EP3525948A1 - Refroidissement d'un cylindre d'une cage de laminoir - Google Patents

Refroidissement d'un cylindre d'une cage de laminoir

Info

Publication number
EP3525948A1
EP3525948A1 EP17791968.5A EP17791968A EP3525948A1 EP 3525948 A1 EP3525948 A1 EP 3525948A1 EP 17791968 A EP17791968 A EP 17791968A EP 3525948 A1 EP3525948 A1 EP 3525948A1
Authority
EP
European Patent Office
Prior art keywords
coolant
cooling
cooling device
roller
roll
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.)
Withdrawn
Application number
EP17791968.5A
Other languages
German (de)
English (en)
Inventor
Alois Seilinger
Erich Opitz
Lukas PICHLER
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.)
Primetals Technologies Austria GmbH
Original Assignee
Primetals Technologies Austria GmbH
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 Primetals Technologies Austria GmbH filed Critical Primetals Technologies Austria GmbH
Publication of EP3525948A1 publication Critical patent/EP3525948A1/fr
Withdrawn legal-status Critical Current

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
    • 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

  • Cooling of a Roll of a Rolling Mill The invention relates to a cooling device for cooling a roll of a roll stand.
  • Roll stands for rolling rolling stock have rolls which are cooled with a cooling liquid, usually with cooling water.
  • Cooling shells by means of which they are under low pressure
  • Coolant is applied to rolls of a rolling stand.
  • JP H06-170420 (A) discloses a cooling apparatus for cooling work rolls of a rolling mill which has a stationary spray bar which is slightly narrower than the narrowest band produced by the respective rolling stand and axially displaceable spray bars for cooling only those
  • Sections of the work rolls, which correspond to the width of the currently rolled strip has.
  • JP S59-156506 A discloses a method for cooling a work roll of a rolling mill, in which cooling water is sprayed onto the work roll instead of with high pressure and with a simultaneously increased application area.
  • WO 2014/170139 AI discloses a spray bar for cooling of rolling stock, which extends transversely to the transport direction of the rolling stock and has a central region and two edge regions, in each of which a cooling medium is separately fed.
  • the invention has for its object to provide an improved cooling device for cooling a roll of a roll stand.
  • the chilled beam has a plurality of full-jet nozzles, which run on one of the roller and parallel to a roll axis of the roller
  • Output side of the cooling bar are arranged. Through each full-jet nozzle, a coolant jet of the coolant with a nearly constant jet diameter can be output from the cooling beam in an output direction to the roll.
  • a full-jet nozzle is understood to be a nozzle through which a substantially straight coolant jet having a virtually constant jet diameter can be dispensed.
  • Full-jet nozzles produce a higher impact pressure on the roller than commonly used flat-jet nozzles due to the concentrated discharge of the coolant at the same coolant pressure in the cooling beam.
  • the higher impact pressure has a positive effect on the cooling effect directly on the
  • Coolant film with a thickness of typically several millimeters to centimeters, which of the impinging coolant jets should be pierced as completely as possible in order to achieve a good heat dissipation. Due to the high impact pressure of the coolant jets on the roller produced by the full jet nozzles, in comparison to the use of flat jet nozzles
  • Coolant pressure in the chilled beam can be significantly reduced, whereby the energy consumption and operating costs of the cooling device can advantageously be significantly reduced.
  • the distance of the spray bar from the roll in a wide range is not critical and therefore does not have to be adapted to the roll diameter.
  • the roll surface to be cooled can be between 50 mm and 500 mm, without the cooling effect of the coolant jets changing appreciably.
  • An embodiment of the invention provides that the
  • Coolant chambers for receiving coolant is divided.
  • Each coolant chamber corresponds to a portion of the discharge side of the cooling beam, in which a plurality of full-jet nozzles are arranged, through each of which a coolant jet from the coolant chamber to the roller can be dispensed.
  • Subdivision of the cooling beam into a plurality of separate coolant chambers, which correspond to different subregions of the discharge side of the cooling beam, advantageously makes it possible to control the cooling effect of the subregions independently of one another by applying the coolant pressures in the subregions and thereby of the subregions
  • a further embodiment of the aforementioned embodiment of the invention provides that a first coolant chamber corresponds to a first subregion of the output side of the cooling beam, the first subregion
  • the first subregion has, for example, the shape of a
  • Embodiment of the first portion takes into account that the roller is usually also heated symmetrically to the central axis.
  • Partial area parallel to the central axis along the direction of the roll axis with a maximum extent along the central axis takes into account that the roll is heated in the middle in the middle most and decreases the heating of the roll to its edge regions.
  • the corresponding design of the first subarea therefore makes it possible to adapt the roller cooling through the first subarea of the location-dependent thermal loading of the roller.
  • a further embodiment of the invention provides that each coolant chamber is connected to a coolant supply line for feeding coolant into the coolant chamber, wherein the coolant supply line opens into the coolant chamber substantially perpendicular to the discharge direction of the coolant. The essentially vertical to the output direction
  • Mouths of the coolant supply lines in the cooling beam allow a substantially uniform pressure distribution of the coolant inside each coolant chamber. This will be advantageous avoided a pressure gradient between close to the mouth and muzzle remote full jet nozzles.
  • a further embodiment of the invention provides that the amounts of coolant fed into the coolant chambers are independently controllable by a respective control valve and / or by one pump. This allows the above-mentioned independent control of the cooling effect of the individual
  • Coolant chambers issued coolant jets.
  • Controlling the amounts of coolant through control valves for example, particularly advantageous if an already existing, conventional coolant supply system can be used on the relevant rolling mill, for example, a water supply system that usually promotes cooling water with a pressure of 4 bar. In this case, it is possible to dispense with a complicated and expensive pressure increase system for supplying the roll cooling.
  • a water supply system that usually promotes cooling water with a pressure of 4 bar. In this case, it is possible to dispense with a complicated and expensive pressure increase system for supplying the roll cooling.
  • Roll breaks or rolling campaigns where only a small amount of cooling power is required to shut down individual pumps or reduce the power of the pumps and thereby reduce the flow rate
  • Coolant chambers supplied quantities of coolant before This advantageously can be controlled automatically from the coolant chambers to the roller output volume flows of the coolant to the volume flows of a
  • Adjust temperature distribution on the roll surface The quantities of coolant fed into the coolant chambers are controlled by the automation system, preferably by controlling the abovementioned control valves and / or pumps.
  • a further embodiment of the invention provides that a nozzle spacing along one another to the roll axis
  • a central region of the output side of the cooling beam least.
  • Embodiments of the invention also make it possible to adapt the arrangement of the full-jet nozzles to the location-dependent thermal loading of the roll surface, by adjusting the nozzle spacing along a direction parallel to the roll axis
  • Output side of the cooling beam takes into account that the middle area of the roll surface is usually thermally stressed most.
  • a further embodiment of the invention provides that the full-jet nozzles are arranged in several mutually parallel nozzle rows. This allows an advantageous
  • a further embodiment of the invention provides that the cooling beam for each jet nozzle has a nozzle recess in which the jet nozzle is releasably secured. This embodiment of the invention advantageously allows easy replacement of defective full jet nozzles.
  • Scrapers for stripping coolant from the roller wherein the scraper and the cooling beam are pivotable together.
  • a scraper can be advantageously prevented that too much coolant to the rolling stock and / or in a roll gap, through which the rolling stock is guided between two rollers passes, and for example, a lubricant to reduce the friction between the rolling stock and the Washes off rolls. Due to the common pivoting of the scraper and the cooling beam is advantageously no additional device for moving the cooling beam
  • the invention is also particularly suitable as a retrofit solution for existing rolling mills with scrapers, for example, only the conventional
  • a rolling stand according to the invention comprises a roller and two cooling devices according to the invention, the two being
  • Cooling devices are arranged on different sides of the roller.
  • FIG. 2 shows a schematic perspective view of a first embodiment of a cooling beam
  • FIG. 3 shows volume flows of a coolant as a function of a position from the cooling beam illustrated in FIG. 2
  • FIG. 4 shows the output side of a second embodiment of a cooling bar
  • FIG. 6 shows the output side of a fourth exemplary embodiment of a cooling beam
  • FIG. 7 shows the output side of a fifth exemplary embodiment of a cooling beam
  • FIG 11 shows the output side of a ninth embodiment of a cooling bar
  • FIG 12 the output side of a tenth embodiment of a cooling bar.
  • FIG. 1 schematically shows a rolling stand 1 for rolling a rolling stock 3.
  • the rolling stand 1 comprises two rolls 5 designed as working rolls and two for each roll 5
  • Cooling devices 7, which are arranged on different sides of the roller 5.
  • the rollers 5 are spaced from each other by a nip 9 through which the rolling stock 3 is passed in a rolling direction 11 to the rolling stock. 3 reshape.
  • Each cooling device 7 comprises a cooling beam 13 and a scraper 15.
  • Each chilled beam 13 is for receiving and outputting a
  • the cooling beam 13 has a plurality of full-jet nozzles 21 arranged on one of the respective rollers 5 and parallel to a roller axis 17 of the roller 5, the discharge side 19 of the cooling beam 13, through each one
  • Output direction 23 can be output to the roller 5.
  • Coolant is in the chilled beam 13 via
  • Control valves 43 and / or by pumps 45 which are for example frequency-controlled, are controllable.
  • the coolant is, for example, water.
  • Each scraper 15 is designed to scrape off coolant from the respective roller 5 and to pivot towards the roller 5 and away from the roller 5.
  • the coolant is, for example, water.
  • FIG. 2 shows a schematic perspective view of a first embodiment of a cooling bar 13 for dispensing coolant on a roller 5.
  • the cooling beam 13 is divided into three separate coolant chambers 25 to 27 for receiving coolant.
  • Coolant chamber 25 to 27 corresponds to a
  • Output side 19 has the shape of a rectangle with two to the Roll axis 17 parallel longitudinal sides 33, 34 and two perpendicular transverse sides 35, 36th
  • a first coolant chamber 25 corresponds to a first portion 29 of the discharge side 19 of the cooling bar 13, which forms a central region of the discharge side 19.
  • the first portion 29 is mirror-symmetrical to one of the
  • Roll axis 17 vertical central axis 37 of the discharge side 19 of the cooling beam 13 and has the shape of a trapezoid, the two vertices lying on a first longitudinal side 33, and two vertices, which lie respectively on an end point of the second longitudinal side 34.
  • the full-jet nozzles 21 are arranged on the output side 19 in a plurality of rows of nozzles 39, each extending parallel to the roll axis 17. It varies in each
  • Nozzle row 39 a nozzle spacing d adjacent to each other
  • Output side 19, for example, parabolic increases.
  • the nozzle spacing d varies for example between 25 mm and 50 mm.
  • Nozzle rows 39 extend equidistantly over substantially the entire extent of the discharge side 19, so that they produce a relatively uniform cooling effect on the roll surface of the roll 5.
  • Embodiment provides that the nozzle rows 39 are arranged offset from one another, so that the
  • Full jet nozzles 21 of different nozzle rows 39 are not arranged along the roll axis 17 perpendicular directions. This advantageously a particularly uniform cooling effect of the nozzle rows 39 is achieved by perpendicular to the rows of nozzles 39 extending "cooling grooves" are avoided, in which no coolant is discharged to the roller 5 and thereby the cooling effect is reduced.
  • full jet nozzles 21, which are located very close to or on a boundary line between two adjacent subregions 29 to 31 in FIG. 2, are either completely omitted or displaced relative to the arrangement shown in FIG. 2 into one of the adjoining subregions 29 to 31 along such a boundary line a corresponding subdivision of the interior of the
  • Each jet nozzle 21 is detachable, for example by a screw connection, in a nozzle recess of the
  • Cooling bar 13 mounted.
  • the full jet nozzles 21 each have, for example, a nozzle cross section with a minimum diameter of about 4 mm.
  • Each coolant chamber 25 to 27 is connected to a
  • Coolant supply line 41 for feeding coolant into the coolant chamber 25 connected to 27, wherein the
  • Coolant supply line 41 opens into the coolant chamber 25 to 27 substantially perpendicular to the discharge direction 23 of the coolant.
  • the cross sections of the coolant supply lines 41 for example, each have a diameter between 100 mm and 150 mm.
  • Coolant chambers 25 to 27 fed quantities of coolant are independent of each other by one (not shown in Figure 2) control valve 43 and / or by a respective (not shown in Figure 2) pump 45 controllable. This advantageously makes it possible for the quantities of coolant discharged from the coolant chambers 25 to 27 to cope with the different thermal loads in different regions of the coolant
  • FIG. 3 shows by way of example three of that in FIG. 2
  • the rated current is the value of a first volume flow Vi at a middle position y m .
  • the first volume flow Vi is generated when in all three coolant chambers 25 to 27
  • Coolant chambers 25 to 27 matching nominal pressure is fed.
  • Volume flow Vi is the increase of the nozzle pitch d of the full-jet nozzles 21 along the nozzle rows 39 from their center to the two ends to twice the value, assuming a parabolic increase of the nozzle pitch d.
  • a second volume flow V 2 is generated when in the first coolant chamber 25 coolant with a coolant pressure which is about twice as large as the nominal pressure is fed and in the other two coolant chambers 26, 27 each coolant with a coolant pressure, which is about half is large as the nominal pressure is fed.
  • a third volumetric flow V 3 is generated when coolant is fed into the first coolant chamber 25 with a coolant pressure which is approximately half the nominal pressure, and into the other two coolant chambers 26, 27 in each case
  • Coolant with a coolant pressure that is about twice the nominal pressure is fed.
  • FIG. 3 shows that through different coolant pressures in the coolant chambers 25 to 27, volume flows Vi, V 2 , V 3 can be generated with a different dependence on the position y along a direction parallel to the roll axis 17, so that the output from the chilled beam 13
  • FIGS. 4 to 12 each show the output side 19 of a further exemplary embodiment of a cooling beam 13. These exemplary embodiments differ from the exemplary embodiment illustrated in FIG. 2 only in terms of the shape and number of the coolant chambers 25 to 27 and the corresponding subregions 29 to 31 of FIG.
  • the full-jet nozzles 21 are each arranged as in the exemplary embodiment shown in Figure 2 from a plurality of rows of nozzles 39, along which the nozzle spacing d increases from the center to the two ends. Therefore, the full jet nozzles 21 are not shown again in FIGS. 4 to 12. Due to the to that in Figure 2
  • the distribution of full jet nozzles 21 on the output side 19 can be with each of the illustrated in Figures 4 to 12
  • Embodiments like the exemplary embodiment illustrated in FIG. 2, each have three coolant chambers 25 to 27 and corresponding subregions 29 to 31 of FIG.
  • FIG. 4 shows an embodiment in which the first portion 29 has the shape of a trapezoid, the two
  • Corner points which lie on a first longitudinal side 33, and two corner points, which lie on the second longitudinal side 34 has.
  • Figure 5 shows an embodiment in which the first portion 29 has the shape of a triangle, the one
  • Corner point which lies in the intersection of the central axis 37 with the first longitudinal side 33, and two corner points, which lie on the end points of the second longitudinal side 34 has.
  • Figure 6 shows an embodiment in which the first portion 29 has the shape of a triangle, the one
  • Section 29 has the shape of a rectangle whose vertices lie on the long sides 33, 34. In this
  • an output of coolant can be generated only from a central region of the output side 19, by no over the two outer portions 30, 31
  • Coolant is discharged. This is suitable for this
  • Figure 8 shows an embodiment in which the second
  • Section 30 and the third portion 31 each have the shape of a rectangle having a corner on the first longitudinal side 33, a corner point which lies on an end point of the first longitudinal side 33, and a corner point which lies on a transverse side 35, 36 ,
  • Figure 9 shows an embodiment in which the first portion 29 has the shape of a hexagon, the two Corner points on the first longitudinal side 33, two corner points, each lying on an end point of the second longitudinal side 34, and each having a corner point on each transverse side 35, 36 has.
  • Figure 10 shows an embodiment in which the first portion 29 has the shape of a pentagon, the one
  • Corner point which lies in the intersection of the central axis 37 with the first longitudinal side 33, two corner points, each lying on an end point of the second longitudinal side 34, and each having a corner point on each transverse side 35, 36.
  • Subregions 29 are mirror-symmetrical to a central axis 37, which is perpendicular to the roll axis 17, of the output side 19 of the cooling beam 13.
  • Figure 11 shows an embodiment in which a first portion 29 has the shape of a triangle, the one
  • Figure 12 shows an embodiment in which a first portion 29 has the shape of a pentagon, the one
  • Corner point which lies on the central axis 37, two corner points, each lying on an end point of the second longitudinal side 34, and each having a corner point on each transverse side 35, 36 has.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Metal Rolling (AREA)
  • Control Of Metal Rolling (AREA)
  • Nozzles (AREA)

Abstract

L'invention concerne un dispositif de refroidissement (7) permettant de refroidir un cylindre (5) d'une cage de laminoir (1). Le dispositif de refroidissement (7) présente une barre de refroidissement (13) recevant et distribuant un fluide de refroidissement, la barre de refroidissement présentant plusieurs buses à jet plein (21) qui sont agencées sur un côté distribution (19) de la barre de refroidissement (13) tourné vers un des cylindres (5) et parallèle à un axe (17) du cylindre (5), par lesquelles un jet de fluide de refroidissement présentant un diamètre de jet à peu près constant peut respectivement être distribué à partir de la barre de refroidissement (13) vers le cylindre (5) dans une direction de distribution (23).
EP17791968.5A 2016-10-17 2017-10-12 Refroidissement d'un cylindre d'une cage de laminoir Withdrawn EP3525948A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP16194099.4A EP3308868B1 (fr) 2016-10-17 2016-10-17 Refroidissement d'un rouleau d'une cage de laminoir
PCT/EP2017/076000 WO2018073086A1 (fr) 2016-10-17 2017-10-12 Refroidissement d'un cylindre d'une cage de laminoir

Publications (1)

Publication Number Publication Date
EP3525948A1 true EP3525948A1 (fr) 2019-08-21

Family

ID=57137949

Family Applications (2)

Application Number Title Priority Date Filing Date
EP16194099.4A Active EP3308868B1 (fr) 2016-10-17 2016-10-17 Refroidissement d'un rouleau d'une cage de laminoir
EP17791968.5A Withdrawn EP3525948A1 (fr) 2016-10-17 2017-10-12 Refroidissement d'un cylindre d'une cage de laminoir

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP16194099.4A Active EP3308868B1 (fr) 2016-10-17 2016-10-17 Refroidissement d'un rouleau d'une cage de laminoir

Country Status (7)

Country Link
US (1) US11338339B2 (fr)
EP (2) EP3308868B1 (fr)
JP (1) JP6828152B2 (fr)
CN (2) CN109843458B (fr)
MX (1) MX2019004413A (fr)
RU (1) RU2726525C1 (fr)
WO (1) WO2018073086A1 (fr)

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US10010282B2 (en) 2015-07-24 2018-07-03 Kurin, Inc. Blood sample optimization system and blood contaminant sequestration device and method
WO2018125929A1 (fr) 2016-12-27 2018-07-05 Kurin, Inc. Système d'optimisation d'échantillon de sang et dispositif et procédé de séquestration de contaminant du sang
US11617525B2 (en) 2017-02-10 2023-04-04 Kurin, Inc. Blood contaminant sequestration device with passive fluid control junction
US10827964B2 (en) 2017-02-10 2020-11-10 Kurin, Inc. Blood contaminant sequestration device with one-way air valve and air-permeable blood barrier with closure mechanism
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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
EP4212259A1 (fr) * 2022-01-18 2023-07-19 Primetals Technologies Austria GmbH Réduction des défauts de surface lors du laminage de finition du feuillard à chaud

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Also Published As

Publication number Publication date
US11338339B2 (en) 2022-05-24
EP3308868A1 (fr) 2018-04-18
RU2726525C1 (ru) 2020-07-14
WO2018073086A1 (fr) 2018-04-26
CN114535300A (zh) 2022-05-27
JP2019534792A (ja) 2019-12-05
EP3308868B1 (fr) 2022-12-07
CN109843458B (zh) 2022-06-17
JP6828152B2 (ja) 2021-02-10
CN109843458A (zh) 2019-06-04
MX2019004413A (es) 2019-08-05
US20190308233A1 (en) 2019-10-10

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