the nozzle outlet.
  • the volume flow measurement can be carried out with a volume flow meter 13 known and suitable to the person skilled in the art.
  • both sensor types are installed, so that either a measurement of the pressure at a known or fixed volume flow or a measurement of the volume flow at known or fixed pressure can take place.
  • the nozzle 5 is an integral part of the cooling shell 9 as shown.
  • the nozzle 5 could also be separated into one Be inserted opening of the cooling shell 5 or at one in totally designedsnchtung U of the cooling shell 9, 1 1 lying end to the cooling shell 9, 10 adjacent.
  • the cooling shell 9, 1 1 may further be formed in several parts.
  • the cooling shell in computersnchtung U have several means for pivoting about an axis parallel to the roll axis A. By one or more such pivot axes A along the diligentsnchtung U, the employment of the cooling shell 9, 1 1 can be adapted to different roll diameter even better.
  • a scraper 17 (for example made of metal, wood or hard tissue) may also generally be arranged at the end of the gap 7 downstream of the coolant 3 or at the end of the gap 7 closest to the strip 15 to be rolled, be arranged.
  • the scraper 17 may for example be formed by a plate which along one of its edges on the circumference U of the roller 1 can be adjusted. It is possible that the scraper 17 is medium or directly movable with the cooling shell 7 and / or is pivotally formed with one of their parts 1 1. However, the scraper 17 can also be provided separately. From the scraper 17, the gap 7 leaving coolant 5 can be sucked. Further, the scraper 17 may be profiled according to the work roll.
  • the regulation or adjustment of the gap height h of the gap 7 between the roll surface and the cooling shell 9, 1 1 could be done by measuring or monitoring the pressure p in the region of the nozzle 3.
  • a measurement by means of a pressure sensor 13 arranged in the nozzle 3 enables a reliable determination of the gap distance h.
  • the measurement by the sensor 13 can also take place in the gap 7 itself, in the region of the nozzle 5 or also upstream of the nozzle 5 and is therefore not restricted to the region of the nozzle 5.
  • the pressure p is measured by means of the encoder 13 and assigned to an actual distance between the cooling shell 9, 1 1 and roll surface or assigned to an actual gap height h.
  • This assignment can be made for example on the basis of previously determined characteristic curves K x .
  • Such characteristic curves K x could either be measured or, preferably, mathematically determined by a numerical simulation.
  • FIG. 2a exemplifies such a characteristic curve K x .
  • the characteristic curve K X (V X ) is represented for a specific (predetermined or defined) volume flow V x and describes the relationship between the pressure p (at the location of the pressure measurement) and the gap height h.
  • each pressure p can be assigned a gap height h at a known volume flow V x . If, for example, only one volume flow V x is to be used for cooling, a characteristic curve K x is sufficient. If it is intended to be possible to use other or several volume flows V y , corresponding characteristic curves K y are preferably provided.
  • the characteristic curve K x shown in FIG. 2 a thus describes the course between pressure p and gap height h for a fixed volume flow V x . The characteristic curve would shift in the illustrated diagram for other volume flows V which are greater or smaller than V x , as shown by the arrows. Furthermore, a preferred working range is shown between the points A1 and A2.
  • Such a working area does not necessarily have to be defined and depends on the conditions of an existing installation and on the existing rolls, the product to be rolled or the intended reduction in strip thickness.
  • the illustrated, preferred work area is through the Value pairs p max , h min (A1) and p min , h max (A2) limited.
  • the slope of the characteristic curve in the working range, ie between Ai and A 2 is preferably of the order of 1 (eg between 0.1 and 10), which improves the controllability of the system compared to larger or smaller values.
  • the maximum pressure p max can be limited both for design reasons and for cost reasons.
  • the maximum gap height h max may be limited insofar as h large amounts of coolant are required in the case of excessively large gap heights in order to ensure sufficient cooling (in particular due to a high flow velocity and / or constant contact of the roll surface with coolant).
  • the gap distance h can be set or regulated with the aid of a volumetric flow-distance characteristic K x (p x ).
  • a characteristic K x (p x ) is shown in FIG. 2b.
  • the determination can be carried out analogously as in FIG. 2a, but the characteristic K x (p x ) is now mapped for a known pressure p x . Plotted is the volume flow V against the gap height h. If the predeterminable pressure p is chosen to be greater or smaller than p x , the characteristic curve K x (p x ) would shift as shown.
  • the further interpretation of the characteristic curve is analogous to the characteristic curve from FIG. 2a, except that the pressure p for a characteristic curve K x (p x ) is recorded and the volume flow V varies.
  • the characteristic curve K x can also be present in the form of value tables, matrices, arrays or a function profile and / or stored in an evaluation device which is designed to be measured Press pi st or measured volume flows V
  • the characteristic curve K x it is possible for the characteristic curve K x to be used in such a way that it serves to assign a setpoint height of the gap h So n to a setpoint pressure p So ii or a setpoint volume flow V So n. This is described in more detail with reference to FIGS. 3b and 4b.
  • FIG. 3a shows an example of a possible regulation or adjustment of the gap height h, which is changed, for example, by a position change of the roll surface (disturbance variable). Such positional change can be caused by a roll change or wear. It is also possible that unpredictable cracks of the roll 1 occur in the rolling operation.
  • An existing gap height leads to a present coolant pressure Pist (controlled variable), which can be detected by a pressure sensor 13 (measuring element).
  • a possibly existing difference e h between actual and desired height is preferably fed to a control device (controller).
  • the control device then preferably outputs an adjustment value Ssteii to a setting device (actuator). This then adjusts the gap distance h accordingly, so that the desired distance h S0 ii (at least in the short term) is restored.
  • the control difference can also be fed directly to a starting device.
  • a pressure sensor 13 determines a coolant pressure pi st (controlled variable) and supplies this actual value to a differential element or differential former where it is compared with a desired value of the coolant pressure p So ii.
  • This desired pressure p So n may preferably result from a pressure-distance characteristic, wherein a desired distance of the gap h So ii is specified and with the aid of the pressure-distance characteristic of the desired distance of the Spalts hsoii a target pressure of the coolant p So ii is assigned.
  • the control difference resulting from the comparison of the actual pressure p ! St and the setpoint pressure p So ii is preferably fed to the control device, which outputs a control value for the adjusting device, so that the gap distance h can be adjusted or adjusted on the basis of the determined pressure difference e p .
  • the cooling process it is possible for the cooling process to be monitored by a volumetric flow meter 13 (measuring element). If the gap height h changes, this leads to a changed coolant volume flow V
  • St can with the help of a volume flow-distance characteristic K x (p x ) at a known, fixed pressure p x in an actual gap height h St be transformed.
  • the value of the actual gap height h 1 determined using the characteristic curve K x can then be determined St are compared with a desired desired gap height h So ii. This comparison can lead to a control difference e h .
  • control device which preferably outputs an adjustment value Ssteii to an adjusting device (actuator).
  • the adjuster then adjusts the gap distance h accordingly, so that the desired distance h So n is restored.
  • the characteristic curve according to FIG. 4b can be used to assign a nominal volume flow Vsoii to a desired distance h So ii, the latter being determined by an actual volume flow V
  • a control difference e v resulting from such a comparison can subsequently be converted into a manipulated variable by a control device in order to set the desired setpoint distance h So n in accordance with the control difference e v .
  • V x volume flow x (defined volume flow)

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Heat Treatment Of Strip Materials And Filament Materials (AREA)

Abstract

L'invention concerne un procédé de refroidissement d'un cylindre (1), en particulier d'un cylindre de travail (1) d'une installation de laminage à chaud, comprenant l'alimentation d'un fluide réfrigérant (3) au moyen d'une buse (5) dans un jeu (7) entre une partie au moins de la surface du cylindre et une chemise de refroidissement (9, 11) qui peut être mise en place sur cette partie de la surface du cylindre, ainsi que le réglage de la hauteur (h) du jeu entre la chemise de refroidissement (9, 11) et la surface du cylindre. Le réglage de la hauteur de jeu (h) comprend selon l'invention la mesure soit de la pression (Préel), soit du débit volumique (Vréel) du fluide de refroidissement (3) alimenté. L'invention concerne en outre un dispositif (10) correspondant pour refroidir un cylindre (1).
EP12798664.4A 2011-12-23 2012-11-29 Procédé et dispositif de refroidissement de cylindres Active EP2794136B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102011089804 2011-12-23
DE201210202340 DE102012202340A1 (de) 2011-12-23 2012-02-16 Verfahren und Vorrichtung zum Kühlen von Walzen
PCT/EP2012/073900 WO2013092152A1 (fr) 2011-12-23 2012-11-29 Procédé et dispositif de refroidissement de cylindres

Publications (2)

Publication Number Publication Date
EP2794136A1 true EP2794136A1 (fr) 2014-10-29
EP2794136B1 EP2794136B1 (fr) 2015-09-16

Family

ID=48575792

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12798664.4A Active EP2794136B1 (fr) 2011-12-23 2012-11-29 Procédé et dispositif de refroidissement de cylindres

Country Status (8)

Country Link
US (1) US9108235B2 (fr)
EP (1) EP2794136B1 (fr)
JP (1) JP5777129B2 (fr)
KR (1) KR20140088620A (fr)
CN (1) CN104169013B (fr)
DE (1) DE102012202340A1 (fr)
RU (1) RU2586375C2 (fr)
WO (1) WO2013092152A1 (fr)

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EP2881186A1 (fr) * 2013-12-09 2015-06-10 Linde Aktiengesellschaft Procédé et appareil pour isoler le froid dans un équipement cryogénique
DE102014222530A1 (de) * 2014-05-05 2015-11-05 Sms Group Gmbh Bandabweiser und Walzenanordnung
DE102014224318A1 (de) * 2014-11-27 2016-06-02 Sms Group Gmbh Vorrichtung und Verfahren zum Kühlen einer Rolle
DE102015210680A1 (de) 2015-06-11 2016-12-15 Sms Group Gmbh Verfahren und Vorrichtung zum Regeln eines Parameters eines Walzgutes
CN104923563B (zh) * 2015-06-12 2016-08-24 山西太钢不锈钢股份有限公司 热连轧精轧冷却水非对称偏差控制方法
CN105302995B (zh) * 2015-11-20 2018-10-09 沈阳黎明航空发动机(集团)有限责任公司 一种数值模拟优化叶片辊轧模具及毛坯设计的方法
DE102016223131A1 (de) * 2016-09-06 2018-03-08 Sms Group Gmbh Vorrichtung und Verfahren zum Aufbringen eines flüssigen Mediums auf eine Walze und/oder auf ein Walzgut und/oder zum Entfernen des flüssigen Mediums
EP3308868B1 (fr) * 2016-10-17 2022-12-07 Primetals Technologies Austria GmbH Refroidissement d'un rouleau d'une cage de laminoir
BE1025125B1 (fr) * 2017-09-04 2018-10-31 Centre de Recherches Métallurgiques asbl-Centrum voor Research in de Metallurgie vzw Essuyeur sans contact et installation industrielle comportant un tel essuyeur

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KR20140088620A (ko) 2014-07-10
JP5777129B2 (ja) 2015-09-09
EP2794136B1 (fr) 2015-09-16
CN104169013B (zh) 2016-03-16
US20150013405A1 (en) 2015-01-15
RU2586375C2 (ru) 2016-06-10
RU2014130217A (ru) 2016-02-20
CN104169013A (zh) 2014-11-26
WO2013092152A1 (fr) 2013-06-27
JP2015502262A (ja) 2015-01-22
DE102012202340A1 (de) 2013-06-27
US9108235B2 (en) 2015-08-18

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