EP0851990A2 - Bruleur, en particlier pour turbine a gaz - Google Patents

Bruleur, en particlier pour turbine a gaz

Info

Publication number
EP0851990A2
EP0851990A2 EP96942244A EP96942244A EP0851990A2 EP 0851990 A2 EP0851990 A2 EP 0851990A2 EP 96942244 A EP96942244 A EP 96942244A EP 96942244 A EP96942244 A EP 96942244A EP 0851990 A2 EP0851990 A2 EP 0851990A2
Authority
EP
European Patent Office
Prior art keywords
burner
swirl
burner according
annular gap
outlet
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP96942244A
Other languages
German (de)
English (en)
Other versions
EP0851990B1 (fr
Inventor
Bernd Prade
Bernhard Schetter
Holger Streb
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Publication of EP0851990A2 publication Critical patent/EP0851990A2/fr
Application granted granted Critical
Publication of EP0851990B1 publication Critical patent/EP0851990B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • 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
    • 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
    • F23C7/004—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion using vanes
    • 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
    • F23D14/26—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid with provision for a retention flame

Definitions

  • the invention relates to a burner with an axis and with respect to this rotationally symmetrical arrangement of an outer jacket and an inner jacket coaxial therewith, which defines an annular gap extending from an inlet to an outlet for guiding a stream of an oxygen-containing gas a plurality of nozzles arranged in the annular gap for supplying a fuel and a swirl grille arranged in the annular gap.
  • the invention relates in particular to such a burner for use in a gas turbine.
  • This effect is the formation of a vortex core in the interior of the stream, that is to say that a stream traveling with a swirl tends to form an annulus, so that in a central region surrounding the axis of a cylindrical tube in which the stream is conducted , no flow in the direction of the current takes place.
  • a burner of the type mentioned in the introduction generally has the purpose of burning a fuel safely and with low pollutants in a stream of an oxygen-containing gas, in particular in compressed air.
  • pollutants such as nitrogen oxides and carbon monoxide premix combustion proved to be favorable; for this purpose, a mixture of fuel and oxygen-containing gas which is as homogeneous as possible is first formed, and only this mixture is ignited.
  • Fuels of this type are e.g. B. gases containing elemental hydrogen, for example
  • a burner is provided with an axis and with respect to this rotationally symmetrical arrangement of an outer jacket and an inner jacket coaxial therewith, which has an annular gap extending from an inlet to an outlet for guiding a stream of an oxygen-containing gas defined, with a plurality of nozzles arranged in the annular gap for supplying a fuel to the stream and a swirl grille arranged in the annular gap, the arrangement of the outer jacket and the inner jacket being designed in such a way that the stream adjusts the
  • Annular gap between the swirl grille and the outlet flows at an essentially constant meridional speed.
  • the feature of the "essentially constant meridional speed" means that the arrangement through which the current flows must oppose the current with an essentially constant meridional flow cross-section. In many cases, however, this flow cross-section will not be perpendicular to an axis of symmetry of the structure to be traversed, but rather must be dimensioned according to a vector field describing the current at an angle to the axis of symmetry and transversely to the vector field.
  • a simple calculation model which does not have to take the current into account explicitly, provides a good approximation for determining the flow cross-section along the arrangement to be flowed through.
  • Tori inscribed touch gential which both the surface of the outer shell and the surface of the inner shell tan ⁇ .
  • the points at which such a torus touches the outer jacket or the inner jacket lie here a circle on the outer jacket or a circle on the inner jacket.
  • a truncated cone surface is clamped between these two circles; this has a surface area which, with a good approximation, corresponds to the effective flow cross-section at the location of the truncated cone surface.
  • the invention is based on the knowledge that the guarantee of a constant meridional speed for the current behind the swirl grid, i. H. ensuring a constant speed of propagation of the current along the axis or in a radial-axial direction with respect to the axis
  • Plane has a stabilizing effect on the current and the current in this material to be formed from the acid mixture ⁇ containing gas and the fuel in a special way.
  • In ⁇ beson ⁇ more complete, this measure ensured that disturbances are suppressed due to egg ner non-ideal flow to the burner.
  • a necessary pressure drop, which must occur above the burner, is largely reduced between the inlet and the swirl grille.
  • ⁇ ie Ge ⁇ is propelled prevents behind the swirl lattice defects to the current m arise.
  • the arrangement of the outer jacket and the inner jacket is designed such that the annular gap between the inlet and the swirl grille narrows.
  • the outer casing ms is designed in such a way that it opens at the entrance in the manner of a lip or a rounded funnel; the inner jacket is particularly equipped with a rounded edge at the entrance. This contributes to a homogenization of the stream passing through the burner and avoids that disturbances which have formed in the stream before the burner continue into the burner.
  • the nozzles arranged in the annular gap for supplying a fuel are arranged in the swirl grille.
  • the swirl grid consists in particular of hollow guide vanes in which the nozzles are arranged.
  • the burner is particularly preferably designed such that one of the swirl grille, a radius of the outer casing and a radius of the inner casing, to determine both radii at the outlet, defines a twist number which can be calculated as a quotient between an angular momentum as dividend and a product of one meridional impulse and the radius of the outer jacket as a divisor, the angular momentum and the meridional impulse characterizing the current at the outlet, when it flows towards the inlet without swirl, is smaller than a critical swirl number, which is determined by the radii.
  • the requirement on which the corresponding design of the burner is based is known as "Strscheletzky's hub criterion".
  • the swirl number can be calculated from characteristic quantities of the current, namely the size of a meridional component of its pulse and the size of its angular momentum, which is largely determined by the swirl grid, but that the swirl number is still one is the characteristic parameter of the burner itself. This results from the flow mechanical similarity relationships.
  • critical swirl number was coined on the basis of the observation that in the vicinity of the axis of a current moving with a swirl along the axis a so-called vortex core forms, ie an area from which the current essentially flows is displaced. The reason for this are, for example, centrifugal forces.
  • the diameter of this vortex core is accessible to the calculation; ⁇ see the quoted books. In principle, the diameter of the vortex core increases with an increasing number of twists.
  • the critical twist number is defined as the twist number at which the radius of the vortex core of the stream corresponds exactly to the inner radius, ie the radius of the inner jacket.
  • the defined as explained swirl number of Brenner ⁇ is normal use before ⁇ preferably significantly smaller than the critical swirl number chooses; in particular, the swirl number of the burner is between 75% and 97% of the critical swirl number and is particularly preferably about 90% of the critical swirl number.
  • the burner of any configuration is preferably provided with a pilot burner.
  • This pilot burner comprises in particular a pilot burner arranged in the inner jacket, which delivers a small, stable burning flame, on which the mixture of gas and fuel containing oxygen which is formed in the burner itself can ignite. This is important if control of the fuel supply and thus control of the heat production of the burner is desired. It has been shown that premix combustion without stabilization is only stable in a relatively narrow operating range, characterized by a chemical composition that must be observed relatively precisely. However, if additional stabilization is provided with a corresponding pilot combustion device, an expansion of the operating range which is important for practical operation can be achieved.
  • the burner is particularly qualified for use in a combustion device of a gas turbine and is particularly qualified for a gas turbine in which relatively flammable fuels are to be burned.
  • the burner is by no means limited to the combustion of gaseous fuels; In principle, the burner can be operated in an appropriate configuration with any flowable fuel, in particular with heating oil and the like.
  • An embodiment of the invention can be seen from the drawing. This shows:
  • 1 shows a longitudinal section through a burner; 2 shows a diagram of a gas turbine
  • the burner shown in FIG. 1 is rotationally symmetrical with respect to axis 1. It has an outer jacket 2 and an inner jacket 3 coaxial with this. Neither the outer jacket 2 nor the inner jacket 3 have to be made in one piece; it is very possible and, for example for reasons of rational production, advantageous to assemble the outer casing 2 and / or the inner casing 3 from several parts, as shown.
  • the outer jacket 2 and the inner jacket 3 define an annular gap 4, through which an inlet 5 to an outlet 6 flows through a stream 7 (represented by arrows) of a gas containing oxygen.
  • a swirl grid 8 Arranged in the annular gap 4 is a swirl grid 8, consisting of a plurality of guide vanes 8, which imparts a swirl to the stream 7; this means that the current 7 executes a helical movement about the axis 1 behind the swirl grid 8. Accordingly, it does not only have velocity vectors that lie in radial-axial planes with respect to axis 1 and are accordingly oriented meridionally according to the technical terminology; behind the swirl grid 8, the velocity vectors also have components which are oriented tangentially to axis 1 or to circles, the center points of which lie on axis 1 and which lie in planes which are oriented perpendicular to axis 1. Such tangential components can also be referred to as "peripheral components" in accordance with the relevant terminology.
  • the guide vanes 8 have nozzles 9, through which a fuel, in particular a combustible gas, is fed to the stream 7. This mixes with the current initially without ignition, and the mixture formed ignites only in the area of the outlet 6. Accordingly, the burner is a premix burner.
  • An essential feature of the burner is that the arrangement of the outer jacket 2 and the inner jacket 3 is designed in such a way that the stream 7 flows through the annular gap 4 between the swirl grid 8 and the outlet 6 at an essentially constant median speed.
  • the annular gap 4 narrows significantly; This narrowing results mainly from the fact that the current 7 is partly guided radially inwards to the axis 1, so that it is sufficient to maintain a largely constant distance between the outer jacket 2 and the inner jacket 3.
  • the outer jacket 2 is expanded in a funnel-like manner in the region of the inlet 5 so that it opens at the inlet 5 in the manner of a rounded funnel or a lip, and the inner jacket 3 has a rounded edge 10 at the inlet 5.
  • the nozzles 9, which serve to feed the fuel, have already been pointed out. These nozzles 9 are arranged in the guide vanes 8 in order to ensure a particularly homogeneous mixing of the fuel into the stream 7 without the flow separating from the guide vanes 8 is coming.
  • the fuel is supplied to the nozzles 9 through a fuel line 11 and a fuel distribution chamber 12 arranged in a ring and on the inside on the inner jacket 3. From this fuel distribution chamber 12, the fuel can pass through channels (not shown) in the inner jacket 3 and the guide vanes 8 the nozzles 9 flow.
  • the geometry of the arrangement of the swirl grille 8, the outer casing 2 and the inner casing 3 is selected such that a swirl number, which determines the essential characteristics of the stream 7, when it flows in the meridional direction at the entrance 5 m enters the ring channel 4, is smaller than a critical swirl number, which results from the radius of the outer jacket 2 and the radius of the inner jacket 3 at the outlet 6.
  • the critical swirl number is defined in such a way that a cylindrical flow caused by a Channel with the mentioned radius of the outer jacket 2 flows along the axis 1, forms a vortex core, that is, an area surrounding the axis 1 from which the flow is displaced, which has a radius that corresponds to the radius of the inner jacket 3 at the outlet 6 corresponds.
  • the geometric structure of the burner has been developed with the help of common mathematical models.
  • the simple calculation model described above has Found sentence in which Tori is inscribed between the outer jacket 2 and the inner jacket 3, with the aid of which approximate values for the flow cross sections in the arrangement are determined.
  • the specification for the definition of the structure is that the flow cross sections over the entire relevant ring channel 4 must be constant.
  • the structure developed with the aid of the simple computing model was then optimized using the commercially available computer program TASCFLOW with regard to the desired constancy of the flow cross section via the ring channel 4.
  • the combustible mixture in stream 7 is ignited outside the burner.
  • a pilot burner 13 with a pilot burner 13 arranged inside the inner jacket 3 is provided for this purpose. It delivers a small one
  • FIG. 2 shows a schematic representation of a gas turbine with a compressor part 15 for the intake and compression of air, a combustion part 16, to which the compressed air is fed, that also receives the fuel provided for combustion, and a turbine part 17, which is the one of the compressor part 15 compressed and in the combustion part 16 additionally heated current is released with the release of mechanical work.
  • the burner shown in FIG. 1 is provided for installation in a combustion part 16 together with a plurality of burners of the same type.
  • the burner according to the invention is characterized by features with which a stream of a gas passing through the burner is particularly favorable for the intended purpose being affected.
  • the burner is also characterized by particularly stable operation and avoids in particular operational malfunctions due to non-ideal flow or due to flashbacks.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)
  • Gas Burners (AREA)

Abstract

L'invention concerne un brûleur présentant un axe (1) et comprenant une enveloppe extérieure (2) et une enveloppe intérieure (3) coaxiale par rapport à celle-ci, disposées selon une symétrie de rotation par rapport audit axe. Cet agencement définit un espace annulaire (4) qui s'étend d'une entrée (5) à une sortie (6) et est conçu pour guider un courant (7) de gaz contenant de l'oxygène. Une pluralité d'ajutages (9) servant à amener un combustible dans le courant (7) et une grille (8) conférant un moment angulaire au courant sont disposés dans l'espace annulaire (4). L'agencement constitué de l'enveloppe extérieure (2) et de l'enveloppe intérieure (3) est conçu de façon que le courant (7) s'écoule à travers l'espace annulaire (4) compris entre ladite grille (8) et la sortie (6) à une vitesse méridienne sensiblement constante. Le brûleur est particulièrement adapté à une utilisation dans une turbine à gaz (15, 16, 17).
EP96942244A 1995-09-22 1996-09-17 Bruleur, en particulier pour turbine a gaz Expired - Lifetime EP0851990B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19535287 1995-09-22
DE19535287 1995-09-22
PCT/DE1996/001756 WO1997011311A2 (fr) 1995-09-22 1996-09-17 Bruleur, en particlier pour turbine a gaz

Publications (2)

Publication Number Publication Date
EP0851990A2 true EP0851990A2 (fr) 1998-07-08
EP0851990B1 EP0851990B1 (fr) 2001-12-05

Family

ID=7772905

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96942244A Expired - Lifetime EP0851990B1 (fr) 1995-09-22 1996-09-17 Bruleur, en particulier pour turbine a gaz

Country Status (7)

Country Link
US (1) US6038864A (fr)
EP (1) EP0851990B1 (fr)
JP (1) JP3939756B2 (fr)
DE (1) DE59608389D1 (fr)
ES (1) ES2169273T3 (fr)
RU (1) RU2156405C2 (fr)
WO (1) WO1997011311A2 (fr)

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59701235D1 (de) * 1996-09-09 2000-04-13 Siemens Ag Vorrichtung und verfahren zur verbrennung eines brennstoffs in luft
EP0995066B1 (fr) * 1997-07-17 2001-09-26 Siemens Aktiengesellschaft Agencement de bruleurs pour une installation de chauffe, notamment une chambre de combustion de turbine a gaz
US6161387A (en) * 1998-10-30 2000-12-19 United Technologies Corporation Multishear fuel injector
DE10104695B4 (de) * 2001-02-02 2014-11-20 Alstom Technology Ltd. Vormischbrenner für eine Gasturbine
US6551098B2 (en) * 2001-02-22 2003-04-22 Rheem Manufacturing Company Variable firing rate fuel burner
US6539721B2 (en) 2001-07-10 2003-04-01 Pratt & Whitney Canada Corp. Gas-liquid premixer
US6698208B2 (en) * 2001-12-14 2004-03-02 Elliott Energy Systems, Inc. Atomizer for a combustor
US6786047B2 (en) 2002-09-17 2004-09-07 Siemens Westinghouse Power Corporation Flashback resistant pre-mix burner for a gas turbine combustor
US6848260B2 (en) 2002-09-23 2005-02-01 Siemens Westinghouse Power Corporation Premixed pilot burner for a combustion turbine engine
EP1645805A1 (fr) * 2004-10-11 2006-04-12 Siemens Aktiengesellschaft brûleur pour combustible fluide et procédé pour uriliser un tel brûleur
US7370466B2 (en) * 2004-11-09 2008-05-13 Siemens Power Generation, Inc. Extended flashback annulus in a gas turbine combustor
EP1944547A1 (fr) 2007-01-15 2008-07-16 Siemens Aktiengesellschaft Procédé de contrôle d'une fuite de carburant
US20080276622A1 (en) * 2007-05-07 2008-11-13 Thomas Edward Johnson Fuel nozzle and method of fabricating the same
US8113000B2 (en) * 2008-09-15 2012-02-14 Siemens Energy, Inc. Flashback resistant pre-mixer assembly
EP2312215A1 (fr) 2008-10-01 2011-04-20 Siemens Aktiengesellschaft Brûleur et procédé de fonctionnement d'un brûleur
EP2236934A1 (fr) * 2009-03-18 2010-10-06 Siemens Aktiengesellschaft Agencement de brûleur
EP2264370B1 (fr) * 2009-06-16 2012-10-10 Siemens Aktiengesellschaft Agencement de brûleur pour une installation de combustion destinée à la combustion de combustibles fluidiques et procédé de fonctionnement d'un tel agencement de brûleur
US8387393B2 (en) * 2009-06-23 2013-03-05 Siemens Energy, Inc. Flashback resistant fuel injection system
WO2012118397A1 (fr) * 2011-02-28 2012-09-07 Открытое Акционерное Общество "Силовые Машины - Зтл, Лмз, Электросила, Энергомашэкспорт" (Оао "Силовые Машины") Brûleur
US9046262B2 (en) * 2011-06-27 2015-06-02 General Electric Company Premixer fuel nozzle for gas turbine engine
WO2019020350A1 (fr) 2017-07-27 2019-01-31 Siemens Aktiengesellschaft Brûleur de turbine à gaz à jets de flamme prémélangés

Family Cites Families (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US33896A (en) * 1861-12-10 Improved automatic
US3589127A (en) * 1969-02-04 1971-06-29 Gen Electric Combustion apparatus
US4013377A (en) * 1975-10-08 1977-03-22 Westinghouse Electric Corporation Intermediate transition annulus for a two shaft gas turbine engine
US4365753A (en) * 1980-08-22 1982-12-28 Parker-Hannifin Corporation Boundary layer prefilmer airblast nozzle
EP0193838B1 (fr) * 1985-03-04 1989-05-03 Siemens Aktiengesellschaft Disposition de brûleur pour installations de combustion, en particulier pour chambres de combustion d'installations de turbines à gaz ainsi que procédé de sa mise en oeuvre
EP0276696B1 (fr) * 1987-01-26 1990-09-12 Siemens Aktiengesellschaft Brûleur hybride pour fonctionnement en prémélange au gaz et/ou au mazout, notamment pour turbines à gaz
US4801261A (en) * 1987-03-19 1989-01-31 Eagleair, Inc. Apparatus and method for delivery of combustion air in multiple zones
DE3819899C1 (en) * 1988-06-11 1989-11-30 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De Apparatus for generating a homogeneous mixture from a first and second medium
DE59000422D1 (de) * 1989-04-20 1992-12-10 Asea Brown Boveri Brennkammeranordnung.
DE69109516T2 (de) * 1990-02-26 1995-09-14 Nippon Denso Co Selbstdiagnoseapparat in einem System zur Verhinderung des Entweichens von verdampftem Brennstoffgas.
US5165241A (en) * 1991-02-22 1992-11-24 General Electric Company Air fuel mixer for gas turbine combustor
DE59204270D1 (de) * 1991-04-25 1995-12-14 Siemens Ag Brenneranordnung, insbesondere für gasturbinen, zur schadstoffarmen verbrennung von kohlegas und anderen brennstoffen.
US5259184A (en) * 1992-03-30 1993-11-09 General Electric Company Dry low NOx single stage dual mode combustor construction for a gas turbine
IT1255613B (it) * 1992-09-24 1995-11-09 Eniricerche Spa Sistema di combustione a basse emissioni inquinanti per turbine a gas
US5323604A (en) * 1992-11-16 1994-06-28 General Electric Company Triple annular combustor for gas turbine engine
CA2167320C (fr) * 1993-07-16 2000-06-06 Steven Jay Bortz Appareil et methode de reduction des emissions de nox, de co et d'hydrocarbures lors de la combustion de gaz
US5423173A (en) * 1993-07-29 1995-06-13 United Technologies Corporation Fuel injector and method of operating the fuel injector
US5351477A (en) * 1993-12-21 1994-10-04 General Electric Company Dual fuel mixer for gas turbine combustor
DE4417769A1 (de) * 1994-05-20 1995-11-23 Abb Research Ltd Verfahren zum Betrieb eines Vormischbrenners
US5865609A (en) * 1996-12-20 1999-02-02 United Technologies Corporation Method of combustion with low acoustics

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9711311A2 *

Also Published As

Publication number Publication date
WO1997011311A2 (fr) 1997-03-27
EP0851990B1 (fr) 2001-12-05
RU2156405C2 (ru) 2000-09-20
JP2000512723A (ja) 2000-09-26
US6038864A (en) 2000-03-21
WO1997011311A3 (fr) 1997-05-15
ES2169273T3 (es) 2002-07-01
DE59608389D1 (de) 2002-01-17
JP3939756B2 (ja) 2007-07-04

Similar Documents

Publication Publication Date Title
EP0851990A2 (fr) Bruleur, en particlier pour turbine a gaz
EP2116766B1 (fr) Brûleur avec lance à combustible
DE833741C (de) Brennkammeraggregat fuer Gasturbinen
EP1800062B1 (fr) Bruleur destine a la combustion d'un gaz combustible a faible pouvoir calorifique et procede pour faire fonctionner un bruleur
EP1754002B1 (fr) Brûleur étagé à prémélange comprenant in injecteur de carburant liquide
DE10217913B4 (de) Gasturbine mit Brennkammer zur flammenlosen Oxidation
DE69129858T2 (de) Verbrennungsanlage mit vermindertem ausstoss von stickstoffoxiden
DE2326302C2 (de) Verbrennungseinrichtung zur kontinuierlichen Verbrennung eines Luft-Brennstoff-Gemisches, insbesondere für Gasturbinen
EP1534997B1 (fr) Brûleur d'une turbine à gaz
DE102010017779B4 (de) Radiale Einlassleitschaufeln für einen Brenner
DE4212810A1 (de) Brenner mit zusaetzlicher zufuehrungsmoeglichkeit fuer fluidische stoffe, insbesondere fuer gasturbinen, und verfahren zu seinem betrieb
DE2841637A1 (de) Brenneranlage zum verbrennen gasfoermiger oder fluessiger brennstoffe
EP0995066B1 (fr) Agencement de bruleurs pour une installation de chauffe, notamment une chambre de combustion de turbine a gaz
DE876495C (de) Brennkammer fuer Gasturbinen
DE2432144A1 (de) Brenner fuer verschiedene brennstoffe
EP3559551A1 (fr) Dispositif de mélange et tête de brûleur pour un brûleur à émission de nox réduite
DE2202913A1 (de) Brenner fuer fluessige oder gasfoermige Brennstoffe
DE112017001173T5 (de) Brenneranordnung, brennkammer und gasturbine
EP2558781B1 (fr) Générateur de turbulence pour un brûleur
CH661974A5 (de) Gasturbinen-brenner.
EP1255077A2 (fr) Dispositif pour la combustion d'un mélange gazeux de combustible et comburant
EP3875854B1 (fr) Brûleur permettant de brûler un écoulement mixte carburant-air, ainsi que appareil de chauffage doté d'un tel brûleur
DE846343C (de) Nachbrennvorrichtung fuer Strahltriebwerke
EP3748228A2 (fr) Brûleur à température de flamme et émission d'oxydes d'azote réduites
DE102020118325A1 (de) Verfahren zur gestuften verbrennung eines brennstoffes und brennkopf

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: 19980304

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): CH DE ES FR GB IT LI SE

17Q First examination report despatched

Effective date: 20000306

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE ES FR GB IT LI SE

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

REF Corresponds to:

Ref document number: 59608389

Country of ref document: DE

Date of ref document: 20020117

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

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20020305

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

Effective date: 20020221

ET Fr: translation filed
REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2169273

Country of ref document: ES

Kind code of ref document: T3

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

Ref country code: ES

Payment date: 20020918

Year of fee payment: 7

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

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020930

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
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030918

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20030918

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 20

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

Ref country code: GB

Payment date: 20150909

Year of fee payment: 20

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

Ref country code: FR

Payment date: 20150910

Year of fee payment: 20

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

Ref country code: IT

Payment date: 20150924

Year of fee payment: 20

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

Ref country code: DE

Payment date: 20151120

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59608389

Country of ref document: DE

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20160916

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

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20160916