WO2010099925A1 - Procédé et dispositif de refroidissement pour refroidir les cylindres d'une cage de laminoir - Google Patents

Procédé et dispositif de refroidissement pour refroidir les cylindres d'une cage de laminoir Download PDF

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Publication number
WO2010099925A1
WO2010099925A1 PCT/EP2010/001275 EP2010001275W WO2010099925A1 WO 2010099925 A1 WO2010099925 A1 WO 2010099925A1 EP 2010001275 W EP2010001275 W EP 2010001275W WO 2010099925 A1 WO2010099925 A1 WO 2010099925A1
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WO
WIPO (PCT)
Prior art keywords
cooling
pressure
roll
low
shell
Prior art date
Application number
PCT/EP2010/001275
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German (de)
English (en)
Inventor
Jürgen Seidel
Matthias Kipping
Rolf Franz
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.)
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Application filed by Sms Siemag Ag filed Critical Sms Siemag Ag
Publication of WO2010099925A1 publication Critical patent/WO2010099925A1/fr

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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

Definitions

  • the invention relates to methods and a cooling device for cooling the Wa zen, in particular the work rolls of a rolling mill.
  • the rollers involved in the rolling process are heated. To protect them from damage and to obtain as long as possible, the rollers are cooled.
  • Cooling systems are nowadays used in most rolling mills, which spray a cooling liquid onto the roll surface with the aid of nozzles (preferably flat-jet nozzles). Such cooling is referred to as spray cooling.
  • the selected pressure level is between 6 bar and 12 bar and, in exceptional cases, 20 bar.
  • the work roll cooling to keep the roller of dirt, oxide and scale particles free.
  • the cooling effect increases with higher coolant quantity and increasing coolant pressure. Disadvantage of the system is that it requires a large amount of energy and at higher pressure, the maintenance of the pump is more complex.
  • WO 2008/104037 A1 discloses a cooling device with highly turbulent cooling in the low-pressure region, in which a roll is cooled by means of nozzles or bores arranged on a concave cooling beam.
  • the cooling device works satisfactorily and reproducibly only when the diameter range of the roller resulting from the grinding is matched to the curvature of the cooling device.
  • the number of cooling devices required for different roller diameters which necessitates a sophisticated roller logistics, is necessary.
  • a low pressure cooling in the form of a flow cooling is described in DE 36 16 070 C2, wherein in a defined relatively narrow gap between the work roll surface and a cooling shell, the cooling liquid is guided in a directed manner and with external pressure on the roll surface.
  • the pressure level is lower and depends on the gap width and flow speed. Higher cooling effects are achieved here by higher flow velocities. Due to the lower pressure level, the system has no cleaning effect on the roll surface.
  • a disadvantage of this device is that a separate cooling block is necessary for each roller, since this is mounted on the roll chocks. For a conventional hot rolling mill, therefore, a large number of these cooling blocks is required.
  • the adaptation of the gap width to different work roll diameter and the consequences of the cooling block of the respective work roll position has also proved to be disadvantageous or very complicated, since the adjustment of the gap must be done manually and outside of the rolling mill.
  • rollers are cooled at least two partial areas along its circumference with the cooling liquid (7), wherein the partial areas by at least two cooling shell segments of the cooling shell, which are opposite one another and are connected to the regions of the roll surface, are represented.
  • the articulation axis of the articulated connection is preferably parallel to the longitudinal axis of the roller.
  • the rolls are also subjected to high-pressure cooling at the same time as the low-pressure cooling, the rolls being sprayed directly with a high-pressure cooling liquid during the high-pressure cooling.
  • the cooling liquid can be taken from a high tank, for example 7-12 m high, or generated directly by low-pressure pumps.
  • the required Pressure range for the cooling liquid of the low pressure roller cooling depends on the thermal load of the rollers and is between z. B. 0.5 to less than 5 bar.
  • a spray cooling, coolant curtain, gap cooling or flow cooling, highly turbulent cooling, or a combination of different low pressure systems can be used.
  • a single-row or double-row spray nozzle beam can be used, as in conventional systems.
  • the small amount of cooling liquid of about 20% of the total amount of cooling liquid is sufficient for this task, wherein a pressure range for the cooling liquid between 5 - 50 bar, preferably 12 bar is required.
  • the pressure range used for the cooling liquid of the high-pressure roll cooling depends on the rolling parameters thickness reduction, specific surface pressure in the roll gap, rolling speed, strip temperatures, roll material and rolled material.
  • the pressure level can be increased accordingly.
  • the roll surface can be observed to derive therefrom the pressure level change.
  • the pressure level can be adjusted individually in steps (for example by switching on or off of pumps) or steplessly.
  • the combined low-pressure high-pressure cooling is provided for example for the front stands of a hot strip mill. In the rear scaffolds, a pure low-pressure cooling can then be used.
  • the high pressure chilled beam can operate over almost the entire length of the bale or be movable in the width direction and with a localized cooling effect. If only a simple low-pressure shell cooling is used in an application, then a combination with the cooling according to the Japanese Patent Application JP 07290120 conceivable and provided. Here, with the help of an engine, two spray nozzle beam sections are moved axially or in the width direction, and the work roll is locally cooled differently.
  • an electric or hydraulic motor with threaded rod or according to two motors for separate adjustment on the left and right side are preferably alternatively also a hydraulically moving single or multi-link articulated rocker with spray bars mounted thereon or rotatable nozzle units executable to the coolant jets on the desired areas To steer the work roll (inside or next to the band area) to positively influence the band profile and the flatness.
  • short segment shell parts with a width of, for example, 150 mm can be axially adjustable in the width direction and only locally (eg symmetrically at two points of the work roll) for a segment of the low-pressure shell cooling be effective.
  • the low-pressure work roll cooling used in the invention has the task optimally and efficiently to cool, despite the low coolant pressure, the cooling effect (heat transfer from the roller to the coolant) should be high. This causes a lower roll temperature or can be used to reduce the amount of cooling liquid.
  • a flow cooling is preferably used, in which the cooling liquid is conducted in front of the roll surface in a relatively narrow gap between the work roll and an arc-shaped cooling shell.
  • the cooling device consists essentially of articulated interconnected movable cooling shell segments.
  • three, but usually two cooling shell segments are used. In special cases, however, only one cooling shell segment can be used.
  • the individual cooling shell segments preferably have laterally or on whose ends are joints or joint halves. At least one pivot point is present on the middle cooling-plate segment, which receives at least one, preferably two cylinders (hydraulic or pneumatic cylinders).
  • the cylinders have their second breakpoint on the other members of the adjacent cooling shell segments.
  • the cylinders can be arranged in the middle of the cooling beam or at the edges on both sides.
  • an adjustment with, for example, hydraulic motors or electric motors is conceivable.
  • the console or the cooling beam support with mounting holes On the middle cooling shell segment is the console or the cooling beam support with mounting holes. It is possible to move the middle cooling-plate segment and thus all components connected to it via the cooling-beam carrier, whereby a horizontal, vertical and rotating movement is possible.
  • the position adjustment is carried out with a multi-link linkage, which is operated pneumatically, hydraulically or electromechanically. Also, an advantageous employment of the central cooling beam carrier in the horizontal direction over, for example, a longitudinal or slot guide and pneumatic or hydraulic cylinder is possible.
  • the cylinders have position measuring systems and pressure transmitters.
  • the position of the cylinders and thus the gap setting or distance determination between the cooling shell segment and roller as well as the monitoring of the set positions can be determined and carried out in the following different ways, whereby a combination of the mentioned methods is also possible:
  • the cooling beam support position and the cooling shell segments with the associated cylinders and joint drives are pressed against the roll with a defined pressure.
  • the position encoders are set to zero. Based on this and with knowledge of the geometric relationships, a defined gap between the cooling shell segments and ment and roller are adjusted.
  • the calibration process of the cooling system may be performed during the framework calibration procedure.
  • the shell position or average gap width can be calculated to a good approximation. Any relative change in roll position (for example, tape thickness change) during the rolling process is thus convertible.
  • the gap can be measured directly and the cylinders and linkages adjusted accordingly with a control system.
  • the cooling device according to the invention adapts to the respective roller diameter and roller positions because the adjusting systems of the cooling beams are connected to the thickness control and follow the vertical movement of the work rolls, for example in the case of a thickness changeover , When driving up the scaffolding (for example, in an emergency on) the cooling shells are automatically pivoted back slightly.
  • the cooling device forms in a structural embodiment by means of a sealing function a space from which only a small amount of cooling liquid enters the environment.
  • the seal is made by conditioning the shell at the top and bottom of the work roll, which can be pressed with a predetermined pressure and / or by applying a dynamic pressure on the edge of the cooling shells.
  • the cooling bars can be fixed with cooling shells and conventional high and / or low pressure spray bars.
  • a gap is formed through which the coolant flows.
  • the gap widths between the cooling shell and the work roll are adjusted in a targeted and reproducible manner during operation, independently of the roll diameter, between 2 and 40 mm, for example to 5 mm.
  • the gap between the work roll and the cooling shell can be approximately equal to -tangential- or the shell is made narrowing toward the outlet.
  • the sectional flow cooling is divided into sections.
  • the cooling liquid flows from an eg funnel-shaped rectangular slot into the individual regions of the cooling shell against the roll and is deflected to either side (upwards or downwards) or even only to one side, whereby the cooling shell forces a flow along the roll.
  • the cooling liquid absorbs the heat of the roller efficiently.
  • the heated coolant then flows backwards making room for new cold coolant.
  • the chilled beams are designed in such a way that the cooling liquid flowing to the rear (away from the roller) can flow off well, especially on slopes.
  • baffles the returning coolant on the upper side is additionally directed to the side in order to reduce the pool effect over the wiper.
  • the individual cooling areas are separated from each other by mutual shielding so that the cooling liquids of the adjacent cooling bars hardly interfere with each other.
  • the cooling liquid is passed over a larger contiguous angular range of the roller.
  • a low adaptable gap width and high flow velocity are required to produce good heat transfer.
  • the gap width and cooling liquid quantity must therefore be coordinated.
  • the contiguous flow cooling can be operated in countercurrent or DC principle. Due to the long path between inlet and outlet side, a lateral sealing of the cooling shell is required.
  • an operating mode can also be carried out in which the cooling liquid is supplied to the upper and lower cooling beam pipelines. The process is then targeted to the pages.
  • the cooling fluid flowing tangentially to the roller absorbs the heat and is then deflected to the side.
  • the warm coolant heats the roller areas next to the belt running area and leads there to the desired positive influence of the thermal crowns.
  • This system is particularly effective when zone cooling is performed, where the areas next to the belt are not directly cooled.
  • a calculation model (process model or level 1 model) is used that fulfills the following tasks: - Adjustment of the coolant quantity and pressure level for the low pressure and possibly for the high pressure part depending on strip thickness decrease, specific surface pressure in the nip, rolling speed, strip temperatures, roll material and rolled material and the measured and / or calculated roller temperatures and / or observed roll surface and also dependent on the set
  • Fig. 2 is a highly turbulent flow cooling device according to the
  • FIG. 3 shows a cooling device according to the invention with a plurality of cooling shell segments, which are hinged together,
  • FIG. 4 shows the cooling device of FIG. 3 with an alternative coolant flow
  • Fig. 5 shows a cooling device according to the invention with radially divided
  • FIG. 7 shows a cooling device with cooling shell segments pressed on by springs
  • FIG. 8 shows a cooling device with roll gap cooling / roll gap lubrication and combined low-pressure high-pressure roll cooling
  • Fig. 16 bending springs as articulated / elastic connection between adjacent cooling shell segments.
  • FIG. 1 shows a prior art spray cooling in which a cooling liquid 7 is sprayed by means of nozzles 27 onto the roll surface of the work rolls 1, 2. Due to the relatively large distance between nozzle and roller, a higher coolant pressure range (eg 6 ... 15 bar) selected. Inlet and outlet side arranged scrapers 17 ensure that as little as possible cooling liquid can come into contact with the rolling stock 4.
  • FIG. 2 shows another known possibility for cooling the work rolls 1, 2. This is a highly turbulent cooling in the low-pressure range. Water is sprayed onto the roll surface of the work rolls 1, 2 with the aid of nozzles 27 arranged on the inlet side and through the holes introduced in the concavely curved contiguous cooling shell 11, and a water cushion with a turbulent and undirected flow is formed in front of the work roll. The replacement of the water is relatively slow in this construction, which adversely affects the cooling efficiency.
  • FIG. 1 A coherent flow cooling according to the invention with a coherent cooling shell 11 is shown in FIG.
  • the cooling device 10 essentially consists of cooling shell segments 13 connected in an articulated manner, which enclose the work roll 1, 2 at a distance, forming a gap 30 in a larger angular range. Via a feed tube 25 and the inlet opening 29, the cooling liquid 7 flows in countercurrent to the rolling direction 5 in the gap 30 to then flow through the outlet opening 24 and the discharge pipe 26 again. If the discharge pipe 26 or the outlet opening 24 is closed or not carried out in a special case, it is possible to selectively generate a coolant outlet transverse to the roll. Side seals are then only partially available here.
  • the segment lengths of the cooling-cup segments 13 forming the gap 30 should be approximately the same, so that when the diameter of the work-roll 1 changes, the cooling-cup segments 13 can follow the change in curvature of the roll-jacket surface 6 optimally.
  • the individual cooling-cup segments 13 have at their ends joints or joint halves which, connected to one another, form a corresponding number of pivot pivots 22 and pivot points 21, which are connected to one another by cylinders 20, for example hydraulic or pneumatic cylinders.
  • the cooling beam support 16 On the middle cooling Lensegment 13 is the cooling beam support 16 with a pivot point 23, through which it is possible, thedeschalensegmente13 and all components that are connected to this, in the illustrated (horizontal, vertical and rotating) adjustment directions 45 of the cooling beam support with a multi-membered not shown here To move linkage.
  • a stripping device 17 arranged below the cooling shell 11 ensures that as little cooling liquid 7 as possible reaches the rolling stock 4.
  • FIG. 3 An alternative flow guidance of the cooling liquid 7 within the gap 30 formed by the cooling shell segments 13 of the cooling shell 11 and the roll shell surface 6 with respect to the flow described in FIG. 3 is shown in the cooling device 10 of FIG.
  • the supply pipes 25 for the low pressure ND to be used cooling liquid 7 are arranged here respectively at the upper and lower cooling shell segment 13, so that here thedefactkeitsteilmengen in countercurrent and in cocurrent, based on the Walzencard 5, are guided through the gap 30.
  • the flow directions are indicated by arrows 43.
  • the upper and lower edges of the cooling shell 11 are formed with a contact surface 46, for example a hard tissue plate, which is sealingly guided against the roll shell surface 6.
  • each work roll 1, 2 is also cooled on the inlet side. Since the achievable cooling is not the main focus here ranges for. B. spray cooling with low pressure ND by means of nozzles 27th
  • FIG. 5 shows a cooling device 10 with a section-wise low-pressure flow cooling.
  • the cooling shells 11 are composed of cooling shell segments 13 but form a coherent, self-contained cooling shell 11
  • the cooling shell segments are 13 of the now radially divided cooling shell 12 are also spatially separated from each other and form separate Strömungskühl Schemee s1, s2, s3.
  • ND low pressure
  • the cooling liquid flows through a funnel-shaped discharge slot 44 in the central region of a cooling shell segment 13 from an outlet opening 24 against the work roll 1, 2 and is deflected upwards and downwards on both sides.
  • mechanical side seals can be arranged.
  • Each cooling shell segment 13 forces a flow according to the arrows 43 along the roll surface 6 and then back to the rear.
  • the cooling-cup segments 13 are designed so that the cooling liquid flowing to the rear (away from the roller) can flow off well with a gradient. By (not shown) deflecting the back-flowing cooling liquid is additionally directed on the top in addition to the side in order to reduce the pool effect on the scraper 17.
  • the outlet openings 24 of the cooling-plate segments 13 can be provided with an exchangeable mouthpiece (for example a rectangular nozzle) so that, if required, the cross-section and the shape can be adapted to slightly changed conditions.
  • high pressure (HD) nozzles are arranged in this embodiment, by means of which the inventions According to the combined low pressure high pressure cooling is realized.
  • the high-pressure spray bar can be arranged separately on the cooling beam carrier 16 or attached to a cooling shell segment, so that it can be adjusted with it.
  • cooling shells of a flow cooling area can also be divided into two, so that the outlet opening 24 can be easily adjusted by relative displacement and subsequent fixing of the two halves. Furthermore, slightly different shell thicknesses or gap widths per cooling beam can be set and the amount of coolant flowing upwards and downwards can be influenced.
  • the cooling beam support 16 is positioned with the middle cooling shell segment 13 in front of the roll.
  • the other two cooling-plate segments 13 are laid against the work rolls 1, 2 with the aid of a straight or curved crossbar 48, which can be rotated in a small defined area, with a corresponding spring contact pressure of the spring 8.
  • coil springs 8 with corresponding holders can be attached to the ends.
  • the gap 30 is determined by spacer plates 49 between the cooling shell 13 and the work roll 1, 2. As a material for the spacer plates z.
  • the spacer plates 49 are arranged only in the chilled beam edge region so as not to disturb the coolant flow in the middle.
  • Optional spacer plates 49 are also conceivable over the cooling beam length. These can be used as distance setting or for influence the flow direction of the coolant serve.
  • These spacer plates may also be mounted on the middle cooling cup segment 13 (not shown).
  • a rigid cooling system is a special case. H. provided with immobile cooling shells (without cylinders between the shells and without springs 8). Also, then advantageously use of rigid spacer rods instead of movable cylinder 20 is possible.
  • the gaps between the roller and the cooling pan then vary somewhat, but the system with the partial flow cooling is still effective and the system is easier to manufacture. It must only be positioned depending on the work roll diameter and the work roll position in front of the roller so that the gap optimally, so the outlet openings are arranged relatively close in front of the roller depending on the work roll diameter.
  • the design can be carried out the same for multiple scaffolding and the adaptation to the different framework diameter ranges of a rolling train is carried out only on the length-adjustable rods.
  • cooling device 10 of FIG. 8 in addition to the previously described combined low-pressure high-pressure cooling, there is also arranged a low-pressure flow cooling with integrated roll gap lubrication 19 and roll gap cooling 18 on the inlet side.
  • a low-pressure flow cooling with integrated roll gap lubrication 19 and roll gap cooling 18 on the inlet side.
  • FIG. 8 it is disclosed in FIG. 8 how different high-pressure and low-pressure systems can be combined with one another.
  • the flow of the cooling liquid 7 can share under a cooling shell or, as shown here for example on the inlet side and outlet side, a larger amount of coolant are preferably directed in one direction. In order to increase the heat transfer, a flow against the direction of rotation is advantageous.
  • the area in which the nip lubrication 19 is arranged, is largely kept dry by the generated flow direction of the work roll cooling and / or provided with an elastic plastic surface cooling shells 50 or cooling shells 51 with elastic plastic or hard tissue plates, including the cooling beam support mechanism, a slight contact pressure is generated over the plates on the roller.
  • the plates themselves are designed to be continuous across the width and have by their structural design (not shown) an elastic effect.
  • the area of the roll surface (seen in the direction of rotation) prior to the application of the rolling gap lubricant is optionally carried out with a (not shown) compressed air spraying in order to blow the roll surface defined dry.
  • the cooling device 10 of FIG. 9 it is also possible, according to the cooling device 10 of FIG. 9, to carry out the three chilled beams with interchangeable cooling shells 47, into which many staggered holes 52 are bored, from which individual coolant jets are blown against them from a short distance Rollers 1, 2 inject. Even so, a partial flow cooling can be established.
  • the holes are arranged offset in the width direction so that a uniform cooling effect across the width.
  • the cross-sectional size and distances of the holes 52 can be designed differently over the bale width, so that a coolant crown can also be produced with this system.
  • the holes 52 can be aligned perpendicular to the rollers 1, 2 or allow an oblique injection of the cooling liquid against the rollers 1, 2.
  • FIGS. 10a to 10f Further details on the nozzle and shell design can be found in FIGS. 10a to 10f, wherein the arrangement of the nozzle in the center of the bowl or alternatively in FIG asymmetric arrangement with one side, for example, above shortened executed shell takes place.
  • the cooling shell may additionally be provided on the side facing the rollers smoothly or with grooves or webs 9 in order to positively influence the cooling effect by causing turbulences shown:
  • Fig. 10a shows a symmetrical arrangement of the lower part of the cooling beam 54 on the cooling shell 11, 12 with replaceable nozzle 27, Fig. 10b coolant exit from the nozzle 27 with angle ⁇ oblique to the roller, Fig. 10c nozzle 27 with alternative cross-sectional shape and possible embodiments of Webs or grooves 9,
  • the funnel-shaped outlet opening formed in the flow direction can be designed with baffles in order to direct the coolant inwardly, outwardly or straightforwardly, so that ultimately a closed and uniform coolant-liquid jet emerges over the length of the cooling-bar.
  • a funnel-shaped design ofdestattkeitszu Crystalkanals to the chilled beam broadsides is possible to reduce the under the shell transverse to the side (beam edges) flowingdeunderkeitmenge.
  • the cooling shell in sections over the length of the cooling bar with a gap width adjustment in the cooling liquid feed channel and thus to control the coolant distribution and the cooling effect via the roller length to influence.
  • bendable spring plates 53 are arranged within the funnel-shaped feed channel 55 in accordance with the example of FIGS. In the normal position, the spring plates lie on the side surfaces of the outlet opening here. If the middle is turned on one side, the gap is reduced there. The edges are held in a slot guide. When the spring plate is set at the two edges, alternatively the gap width is reduced there.
  • FIG. 10e and FIG. 10f only represents the principle. Other constructions with the same effect are also possible.
  • FIGS. 11a to 11c Details for an exemplary embodiment of the gap adjustment in the feed channel 55 are shown in FIGS. 11a to 11c in a side view and in FIG. 12 in the corresponding plan view.
  • the elongated outlet cross-section 58 of the cooling bar is divided into individual width sections 59.
  • the flow opening b and thus the volume flow of the cooling liquid can be adjusted individually.
  • the width section 59 can be designed, for example, 50-500 mm wide.
  • a paired, symmetrically arranged to the frame center control of the zone cooling (gap setting) is possible.
  • All the cooling bars of a scaffold can be provided with zone-by-zone control of the cooling cross-sections and the zones can be correspondingly connected, or the individual bars of a scaffold can be controlled separately.
  • a closing mechanism of the outlet cross section a system operated with air pressure or liquid pressure is provided for the embodiment in FIG.
  • the flow opening b can be adjusted from open to partially open or closed.
  • stretchable plastic bottles 60 arranged in sections it is also possible to use rotatable or displaceable flaps or tappets, eccentric adjustments or other mechanical actuators for segment-wise influencing of the cross section of the outlet opening.
  • a pressure chamber 56 is arranged laterally on the feed channel 55 as the closure member, the expandable plastic tube 60 of which forms part of the feed channel 55.
  • the air chamber 56 In the initial state of FIG. 11a, the air chamber 56 is in the pressureless state, so that, as shown in FIG. 12 at the width section 59a, the flow opening b is fully opened.
  • the pressure chamber 56 was partially filled with compressed air or a liquid via a pressure line 57, whereby the plastic tube 60 was partially pressed into the feed channel 55 and the flow opening b is now partially closed, as in FIG. 12 at the width section 59b is shown.
  • a completely closed flow opening b is shown in FIG. 12 at the width section 59c.
  • FIG. 1 Another mode of operation of the zone cooling is shown in FIG.
  • narrow cooling shells 14 are arranged side by side in roll length, the columns 31, 32, 33 can be adjusted with different gap widths W1, W2, W3.
  • a different specific cooling liquid flow 41 per unit time over the roll length can thus be generated.
  • a barrier cooling liquid generating a dynamic pressure can be introduced into the gap 34 existing between the cooling shells 14.
  • a cooling shell without adjusting device can be designed such that the gap between the cooling shell and the roll is arbitrarily different over the length of the roll.
  • cooling shells 13,14 can be used with advantage a material which may rest against the roller without damaging it and is elastic.
  • a material which may rest against the roller without damaging it and is elastic may be, for example, a sand-free cast iron, lubricious plastic, self-lubricating metals, aluminum or hard tissue.
  • FIG. 14 shows a possibility for sealing the gap 30 formed between the work roll 1 and the cooling shell 14 at its edges.
  • a fluid jet 28 for example air or coolant, is selectively blown into the opening of the gap 30.
  • the fluid jet 28 thus generates a back pressure, which prevents the escape of the cooling liquid 7 from the gap 30.
  • FIGS. 15a and 15b A spatially acting, axially adjustable work roll spray cooling, which can be designed as high-pressure or low-pressure cooling, is shown in FIGS. 15a and 15b.
  • This cooling is an additional cooling and can be operated in combination with the low-pressure shell cooling, not shown.
  • the local positioning of the spray nozzles or application of the cooling liquid 7 preferably takes place as a function of the profile and flatness control or regulation.
  • the spray nozzle bar sections 40 ' are moved on a guide rod 63 for this purpose.
  • FIG. 15b A similar arrangement of a spatially acting work roll cooling is shown in FIG. 15b.
  • a hydraulic cylinder 61 is used here for articulated rods and articulated rockers 62 with injection nozzle beam sections 40 'attached thereto via a pivot point 66 moves on a circular path 64 and so the cooling jet 7 directed to different positions within or adjacent to the band area on the work roll 1.
  • Swing the two spray nozzle bar sections 40 ' can each be moved with a coupling gear (4-joint arc) when a movement on a circular path 64 is to be avoided.
  • the use of electric or hydro-stepping motors at the positions of the pivot points 66 for the direct movement of the nozzle units on the spray nozzle bar sections 40 'via a bar on the circular path 64 are also possible.
  • the low pressure cooling system is also alone, i. not usable in combination with the high pressure cooling system.
  • FIG. 16 shows bending springs 8 as an elastic connection between the adjacent cooling shell segments 13.

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

Abstract

L'invention vise à proposer un procédé et un dispositif de refroidissement (10) permettant de refroidir de façon optimale les cylindres (1, 2) d'une cage de laminoir, tout en tenant compte d'aspects énergétiques tels que la minimisation du flux de liquide de refroidissement nécessaire et de la pression de liquide de refroidissement, et des coûts de construction et de fabrication. A cet effet, une coquille de refroidissement (11, 12) est formée à partir d'au moins deux segments de coquille de refroidissement mobiles, reliés de façon articulée l'un à l'autre.
PCT/EP2010/001275 2009-03-03 2010-03-02 Procédé et dispositif de refroidissement pour refroidir les cylindres d'une cage de laminoir WO2010099925A1 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
DE102009011111.5 2009-03-03
DE102009011111 2009-03-03
DE102009011110.7 2009-03-03
DE102009011110 2009-03-03
DE102009014125.1 2009-03-24
DE102009014125 2009-03-24
DE102009036696.2 2009-08-07
DE102009036696 2009-08-07
DE102009053073A DE102009053073A1 (de) 2009-03-03 2009-11-13 Verfahren und Kühlvorrichtung zum Kühlen der Walzen eines Walzgerüstes
DE102009053073.8 2009-11-13

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WO2010099925A1 true WO2010099925A1 (fr) 2010-09-10

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PCT/EP2010/001274 WO2010099924A1 (fr) 2009-03-03 2010-03-02 Procédé et dispositif de refroidissement pour refroidir les cylindres d'une cage de laminoir
PCT/EP2010/001275 WO2010099925A1 (fr) 2009-03-03 2010-03-02 Procédé et dispositif de refroidissement pour refroidir les cylindres d'une cage de laminoir

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Country Link
US (1) US20120031159A1 (fr)
EP (1) EP2403663B2 (fr)
CN (1) CN102421541B (fr)
DE (2) DE102009053073A1 (fr)
RU (1) RU2483817C1 (fr)
TW (2) TW201036721A (fr)
WO (2) WO2010099924A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012219722A1 (de) 2012-05-11 2013-11-14 Sms Siemag Ag Vorrichtung zum Kühlen von Walzen
US10807134B2 (en) 2015-06-11 2020-10-20 Sms Group Gmbh Method and device for controlling a parameter of a rolled stock

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EP3599036B1 (fr) 2018-07-26 2022-06-15 Primetals Technologies Austria GmbH Cage de laminoir pourvu de dispositif de refroidissement hybride
KR20210104710A (ko) 2018-12-19 2021-08-25 타타 스틸 이즈무이덴 베.뷔. 열간 압연기용 냉각 장치
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CN114571702B (zh) * 2022-03-17 2024-03-26 广东易聚源塑业科技有限公司 一种塑料母粒加工制备系统
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CN102421541B (zh) 2014-10-29
WO2010099924A1 (fr) 2010-09-10
CN102421541A (zh) 2012-04-18
EP2403663A1 (fr) 2012-01-11
DE102009053074A1 (de) 2010-09-09
TW201036722A (en) 2010-10-16
US20120031159A1 (en) 2012-02-09
RU2011139995A (ru) 2013-04-10
RU2483817C1 (ru) 2013-06-10
DE102009053073A1 (de) 2010-09-09
EP2403663B2 (fr) 2021-03-10
TW201036721A (en) 2010-10-16

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