EP0724114A2 - Brûleur - Google Patents

Brûleur Download PDF

Info

Publication number
EP0724114A2
EP0724114A2 EP96810023A EP96810023A EP0724114A2 EP 0724114 A2 EP0724114 A2 EP 0724114A2 EP 96810023 A EP96810023 A EP 96810023A EP 96810023 A EP96810023 A EP 96810023A EP 0724114 A2 EP0724114 A2 EP 0724114A2
Authority
EP
European Patent Office
Prior art keywords
burner
fuel
flow
burner according
air
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Withdrawn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
EP96810023A
Other languages
German (de)
English (en)
Other versions
EP0724114A3 (fr
Inventor
Alfred Häusermann
Jörg Schmidli
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.)
ABB AG Germany
Original Assignee
ABB Management 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 ABB Management AG filed Critical ABB Management AG
Publication of EP0724114A2 publication Critical patent/EP0724114A2/fr
Publication of EP0724114A3 publication Critical patent/EP0724114A3/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/002—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D17/00—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/07002—Premix burners with air inlet slots obtained between offset curved wall surfaces, e.g. double cone burners

Definitions

  • the present invention relates to a burner according to the preamble of claim 1.
  • LBTU gas In steel production, a by-product is a fuel gas with a low calorific value (2-4 MJ / kg).
  • This so-called LBTU gas has so far been burned in gas turbines with thermal outputs of up to 300 MW using a single burner.
  • individual burners In order to burn this gas in modern gas turbines, which are equipped, for example, with an annular combustion chamber, individual burners are required which have a thermal output of the order of less than 20 MW.
  • the difficulty in realizing a burner that can be operated with LBTU is that the mass ratio of air to fuel is of the order of 1: 1, in contrast to a natural gas-fired burner, in which the ratio is 30: 1.
  • a burner has become known from EP-0 321 809, which permits premix-like combustion, and also has a number of other advantages, which are described in detail in this document are.
  • This burner essentially consists of at least two hollow, conical, part-bodies nested one inside the other in the direction of flow, the respective longitudinal axes of symmetry of which are offset with respect to one another in such a way that the adjacent walls of the part bodies form tangential channels for a combustion air flow in their longitudinal extension.
  • a liquid fuel is preferably injected into the cavity formed by the partial bodies via a central nozzle, while a gaseous fuel is introduced via the further nozzles in the area of the tangential channels in the longitudinal direction.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, is based on the object of proposing precautions for a burner of the type mentioned at the outset which permit operation of this burner with LBTU gas and the inherent advantages of this burner are not lost therefrom.
  • the main advantage of the invention can be seen in the fact that the burner allows operation with LBTU gas, that an optimal mixture formation is provided, and that the combustion continues at the exit of the burner with formation of a backflow zone and with minimization of the pollutant emissions at maximum efficiency.
  • FIG. 3 is used simultaneously with FIG. 1. Furthermore, in order not to make FIG. 1 unnecessarily confusing, the guide plates 19, 20 shown schematically according to FIG. 3 have only been hinted at in it. In the description of FIG. 1, reference is made to FIG. 3 as required below.
  • the burner 1 according to FIG. 1 consists of two hollow conical partial bodies 2, 3, which are nested in one another offset.
  • the offset of the respective central axis or longitudinal axis of symmetry 2a, 3a (see FIG. 3) of the conical partial bodies 2, 3 to one another creates a tangential air inlet slot 2b, 3b on both sides, in a mirror-image arrangement (see FIG. 3) which flows the combustion air 4 into the interior of the burner 1, ie into the cone cavity 5.
  • the conical shape of the partial bodies 2, 3 shown in the flow direction has a certain fixed angle.
  • the partial body 2, 3 may have an increasing or decreasing cone inclination in the flow direction, similar to a trumpet or. Tulip.
  • the two tapered partial bodies 2, 3 each have a cylindrical starting part 2c, 3c, which, similarly to the tapered partial bodies 2, 3, also run offset from one another, so that the tangential air inlet slots 2b, 3b are present over the entire length of the burner 1.
  • the burner 1 can be designed to be purely conical, that is to say without cylindrical starting parts 2c, 3c.
  • the two conical partial bodies 2, 3 each have an inwardly displaced and also tangentially guided channel 6, 7 (cf. also FIG. 3), through which a gaseous fuel 8 is fed into the cone cavity 5.
  • the two flows namely the combustion air 4 and the gaseous fuel 8 are guided separately up to the region of the tangential air inlet slots 2b, 3b by means of a partition 6a, 7a (cf. FIG. 3).
  • this can be achieved by placing a fuel-carrying chamber on the respective partial body 2, 3, which chamber has a continuous tangential opening in the area of the air inlet slots 2b, 3b mentioned. It is thereby achieved that two parallel currents flow into the cone cavity 5 at the same time.
  • the flow openings of the two channels towards the cone cavity 5 are to be designed in such a way that they allow the flow of an approximately equal mass flow, which is always necessary when the burner 1 is operated with an LBTU gas.
  • the gas-carrying duct (6, 7) is guided on the cone cavity side with respect to the flow of the combustion air 4.
  • the flow of media 4, 8 can be interchanged.
  • the mixing of the two media 4, 8 in the cone cavity 5 takes place very intensively due to the mutually forming shear forces in the inflow into the cone cavity 5 guided by partition walls 6a, 7a.
  • an optimal, homogeneous mixture 9 is achieved across the cross section at the end of the burner 1. If the combustion air 4 is additionally preheated or enriched with a recirculated exhaust gas, this supports the degree of mixing of the two media 4, 8 sustainably.
  • the critical swirl number should be set at the outlet of the burner 1:
  • a backflow zone (vortex breakdown) 10 is also formed, which triggers a stabilizing effect on the flame front 11, the
  • the cross-sectional expansion specified there between the flow cross-section of the burner 1 and the combustion chamber 12 triggers peripheral vortex detachments, which further stabilize the flame front 11, in such a way that radial flattening of the backflow zone 10 and back-ignition of the flame 11 into the interior of the burner 1 are prevented.
  • the critical swirl number given the Keqel configuration of the partial bodies 2, 3, is reduced of the tangential air inlet slots 2b, 3b sets faster, so that the backflow zone 10 coinciding with the critical number of swirls may set up even before the burner 1 exits.
  • the axial speed within the burner 1 can, however, be changed by a correspondingly large supply of an axial combustion air flow 4a.
  • the design of the burner 1 is furthermore excellently suitable for changing the size of the tangential air inlet slots 2b, 3b, with which a relatively large operational bandwidth can be recorded without changing the overall length of the burner 1.
  • the partial bodies 2, 3 can also be displaced relative to one another in another plane, as a result of which even an overlap thereof can be initiated.
  • FIG. 2 shows the same burner structure according to FIG. 1, this burner 1a being equipped with a central fuel nozzle 15 which acts as the head stage of this burner la.
  • this nozzle 15 can also be operated with a gaseous fuel.
  • it is also possible to operate this nozzle with a liquid fuel 16 the operation of this burner la being carried out solely via said nozzle 15 or in cooperation with the gaseous fuel 8 which is introduced via the slots provided tangentially therefor (see FIG . 1, 3).
  • a liquid fuel 16 is introduced via the nozzle 15, a conical fuel profile 18 is formed in the cone cavity 5 due to the acute angle 17 set there, which is encased by the combustion air 4 flowing in tangentially and swirling.
  • the concentration of the fuel 16 is continuously reduced to a mixture by the incoming combustion air 4. Even when a liquid fuel 16 is used via said nozzle 15, the optimum, homogeneous concentration over the cross section is achieved at the outlet of the burner 1a. If the combustion air 4 is preheated or enriched with a recirculated exhaust gas, the evaporation of the liquid fuel 16 is markedly increased in such a way that a return flow zone 10 and a flame front 11 also form at the outlet of the burner 1 a, as already shown in FIG. 1 Explanation came. In the case of lean gases in particular, it can be introduced by one Difficult to accomplish nozzle because of the large fuel mass required for this. With such specifications, the configuration according to FIG. 1 is used.
  • baffles 19, 20 have a flow introduction function, and they can be designed in various ways.
  • the channeling of the combustion air 4 into the cone cavity 5 can be optimized accordingly by opening or closing these guide plates 19, 20, for example about a pivot point (not shown) in the region of the tangential air inlet slots 2b, 3b.
  • these dynamic arrangements can also be provided statically, in that guide baffles corresponding to requirements form a fixed component with the conical partial bodies 2, 3.
  • the burner can also be operated without baffles, or other aids can be provided for this.
  • 3 also shows how the inflow of the gaseous fuel 8, on the inside of the combustion air 4, is determined.
  • the partition walls 6a, 7a tapped under FIG. 1, which accomplish the respective channel formation for the two media 4, 8, can now be clearly seen from FIG. 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
  • Spray-Type Burners (AREA)
EP96810023A 1995-01-30 1996-01-10 Brûleur Withdrawn EP0724114A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19502796A DE19502796B4 (de) 1995-01-30 1995-01-30 Brenner
DE19502796 1995-01-30

Publications (2)

Publication Number Publication Date
EP0724114A2 true EP0724114A2 (fr) 1996-07-31
EP0724114A3 EP0724114A3 (fr) 1998-03-11

Family

ID=7752619

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96810023A Withdrawn EP0724114A3 (fr) 1995-01-30 1996-01-10 Brûleur

Country Status (4)

Country Link
US (1) US5674066A (fr)
EP (1) EP0724114A3 (fr)
JP (1) JP3702021B2 (fr)
DE (1) DE19502796B4 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0918191A1 (fr) * 1997-11-21 1999-05-26 Abb Research Ltd. Brûleur pour la mise en oeuvre d'un générateur de chaleur
EP0981016A1 (fr) * 1998-08-19 2000-02-23 Asea Brown Boveri AG Brûleur et procédé de fonctionnement d'un moteur à combustion interne

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19619873A1 (de) * 1996-05-17 1997-11-20 Abb Research Ltd Brenner
DE19654009B4 (de) * 1996-12-21 2006-05-18 Alstom Vormischbrenner zum Betrieb einer Brennkammer mit einem flüssigen und/oder gasförmigen Brennstoff
EP0924462A1 (fr) 1997-12-15 1999-06-23 Asea Brown Boveri AG Brûleur pour le fonctionnement d'un générateur de chaleur
DE10049205A1 (de) * 2000-10-05 2002-05-23 Alstom Switzerland Ltd Verfahren und Vorrichtung zur Brennstoffversorgung eines Vormischbrenners
DE10051221A1 (de) * 2000-10-16 2002-07-11 Alstom Switzerland Ltd Brenner mit gestufter Brennstoff-Eindüsung
GB2368386A (en) 2000-10-23 2002-05-01 Alstom Power Nv Gas turbine engine combustion system
EP1262714A1 (fr) * 2001-06-01 2002-12-04 ALSTOM (Switzerland) Ltd Brûleur avec recirculation des gaz de combustion
US7097448B2 (en) * 2004-05-07 2006-08-29 Peter Chesney Vortex type gas lamp
US7421843B2 (en) * 2005-01-15 2008-09-09 Siemens Power Generation, Inc. Catalytic combustor having fuel flow control responsive to measured combustion parameters
US20090301054A1 (en) * 2008-06-04 2009-12-10 Simpson Stanley F Turbine system having exhaust gas recirculation and reheat
US8382565B2 (en) * 2008-06-09 2013-02-26 International Business Machines Corporation System and method to redirect and/or reduce airflow using actuators
US9297306B2 (en) * 2008-09-11 2016-03-29 General Electric Company Exhaust gas recirculation system, turbomachine system having the exhaust gas recirculation system and exhaust gas recirculation control method
JP5462527B2 (ja) * 2009-05-19 2014-04-02 大阪瓦斯株式会社 管状火炎バーナ
JP5462526B2 (ja) * 2009-05-19 2014-04-02 大阪瓦斯株式会社 管状火炎バーナ
US9170017B2 (en) 2010-01-06 2015-10-27 The Outdoor Greatroom Company LLLP Fire container assembly
US9127598B2 (en) 2011-08-25 2015-09-08 General Electric Company Control method for stoichiometric exhaust gas recirculation power plant
US8453462B2 (en) 2011-08-25 2013-06-04 General Electric Company Method of operating a stoichiometric exhaust gas recirculation power plant
US8266883B2 (en) 2011-08-25 2012-09-18 General Electric Company Power plant start-up method and method of venting the power plant
US8245492B2 (en) 2011-08-25 2012-08-21 General Electric Company Power plant and method of operation
US8713947B2 (en) 2011-08-25 2014-05-06 General Electric Company Power plant with gas separation system
US8453461B2 (en) 2011-08-25 2013-06-04 General Electric Company Power plant and method of operation
US8347600B2 (en) 2011-08-25 2013-01-08 General Electric Company Power plant and method of operation
US8205455B2 (en) 2011-08-25 2012-06-26 General Electric Company Power plant and method of operation
US8266913B2 (en) 2011-08-25 2012-09-18 General Electric Company Power plant and method of use
DE102013214387B4 (de) * 2013-07-23 2020-10-22 Eberspächer Climate Control Systems GmbH Einströmelement, insbesondere für einen Verbrennungsluftströmungsweg im Fahrzeugheizgerät
JP2013228207A (ja) * 2013-08-15 2013-11-07 Osaka Gas Co Ltd 管状火炎バーナ

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE413283C (de) * 1925-05-05 Faconeisen Walzwerk L Mannstae Gasfeuerung fuer Dampfkessel und Drehtrommeln
DE3151479A1 (de) * 1981-12-24 1983-07-14 Horst 4630 Bochum Ley Zur industriellen verwendung ausgelegter gasbrenner
US5169302A (en) * 1989-12-22 1992-12-08 Asea Brown Boveri Ltd. Burner
US5274993A (en) * 1990-10-17 1994-01-04 Asea Brown Boveri Ltd. Combustion chamber of a gas turbine including pilot burners having precombustion chambers
DE4409918A1 (de) * 1994-03-23 1995-09-28 Abb Management Ag Brenner zum Betrieb einer Brennkammer

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE28736C (de) * W. GARDNER in St. Leonards, England Verbindung der Ober- und Unter-Laffete von Geschützen
EP0210462B1 (fr) * 1985-07-30 1989-03-15 BBC Brown Boveri AG Chambre de combustion double
CH671449A5 (fr) * 1986-07-08 1989-08-31 Bbc Brown Boveri & Cie
CH674561A5 (fr) * 1987-12-21 1990-06-15 Bbc Brown Boveri & Cie
US5193995A (en) * 1987-12-21 1993-03-16 Asea Brown Boveri Ltd. Apparatus for premixing-type combustion of liquid fuel
CH680946A5 (fr) * 1989-12-19 1992-12-15 Asea Brown Boveri
DE59104727D1 (de) * 1991-12-23 1995-03-30 Asea Brown Boveri Vorrichtung für die Vermischung zweier gasförmiger Komponenten und Brenner, in welchem diese Vorrichtung eingesetzt wird.
US5307634A (en) * 1992-02-26 1994-05-03 United Technologies Corporation Premix gas nozzle

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE413283C (de) * 1925-05-05 Faconeisen Walzwerk L Mannstae Gasfeuerung fuer Dampfkessel und Drehtrommeln
DE3151479A1 (de) * 1981-12-24 1983-07-14 Horst 4630 Bochum Ley Zur industriellen verwendung ausgelegter gasbrenner
US5169302A (en) * 1989-12-22 1992-12-08 Asea Brown Boveri Ltd. Burner
US5274993A (en) * 1990-10-17 1994-01-04 Asea Brown Boveri Ltd. Combustion chamber of a gas turbine including pilot burners having precombustion chambers
DE4409918A1 (de) * 1994-03-23 1995-09-28 Abb Management Ag Brenner zum Betrieb einer Brennkammer

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0918191A1 (fr) * 1997-11-21 1999-05-26 Abb Research Ltd. Brûleur pour la mise en oeuvre d'un générateur de chaleur
US6155820A (en) * 1997-11-21 2000-12-05 Abb Research Ltd. Burner for operating a heat generator
EP0981016A1 (fr) * 1998-08-19 2000-02-23 Asea Brown Boveri AG Brûleur et procédé de fonctionnement d'un moteur à combustion interne
US6263676B1 (en) 1998-08-19 2001-07-24 Asea Brown Boveri Ag Burner having a frame for operating an internal combustion machine

Also Published As

Publication number Publication date
EP0724114A3 (fr) 1998-03-11
JPH08233219A (ja) 1996-09-10
US5674066A (en) 1997-10-07
JP3702021B2 (ja) 2005-10-05
DE19502796B4 (de) 2004-10-28
DE19502796A1 (de) 1996-08-01

Similar Documents

Publication Publication Date Title
DE19502796B4 (de) Brenner
EP0704657B1 (fr) Brûleur
EP0777081B1 (fr) Brûleur à prémélange
EP0918191B1 (fr) Brûleur pour la mise en oeuvre d'un générateur de chaleur
EP0571782B1 (fr) Procédé de fonctionnement d'une chambre de combustion pour turbine à gaz
EP0694740A2 (fr) Chambre de combustion
EP0548396B1 (fr) Dispositif servant à mélanger deux composants gazeux et brûleur dans lequel ce dispositif est appliqué
EP0718561B1 (fr) Brûleur
EP0321809A1 (fr) Procédé pour la combustion de combustible liquide dans un brûleur
CH678757A5 (fr)
EP0202443A2 (fr) Procédé et dispositif à combustion de combustibles liquides et/ou solides pulvérulents
CH680084A5 (fr)
DE2621496A1 (de) Wirbelstrombrenner fuer industrieoefen, wie hochoefen und dergleichen
EP0780630A2 (fr) Brûleur pour un générateur de chaleur
EP0851172B1 (fr) Brûleur et méthode pour la mise en oeuvre d'une chambre de combustion avec un combustible liquide et/ou gazeux
EP0641971A2 (fr) Procédé pour commander un brûleur à prémélange
EP0994300B1 (fr) Brûleur pour la conduite d'un générateur de chaleur
EP0751351B1 (fr) Chambre de combustion
EP0694730B1 (fr) Bruleur
EP0777082A2 (fr) Brûleur à prémélange
DE4412315A1 (de) Verfahren und Vorrichtung zum Betreiben der Brennkammer einer Gasturbine
EP0740108A2 (fr) Brûleur
EP0961905B1 (fr) Procede et dispositif de combustion d'un combustible
EP0780628B1 (fr) Brûleur à prémélange pour un générateur de chaleur
EP0899506A2 (fr) Dispositif de combustion

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

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE GB NL

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ASEA BROWN BOVERI AG

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE GB NL

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19980912