EP0148983B1 - Tuyère refroidie pour four à cuve - Google Patents

Tuyère refroidie pour four à cuve Download PDF

Info

Publication number
EP0148983B1
EP0148983B1 EP84107748A EP84107748A EP0148983B1 EP 0148983 B1 EP0148983 B1 EP 0148983B1 EP 84107748 A EP84107748 A EP 84107748A EP 84107748 A EP84107748 A EP 84107748A EP 0148983 B1 EP0148983 B1 EP 0148983B1
Authority
EP
European Patent Office
Prior art keywords
tuyere
difference
less
coolant
outer diameter
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.)
Expired
Application number
EP84107748A
Other languages
German (de)
English (en)
Other versions
EP0148983A1 (fr
Inventor
Hans-Günther Dr. Ing. Rachner
Joachim Dipl. Ing. Schulze-Elberg
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.)
Kuettner GmbH and Co KG
Original Assignee
Kuettner GmbH and Co KG
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 Kuettner GmbH and Co KG filed Critical Kuettner GmbH and Co KG
Priority to AT84107748T priority Critical patent/ATE31941T1/de
Publication of EP0148983A1 publication Critical patent/EP0148983A1/fr
Application granted granted Critical
Publication of EP0148983B1 publication Critical patent/EP0148983B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21B—MANUFACTURE OF IRON OR STEEL
    • C21B7/00—Blast furnaces
    • C21B7/16—Tuyéres

Definitions

  • the invention relates to liquid-cooled, in particular water-cooled, wind nozzles for coke-controlled shaft ovens, a system of spirally extending channels being arranged between the inner jacket and the outer jacket of the wind nozzle, one channel of which guides the coolant to the nozzle head and another channel of the coolant returns from the nozzle head and one between the and outer jacket arranged intermediate jacket separates the two channels.
  • the shaft furnaces include e.g. B. blast furnaces and cupola furnaces and other coke-controlled furnaces for melting or reducing raw materials.
  • Shaft furnaces consist of a mostly cylindrical furnace body. Before being tapped, the feed mixes pass through a reduction zone, melting zone and combustion or wind zone in the furnace. These zones and the furnace output are largely determined by the amount of wind (fan air). The wind is blown into the furnace through wind nozzles (blow molding) that are evenly distributed around the circumference of the furnace. The wind is fed and distributed to the wind nozzles by a wind box which surrounds the furnace in a ring. For reasons of good air distribution, it is desirable to arrange as many nozzles as possible on the circumference of the furnace.
  • the associated heat load causes the wind nozzles to be cooled.
  • the cooling takes place with water and represents a not inconsiderable source of heat loss. For this reason, the number of wind nozzles is limited in practice and the most economical possible relationship between wind distribution and heat loss is sought.
  • a particularly advantageous embodiment provides channels arranged in spirals for the water flow.
  • the water is supplied via channels that are arranged on the outer jacket of the nozzle, and the water is removed via channels that are arranged on the inner jacket.
  • the cooling water is deflected in the nozzle head without an abrupt change of direction.
  • the known nozzle is designed as a casting, in which a cast workpiece is inserted into the cavity between the inner and outer jacket, which forms the spiral channels for the water flow towards the inner and outer jacket.
  • a known wind nozzle of this type with a design that is favorable for the water flow has the disadvantage that the outer jacket determining the heat loss of the wind nozzle has relatively large dimensions because 3 thick-walled cast body surfaces are nested inside one another. Only the cast version has so far been able to withstand the extreme temperature differences at various points on the surface.
  • Wind nozzles of the type mentioned in the introduction can also be found in US-A-3 826 479, GB-A-204 262 and FR-A-559 345. However, none of these known wind jets offer a remedy for heat loss.
  • the object of the invention is therefore to create a wind nozzle with smaller dimensions in order to reduce heat losses.
  • the specified diameters refer to cylindrical wind nozzle shapes. In the case of conical wind nozzle shapes, this corresponds to the mean diameter of the wind nozzle inner jacket or wind nozzle outer jacket protruding into the furnace. In any case, compliance with the dimensions according to the invention brings about a considerable reduction in heat losses.
  • nozzle diameters according to the invention can be maintained particularly advantageously with wires as the lateral delimitation of the channels.
  • the wires can be brought into any desired spiral shape with little effort and mounted between the inner and outer sheath on one or in a smooth, preferably drawn intermediate sheath of the wind nozzle.
  • the wires and the resulting smooth intermediate sheath have much smaller dimensions than the cast intermediate piece of the known wind nozzle. With the same external dimensions of the wind nozzle, this results in larger duct cross sections in the interior. If the same duct cross-sections are retained, this can also be used to reduce the external dimensions.
  • Particularly favorable conditions arise with the use of wires with a round or triangular cross section. In the case of a triangular cross-section, the pointed cross-sectional ends each point to the outer jacket or inner jacket.
  • the outer diameter of the wind nozzle could be reduced to 190 mm. This brought a reduction in heat loss from 10 to 7%.
  • wind nozzles constructed in this way not only offer thermal advantages for furnace operation, but also further procedural advantages.
  • the wind nozzles according to the invention enable a high temperature rise in the cooling medium with appropriate water guidance, so that the heat accumulating in the cooling medium can be partially used. This significantly improves the economy of the furnace operation.
  • the water speed required for perfect heat transfer and the amount of heat to be removed determine the dimensions of the channels. Since there are hardly any design constraints, the channels can be adapted to the respective heat supply.
  • the amount of water can be controlled so that desired temperature increases occur. In particular, it is envisaged that the temperature rise will not be less than 20 ° C, so that downstream heat exchangers can be optimally used and that heat can also be used for heating the building or for other thermal engineering tasks.
  • the cooling circuit then also forms a heating circuit.
  • the wind nozzle with narrow, spirally arranged channels can also be designed in connection with a closed water circuit and a convective heat exchanger so that temperatures of the cooling medium of z. B. 80-120 ° C can be driven so that the flow of central heating can be operated directly from water to water via a heat exchanger. It is therefore also envisaged to operate the water circuit with increased pressure or to use other cooling media with evaporation temperatures above 100 ° C instead of water, while the water-cooled wind nozzles of the previously conventional design use such large amounts of water that only very small temperature increases in the cooling medium are achieved will.
  • the wind nozzle according to FIG. 1 is similar in the outer configuration to the known wind nozzle projecting into the furnace interior of a shaft furnace.
  • the water is supplied via a hollow flange-like body 1 made of steel, which is divided into two sections 2 and 3.
  • the contact surface of both sections 2 and 3 is designated 4.
  • Sections 2 and 3 are attached to each other there.
  • the lower section 3 has a connection to the spirally arranged channel system for water cooling located inside the wind nozzle.
  • Section 3 is drained of water through a connecting piece 5.
  • the connecting piece 5 lies behind the body 1 and runs parallel to the contact surface 4.
  • Section 2 is used to supply water to the duct system on the outer jacket.
  • the outflow opening is designated 7 and extends in an arc at section 2.
  • the water enters section 2 through a nozzle 6.
  • the sections 2 and 3 are welded together.
  • the nozzle connection is also cooled by the flange through which water flows.
  • the nozzle itself consists of an outer jacket 8 made of copper and an inner jacket 9 made of copper.
  • a smooth intermediate jacket 10 made of stainless steel is arranged in the cylindrical cavity between the inner jacket 9 and the outer jacket 8.
  • the jackets 8 and 10 are welded in the wind nozzle.
  • Spiral channels are between the outer jacket 8 and the intermediate jacket 10 on the one hand and between the intermediate jacket 10 and the inner jacket 9 on the other hand Spiral channels, the lateral boundary of which is formed by spiral channels, the lateral boundary of which is formed by spirally wound wires 11 and 12.
  • the wire 11 is shown enlarged in FIG. 2, has a round cross section and is located between the outer sheath 8 and the intermediate sheath 10.
  • the wire 12 is arranged between the intermediate sheath 10 and the inner sheath 9 and has the same cross section and approximately the same pitch with regard to the spiral shape.
  • the outer jacket 8 and the inner jacket 9 are welded to the nozzle head.
  • the outer jacket has an inward curvature 13 at the end to be welded and the inner jacket 9 has a thickening 14 at the corresponding end.
  • the water is deflected in a further exemplary embodiment with the inner jacket 15 and the outer jacket 16 by a head part 17, which is designed as a turned part and which is welded to the outer jacket 16 and the inner jacket 15 in the region of lower heat load.
  • the exemplary embodiment according to FIG. 3 differs by a lower inclination of the wire spirals designated there with 18 and 19.
  • the gradient of the wire spirals is between 10 and 30 °.
  • the wire thickness in the exemplary embodiment is 6 mm and is preferably between 4 and 8 mm.
  • the inner diameter of the inner jacket 15 is 130 mm.
  • the difference to the diameter of the outer jacket is less than 70 mm.
  • the parameters for the structural design are the wind nozzle set.
  • FIG. 4 shows a cross-sectional part of the wind nozzle according to FIG. 3 with an intermediate sheath and wire spirals 18 and 19 as well as outer sheath 16 and inner sheath 15.
  • drawn tube material is used for the inner and outer jacket.
  • the wind nozzles according to FIGS. 1 to 5 are each provided with a cooling circuit 35 in the exemplary embodiments, in which there are temperatures above 50 ° C., and the recooling takes place via a heat exchanger or convection cooler.
  • the general rule is that the pressure is less than 4 bar in a temperature range below 100 ° C. At temperatures of 100 ° C and more, the pressure is a maximum of 10 bar.
  • the cooling circuit is closed and is operated with treated (decalcified) water.
  • the heat extracted from the cooling circuit 35 via the convection cooler 37 is preferably used for heating the workshop halls belonging to the shaft furnace or surrounding other halls.
  • the cooling circuit 35 is operated at an outlet temperature of 4 bar and 100 ° C. at the wind nozzle designated 38. Heat is removed from the cooling circuit 35 for any purpose via the heat exchanger 36.
  • the associated heating circuit is designated 39.
  • the water of the heating circuit 39 is heated in the exemplary embodiment in the heat exchanger from 60 to 80 ° C.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Manufacturing & Machinery (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Vertical, Hearth, Or Arc Furnaces (AREA)
  • Blast Furnaces (AREA)
  • Heat Treatment Of Articles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (7)

1. Tuyère à vent refroidie par un fluide, en particulier tuyère refroidie à l'eau, pour fours à cuve fonctionnant au coke, dans laquelle est diposé entre l'enveloppe interne et l'enveloppe externe de la tuyère un système de canaux en spirale comprenant un canal amenant le fluide de refroidissement jusqu'à la tête de la tuyère et un autre canal ramenant le fluide de refroidissement depuis la tête de tuyère, les deux canaux étant séparés l'un de l'autre par une enveloppe intermédiaire disposée entre les enveloppes interne et externe, et dans laquelle les enveloppes interne et externe sont directement soudées l'une à l'autre ou sont indirectement soudées l'une à l'autre par t'intermédiaire d'un embout, caractérisée en ce que, pour un diamètre intérieur de tuyère de
- 80 à 120 mm la différence avec le diamètre extérieur est inférieure à 60 mm
- 120 à 180 mm la différence avec le diamètre extérieur est inférieure à 70 mm
- 180 à 250 mm la différence avec le diamètre extérieur est inférieure à 80 mm
- plus de 250 mm la différence avec le diamètre extérieur est inférieure à 90 mm,

et en ce que des fils métalliques (18, 19) sont utilisés comme limites latérales des canaux entre les enveloppes interne, externe et intermédiaire (15, 16, 31, 32).
2. Tuyère à vent selon la revendication 1, caractérisé en ce que les fils métalliques ont une section ronde ou triangulaire.
3. Tuyère à vent selon l'une des revendications 1 ou 2, caractérisé en ce que les fils métalliques ont une épaisseur comprise entre 4 et 8 mm.
4. Utilisation d'une tuyère à vent selon l'une ou plusieurs des revendications 1 à 3, caractérisée en ce que le fluide de refroidissement subit dans la tuyère à vent un échauffement d'au moins 20° C.
5. Utilisation d'une tuyère à vent selon la revendication 4, caractérisée en ce que le fluide de refroidissement est refroidi dans un échangeur de chaleur et un circuit de refroidissement fonctionnant à des températures dépassant 50° C.
6. Utilisation d'une tuyère à vent selon l'une ou plusieurs des revendications 1 à 3, caractérisée en ce que le circuit de refroidissement à l'eau fonctionne à une pression maximale de 4 bars dans le domaine des températures inférieures à 100°C et à une pression maximale de 10 bars dans le domaine des températures supérieures à 100° C.
7. Utilisation d'une tuyère à vent selon l'une ou plusieurs des revendications 1 à 3, caractérisé en ce qu'il est fait usage d'un fluide de refroidissement ayant une température de vaporisation dépassant 100°C.
EP84107748A 1984-01-04 1984-07-04 Tuyère refroidie pour four à cuve Expired EP0148983B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84107748T ATE31941T1 (de) 1984-01-04 1984-07-04 Fluessigkeitsgekuehlte windduese fuer schachtoefen.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3400155 1984-01-04
DE3400155 1984-01-04

Publications (2)

Publication Number Publication Date
EP0148983A1 EP0148983A1 (fr) 1985-07-24
EP0148983B1 true EP0148983B1 (fr) 1988-01-13

Family

ID=6224340

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84107748A Expired EP0148983B1 (fr) 1984-01-04 1984-07-04 Tuyère refroidie pour four à cuve

Country Status (3)

Country Link
EP (1) EP0148983B1 (fr)
AT (1) ATE31941T1 (fr)
DE (1) DE3468699D1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN106705729B (zh) * 2016-12-26 2018-10-23 江苏龙冶节能科技有限公司 一种焦炉荒煤气上升管换热装置

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB204262A (en) * 1923-01-25 1923-09-27 Robert Edwin Goldsbrough Improvements relating to blast furnace tuyeres and the like
FR792759A (fr) * 1934-09-10 1936-01-10 Nouvelle tuyère, avec refroidissement intégral par eau pour le soufflage du vent chaud ou des gaz chauds dans les hauts fourneaux, cubilots ou fours, etc.
DE1236707B (de) * 1963-05-02 1967-03-16 Schmidt Sche Heissdampf Ges M Blasform fuer Abstickgeneratoren, Hochoefen u. dgl. metallurgische OEfen
FR1495488A (fr) * 1966-06-10 1967-09-22 Lorraine Escaut Sa Tuyère à vent pour haut fourneau
LU55579A1 (fr) * 1967-07-17 1968-05-06
DE2031379A1 (en) * 1970-06-25 1971-12-30 Rohde, Ewald, W , Dr Ing, 5905 Freundenberg Cooling system for blast furnace tuyeres - using secondary cooling circuit
US3727898A (en) * 1971-02-22 1973-04-17 J Allen Fabricated tuyere nozzle
DE2204212C2 (de) * 1972-01-29 1982-06-16 Siegerländer Kupferwerke GmbH, 5900 Siegen Hochofen-Blasform
US3826479A (en) * 1973-02-16 1974-07-30 Kurimoto Ltd Tuyere for a melting furnace
US3898078A (en) * 1973-03-29 1975-08-05 Youngstown Sheet And Tube Co Method and apparatus for injecting refining oxygen in steelmaking processes
DE2608365C3 (de) * 1976-03-01 1978-11-16 S.A. Des Anciens Etablissements Emile Dupret, Luxemburg Wassergekühlte, geschweißte Doppelkammerblasform für Schachtöfen, insbesondere Hochöfen
DE2907511C2 (de) * 1979-02-26 1986-03-20 Kabel- und Metallwerke Gutehoffnungshütte AG, 3000 Hannover Kühlplatte für Schachtöfen, insbesondere Hochöfen, und Verfahren zur Herstellung derselben

Also Published As

Publication number Publication date
ATE31941T1 (de) 1988-01-15
EP0148983A1 (fr) 1985-07-24
DE3468699D1 (en) 1988-02-18

Similar Documents

Publication Publication Date Title
DE60203911T2 (de) Gasspüllanze
DE2914728A1 (de) Glasspinnvorrichtung
EP0148983B1 (fr) Tuyère refroidie pour four à cuve
EP1136621A2 (fr) Rouleau rotative
DE2623425B2 (de) Vorrichtung zum Kühlen einer Külbelform
DE2313320A1 (de) Durch umgiessen eines oder mehrerer rohre, insbesondere kuehlrohr, geformtes gussteil
DE4236158C1 (de) Elektrodentragarm für Lichtbogenöfen
DE69932656T2 (de) Intern gekühlte Umlenkrinne und Methode für die Zuführung von Glasposten
DE2730886A1 (de) Verfahren und vorrichtung zur herstellung von fasern, insbesondere glasfasern
DE3390182C2 (fr)
EP0144029B1 (fr) Tuyau de refroidissement pour section de refroidissement pour refroidir rapidement du fil laminé ou du matériel à barres
DE656868C (de) Wassergekuehlte Blasform fuer Schachtoefen, z. B. Hochoefen
DE3424601A1 (de) Kuehlkreis fuer fluessigkeitsgekuehlte windduese
DE102021003023B3 (de) Formgebungswerkzeug und Verfahren zur Herstellung von Mehrlumenschläuchen
DE3505968C2 (fr)
DE3729915C2 (de) Wassergekühlte Blasform für Hochöfen und Heißwindkupolöfen
DE903795C (de) Verfahren und Vorrichtung zum Herstellen von Mineralfasern, insbesondere Schlackenwolle
AT391877B (de) Metallurgisches gefaess, insbesondere stationaerer oder auswechselbarer stahlwerkskonverter
DE1037658B (de) Schachtofen, insbesondere Kupolofen fuer Heisswindbetrieb, mit luftgekuehlter Ofenwand im Bereich der Schmelzzone
DE10017604A1 (de) Rotierbare Walze
DE2219715C3 (de) Band-Schwebeführungsvorrichtung zur Wärmebehandlung innerhalb eines Ofens
DE2204212C2 (de) Hochofen-Blasform
DE1042188B (de) Verfahren und Vorrichtung zum Kraeuseln von Mineral- oder aehnlichen Faeden
AT202581B (de) Blasrohr zum Frischen von Roheisen
EP1673481A2 (fr) Four industriel et buse associee

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19850508

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI NL SE

17Q First examination report despatched

Effective date: 19860625

ITF It: translation for a ep patent filed
GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI NL SE

REF Corresponds to:

Ref document number: 31941

Country of ref document: AT

Date of ref document: 19880115

Kind code of ref document: T

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3468699

Country of ref document: DE

Date of ref document: 19880218

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19930521

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19940620

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19940624

Year of fee payment: 11

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19940704

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19940720

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19940725

Year of fee payment: 11

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19940731

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19941228

Year of fee payment: 11

EAL Se: european patent in force in sweden

Ref document number: 84107748.0

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19950704

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19950705

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19950719

Year of fee payment: 12

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19950731

Ref country code: CH

Effective date: 19950731

Ref country code: BE

Effective date: 19950731

BERE Be: lapsed

Owner name: KUTTNER G.M.B.H. & CO. K.G.

Effective date: 19950731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19960201

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19950704

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19960201

EUG Se: european patent has lapsed

Ref document number: 84107748.0

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19960430

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19970402