EP0918191B1 - Brûleur pour la mise en oeuvre d'un générateur de chaleur - Google Patents

Brûleur pour la mise en oeuvre d'un générateur de chaleur Download PDF

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Publication number
EP0918191B1
EP0918191B1 EP97810894A EP97810894A EP0918191B1 EP 0918191 B1 EP0918191 B1 EP 0918191B1 EP 97810894 A EP97810894 A EP 97810894A EP 97810894 A EP97810894 A EP 97810894A EP 0918191 B1 EP0918191 B1 EP 0918191B1
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EP
European Patent Office
Prior art keywords
fuel
burner according
flow
burner
section
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 - Lifetime
Application number
EP97810894A
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German (de)
English (en)
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EP0918191A1 (fr
Inventor
Klaus Dr. Döbbeling
Hans Peter Knöpfel
Thomas Ruck
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.)
Alstom SA
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Alstom SA
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 Alstom SA filed Critical Alstom SA
Priority to DE59710380T priority Critical patent/DE59710380D1/de
Priority to EP97810894A priority patent/EP0918191B1/fr
Priority to AT97810894T priority patent/ATE244380T1/de
Priority to US09/192,531 priority patent/US6155820A/en
Priority to JP33132098A priority patent/JP4130716B2/ja
Publication of EP0918191A1 publication Critical patent/EP0918191A1/fr
Application granted granted Critical
Publication of EP0918191B1 publication Critical patent/EP0918191B1/fr
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F23D11/402—Mixing chambers downstream of the nozzle
    • 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
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • 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
    • F23D17/002—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel gaseous or liquid 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/14—Special features of gas burners
    • F23D2900/14021—Premixing burners with swirling or vortices creating means for fuel or air

Definitions

  • the invention relates to a burner for the Operation of a heat generator according to the generic term of claim 1.
  • a burner has become known from EP-0 780 629 A2, the upstream side from a swirl generator exists, the flow formed herein is seamlessly transferred into a mixing section.
  • the outflow side of these transition channels has the Mixing section a number of filming holes, which is an increase in flow velocity ensure along the pipe wall. Subsequently follows a combustion chamber, the transition between the mixing section and the combustion chamber a cross-sectional jump is formed in the Level a backflow zone or backflow bubble forms.
  • the swirl strength in the swirl generator is made chosen so that the vertebra does not burst within the mixing section, but further downstream takes place, as explained above, in the area of the cross-sectional jump.
  • the swirl generator fulfills that here Function of a premix section. This consists of at least two hollow, conical, in the direction of flow nested partial bodies, whereby the respective axes of longitudinal symmetry of the individual Partial body run mutually. Form thereby the neighboring walls of the partial body in their Longitudinal extension of tangential inflow channels for a combustion air flow, being in from the partial bodies formed interior at least one fuel nozzle acts.
  • the burner changes into a diffusion mode, which then inevitably leads to high NO x emissions.
  • the burner may overheat or even burn parts of it.
  • the fuel is therefore injected as far downstream as possible so that the flame cannot strike back upstream.
  • the fuel is diluted with water vapor or nitrogen, but in both cases the efficiency is reduced.
  • the invention seeks to remedy this.
  • the Invention as characterized in the claims is the task of a burner propose precautions at the beginning, which is a good mix when using a low calorie Fuel, with minimized pollutant emissions and maximized efficiency guarantee.
  • the swirl generator receives for this purpose in addition to the air intake ducts, a second independent one Fuel guide, preferably designed as a channel, through which the low calorific fuel is introduced. This will then be adequately admixed to the combustion air flow, in such a way that there is a partial mix of the two media comes before this in the wider interior of the Swirl generator flow.
  • Another advantage of the invention is therein see that the fuel is injected isokinetically can, with which high turbulence is injected between the Fuel and the combustion air flow preventing the flame from kicking back is sustainably suppressed.
  • Fig. 1 shows the overall structure of a burner.
  • a swirl generator 100 operates Design in connection with Fig. 2 in more detail can be seen.
  • the one that forms in this swirl generator 100 Swirl flow is based on a downstream of it provided transition geometry seamlessly in transferred a transition piece 200 so that no detachment areas can form in this zone.
  • the configuration of this transition geometry is described in more detail in Fig. 3.
  • the swirl generator 100 is described below Using Fig. 2 described.
  • the cone shape of the partial body shown 101-104 in the flow direction has a certain fixed angle. Of course, depending on the operational use, can the body 101-104 in the direction of flow an increasing or decreasing Show cone inclination, similar to a trumpet. Tulip.
  • the partial bodies 101-104 have a cylindrical initial part, the 5 is described in more detail.
  • the swirl generator 100 can be pure conical, ie without the cylindrical starting part his.
  • the partial bodies 101-104 each have one offset inside and also guided tangentially Channel 121, 122, 123, 124 (see also Fig. 2) on, through which introduces a gaseous fuel 117 which is in each case via an axially extending inflow slot 131, which is parallel or quasi-parallel extends to the course of the partial body 101-104, in the tangential combustion air inlet channels 101b-104b is injected.
  • the flow cross section and the course of this inflow slot 131 is the pressure and the amount to be introduced Adjusted fuel 117.
  • the two streams namely the combustion air 115 and the gaseous Fuel 117, will be until their first mixing. before the inflow of the same into the Interior 118 happens, managed independently.
  • the Fuel 117 becomes the combustion air 115 .mu.m a stretch upstream of the tangential transition Inflow channels 101b-104b into the interior 118 mixed. This ensures that the both media until entering the interior 118 have already pre-mixed. This can be done constructively by using the fuel channels 121-124 the respective body 101-104 as an independent Guided tours are put on.
  • the flow openings of the two media 115, 117 to the level of their Mixing is designed so that the flow allow approximately the same mass flow, which is always necessary when the burner is connected an LBTU or MBTU gas is operated.
  • present the gaseous fuel 117 flows out of the gas-carrying channels 121-124, as already mentioned, via the inflow slots 131 on the inside of the combustion air flow 115.
  • the level of mixing lies, as mentioned, upstream of the Transition of the tangential inflow channels 101b-104b in the interior 118. In the interior 118 thus flows in a premixed mixture 130.
  • the flow of the Media 115, 117 interchanged his.
  • the further one Premixing section in the swirl generator 100 then ensures for the final provision of an optimal homogeneous Mixture between the two media 115. 117.
  • the combustion air 115 is additionally preheated or enriched with a recirculated exhaust gas, so this supports the degree of mixing of the two Media sustainable.
  • the swirl generator 100 is also included a central fuel nozzle 105, which acts as a head stage.
  • This fuel nozzle is preferred operated with a liquid fuel 106. It However, it is also possible to use a gaseous nozzle To operate fuel.
  • a liquid fuel 106 When bringing in of a liquid fuel 106 through the nozzle 105 there is a conical fuel profile in the cone cavity 118 107, from the tangential and under twist incoming combustion air 115 is encased.
  • the combustion air 115 flowing in here can replaced by the mixture described above 115/117 In the axial direction, the concentration of the Fuel 106 continuously through the inflowing Combustion air 115 is broken down into a mixture.
  • the swirl generator 100 also points along the tangential inflow channels 101b-104b each one Fuel line 111-114 through which a fuel 116 flows, this fuel at the transition to the interior 118 via integrated in the fuel line Openings in the combustion air flow 115 is injected. Operation of the burner with fuel from lines 111-114, because the tangential fuel channels 121-124 not up to the transition into the interior 118 of the Swirl generator 100 are sufficient.
  • the number of tapered body parts 101-104 is not limited to four. Swirl generator with only are two tangential inflow channels too possible.
  • the transition piece 200 is on the outflow side the transition geometry (see FIG. 3) by a Mixing tube 20 extended, both parts of the actual Form mixing section 220.
  • the mixing section 220 consist of a single piece, i.e. then that the transition piece 200 and that Mixing tube 20 into a single coherent Forms merge, the characteristics of each part are preserved.
  • a transition piece 200 and mixing tube 20 made of two parts they are through a bushing ring 10 connected, the same socket ring 10 on the head side serves as anchoring surface for the swirl generator 100.
  • Such a bushing ring 10 also has the advantage that different mixing tubes are used can change anything without changing the basic configuration to have to.
  • the mixing section 220 largely fulfills the task that downstream of the swirl generator 100 a defined route is provided, in which a perfect premixing of different fuelskind can be achieved.
  • This mixing section so superficially the mixing tube 20 further enables a lossless flow, so that too in active connection with the transition geometry initially no backflow zone or backflow bubble can form, thus over the length of the mixing section 220 influence on the quality of the mixture for all types of fuel can be exercised.
  • This mixing section 220 but has another property, which is in it there is in it itself the axial velocity profile has a pronounced maximum on the axis, so that the flame reignites from the combustion chamber not possible.
  • the mixing tube 20 in Flow and circumferential direction with a number regularly or irregularly distributed holes 21 different cross sections and directions provided, through which an amount of air into the interior of the Mixing tube 20 flows, and along the wall in the sense a filming an increase in the flow rate induce.
  • These holes 21 can also be designed so that it is on the inner wall of the mixing tube 20 at least additionally sets an effusion cooling.
  • transition channels 201 which the form the transition geometry already mentioned, a Undergoes narrowing, reducing the overall speed level raised within the mixing tube 20 becomes.
  • these bores 21 run below at an acute angle with respect to the burner axis 60.
  • the outlet of the transition channels corresponds 201 the narrowest flow cross section of the Mixing tube 20.
  • the mentioned transition channels 201 bridge the respective cross-sectional difference, without making the flow negative to influence.
  • the combustion chamber 30 has an end face, insofar as this Not by other means, is occupied, for example, by pilot burners Number of openings 31 through which an amount of air flows directly into the cross-sectional jump, and there among other things helps that the ring stabilization the backflow zone 50 is strengthened.
  • Danebst It should not go unmentioned that the generation of a stable backflow zone 50 a sufficiently high Twist number in a pipe required. It is one Initially undesirable, stable backflow zones can occur by supplying small, highly swirled air currents at the pipe end, for example by tangential openings. It goes one assumes here that the amount of air required for this is about 5-20% of the total air volume.
  • the design of the burner front 70 in the end of the mixing tube 20 to stabilize the backflow zone or backflow bladder 50 is concerned with the Description under Fig. 4 referenced.
  • transition piece 200 in three dimensions View.
  • the transition geometry is for a swirl generator 100 with four partial bodies, accordingly 1, 2 constructed. Accordingly shows the transition geometry as a natural extension the upstream partial body has four transition channels 201 on, making the cone area the partial body mentioned is extended until it Wall of the mixing tube cuts the same considerations also apply if the swirl generator is off another principle than that described under Fig. 1, 2, is constructed.
  • the down in the flow direction running area of each Transition channels 201 have one in the flow direction spiral shape, which one describes crescent shape, according to the The fact that there is a flow cross-section of the transition piece 200 in the flow direction flared.
  • the twist angle of the Transition channels 201 in the flow direction is like this chosen that the pipe flow then up to the cross-sectional jump at the combustion chamber inlet there is a sufficient distance to make a perfect one Premix with the injected fuel accomplish. It also increases through the above measures mentioned also the axial speed on the mixing tube wall downstream of the swirl generator.
  • the Transition geometry and the measures in Area of the mixing tube cause a significant increase of the axial velocity profile to the center of the mixing tube, so that there is a risk of Early ignition is decisively counteracted.
  • the cross section of the tube 20 is obtained in this Area a transition radius R, its size basically from the flow inside the pipe 20 depends.
  • This radius R is chosen so that the flow applies to the wall and so the swirl number can rise sharply.
  • the size can be quantified of the radius R so that this> 10% of the Inner diameter d of the tube 20. Across from a flow without a radius now increases the backflow bladder 50 tremendous.
  • This radius R runs to the exit plane of the tube 20, the Angle ⁇ between the beginning and end of the curvature ⁇ Is 90 °.
  • the tear-off edge A runs inside the tube 20 and thus forms a demolition step S compared to the front Point of the tear-off edge A, the depth of which is> 3 mm is.
  • this can be parallel to the exit level of the pipe 20 running edge a curved course again at the exit level to be brought.
  • the angle ⁇ 'that is between Tangent of the tear-off edge A and perpendicular to Extending plane of the tube 20 is the same as large as angle ⁇ .
  • the benefits of this training this Tear edge go from EP-0 780 629 A2 under Dem Chapter "Presentation of the invention".
  • Another Design of the tear-off edge for the same purpose with torus-like notches on the combustion chamber side to reach. This publication is inclusive the scope of protection there what the tear-off edge concerns an integrating component of the present Description.
  • Fig. 5 shows a schematic view of the 1, in particular here the washing around a centrally arranged fuel nozzle 105 and on the effect of fuel injectors 170 is pointed out.
  • the mode of action of the rest Main components of the burner, namely swirl generator 100 and transition piece 200 is above have been described in more detail.
  • the fuel nozzle 105 is encased with a spaced ring 190, in which has a number scheduled in the circumferential direction Bores 161 are placed through which an amount of air 160 flows into an annular chamber 180 and there flushes the fuel lance. These holes 161 are slanted forward such that an adequate axial component arises on the burner axis 60.
  • additional fuel injectors 170 provided which a certain Amount preferably a gaseous fuel enter 160 in the respective air volume, in such a way that there is a uniform fuel concentration in the mixing tube 20 150 over the flow cross section sets how the representation in the figure symbolizes want.
  • Exactly this uniform fuel concentration 150, especially the strong concentration on the burner axis 60 ensures that a Stabilization of the flame front at the exit of the Brenners sets, with which occurring combustion chamber pulsations be avoided.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Gas Burners (AREA)
  • Sorption Type Refrigeration Machines (AREA)

Claims (17)

  1. Brûleur pour faire fonctionner un générateur de chaleur, le brûleur étant constitué essentiellement d'un générateur de tourbillon ayant au moins deux canaux d'entrée à action tangentielle pour un courant d'air de combustion, de moyens d'injection d'au moins un combustible dans le courant d'air de combustion, le générateur de tourbillon étant monté en aval d'une section de mélange qui a, dans une première partie de la section, dans le sens du courant, un certain nombre de canaux de transition pour la transmission d'un courant formé dans le générateur de tourbillon à un tube de mélange monté en aval de ces canaux de transition, caractérisé en ce qu'il est prévu, en coopération avec au moins l'un des canaux (101b à 104b) tangentiels d'entrée, un deuxième canal (121 à 124) s'étendant parallèlement ou quasi parallèlement et dans lequel passe du combustible, et en ce que le canal (121 à 124) dans lequel passe du combustible se termine autour d'une section en amont de la transition du canal (101b à 104b) tangentiel d'entrée en une chambre (118) intérieure du générateur (100) de tourbillon.
  2. Brûleur suivant la revendication 1, caractérisé en ce que le canal (121 à 124) dans lequel passe du carburant se termine par une fente (131) d'entrée dans le canal (101 b à 104b) tangentiel d'entrée.
  3. Brûleur suivant la revendication 2, caractérisé en ce que la forme (131) d'entrée est munie de moyens facilitant le passage du courant.
  4. Brûleur suivant la revendication 1, caractérisé en ce que le générateur (100) de tourbillon est constitué d'au moins deux sous-corps (101 à 104) creux, coniques et emboítés l'un dans l'autre dans la direction du courant, en ce que les axes (101a à 104a) de symétrie longitudinale respectifs de ces sous-corps sont décalés les uns par rapport aux autres de façon à ce que les parois voisines des sous-corps forment dans leur étendue longitudinale des canaux (101b à 104b) d'entrée d'un courant (115) d'air de combustion dans la chambre (118) intérieure, et en ce que, dans la chambre (108) intérieure formée par les sous-corps (101 à 104), d'autres buses (105, 116) de combustible peuvent être mises en action.
  5. Brûleur suivant les revendications 1 et 4, caractérisé en ce que le brûleur peut fonctionner par l'intermédiaire des canaux (121 à 124) dans lesquels passe du combustible avec un combustible (117) gazeux à faible valeur calorifique par des conduits (111, 114) pour du combustible le long de la transition des canaux (101b à 104b) tangentiels d'entrée dans la chambre (118) intérieure avec du combustible (116) gazeux de forte valeur calorifique et par une buse (105) pour du combustible disposée centralement du côté de la tête du générateur (100) de tourbillon avec un combustible (106) liquide.
  6. Brûleur suivant la revendication 4, caractérisé en ce que les sous-corps (101 à 104) ont, dans la direction du courant, un angle de cône fixe ou une inclinaison de cône croissante ou une inclinaison de cône décroissante.
  7. Brûleur suivant la revendication 4, caractérisé en ce que les sous-corps (101 à 104) sont emboítés l'un dans l'autre en forme de spirale.
  8. Brûleur suivant la revendication 4, caractérisé en ce que la buse (105) de combustible disposée du côté de la tête est entourée d'un anneau (190) concentrique, en ce que cet anneau (190) a un certain nombre de trous (161) disposés dans la direction du pourtour, et en ce qu'un autre combustible (161) peut être injecté dans une quantité (160) d'air passant par les trous (161).
  9. Brûleur suivant la revendication 8, caractérisé en ce que les trous (161) sont inclinés vers l'avant.
  10. Brûleur suivant la revendication 8, caractérisé en ce que la buse (105) pour du combustible est entourée d'une chambre (180) annulaire pour de l'air.
  11. Brûleur suivant la revendication 1, caractérisé en ce que le nombre des canaux (201) de transition dans la section (220) de mélange correspond au nombre des sous-courants formés par le générateur (100) de tourbillon.
  12. Brûleur suivant la revendication 1, caractérisé en ce que le tube (20) de mélange en aval des canaux (201) de transition est muni dans la direction du courant et dans la direction du pourtour d'ouvertures (21) d'injection d'un courant d'air à l'intérieur du tube (20) de mélange.
  13. Brûleur suivant la revendication 12, caractérisé en ce que les ouvertures (21) s'étendent en faisant un angle aigu avec l'axe (60) de brûleur du tube (20) de mélange.
  14. Brûleur suivant la revendication 1, caractérisé en ce que la section transversale de passage du tube (20) de mélange est, en aval des canaux (201) de transition, inférieure, égale ou supérieure à la section transversale du courant (40) formé dans le générateur (100) de tourbillon.
  15. Brûleur suivant la revendication 1, caractérisé en ce qu'il est disposé, en aval de la section (220) de mélangé, une chambre (30) de combustion, en ce qu'il y a entre la section (220) de mélange et la chambre (30) de combustion un saut de section transversale qui induit une section transversale initiale de courant de la chambre (30) de combustion, et en ce qu'une zone (50) de reflux peut agir dans la région de ce saut de section transversale.
  16. Brûleur suivant la revendication 15, caractérisé en ce qu'en amont de la zone (50) de reflux est prévu un diffuseur et/ou une section à venturi.
  17. Brûleur suivant la revendication 1, caractérisé en ce que le tube (20) de mélange a, du côté de la chambre (30) de combustion, un bord (A) de décollement.
EP97810894A 1997-11-21 1997-11-21 Brûleur pour la mise en oeuvre d'un générateur de chaleur Expired - Lifetime EP0918191B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
DE59710380T DE59710380D1 (de) 1997-11-21 1997-11-21 Brenner für den Betrieb eines Wärmeerzeugers
EP97810894A EP0918191B1 (fr) 1997-11-21 1997-11-21 Brûleur pour la mise en oeuvre d'un générateur de chaleur
AT97810894T ATE244380T1 (de) 1997-11-21 1997-11-21 Brenner für den betrieb eines wärmeerzeugers
US09/192,531 US6155820A (en) 1997-11-21 1998-11-17 Burner for operating a heat generator
JP33132098A JP4130716B2 (ja) 1997-11-21 1998-11-20 熱発生器を稼働するためのバーナ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97810894A EP0918191B1 (fr) 1997-11-21 1997-11-21 Brûleur pour la mise en oeuvre d'un générateur de chaleur

Publications (2)

Publication Number Publication Date
EP0918191A1 EP0918191A1 (fr) 1999-05-26
EP0918191B1 true EP0918191B1 (fr) 2003-07-02

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EP97810894A Expired - Lifetime EP0918191B1 (fr) 1997-11-21 1997-11-21 Brûleur pour la mise en oeuvre d'un générateur de chaleur

Country Status (5)

Country Link
US (1) US6155820A (fr)
EP (1) EP0918191B1 (fr)
JP (1) JP4130716B2 (fr)
AT (1) ATE244380T1 (fr)
DE (1) DE59710380D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7445445B2 (en) 2003-09-01 2008-11-04 Alstom Technology Ltd. Burner having a burner lance and staged fuel injection

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US6769903B2 (en) 2000-06-15 2004-08-03 Alstom Technology Ltd Method for operating a burner and burner with stepped premix gas injection
DE10029607A1 (de) * 2000-06-15 2001-12-20 Alstom Power Nv Brenner mit gestufter Vormischgas-Eindüsung
GB2368386A (en) 2000-10-23 2002-05-01 Alstom Power Nv Gas turbine engine combustion system
US7681104B1 (en) * 2004-08-09 2010-03-16 Bakbone Software, Inc. Method for erasure coding data across a plurality of data stores in a network
CN100559080C (zh) 2004-10-18 2009-11-11 阿尔斯通技术有限公司 燃气轮机用的燃烧器
US7421843B2 (en) * 2005-01-15 2008-09-09 Siemens Power Generation, Inc. Catalytic combustor having fuel flow control responsive to measured combustion parameters
EP1856447B1 (fr) * 2005-03-09 2014-09-24 Alstom Technology Ltd Bruleur a premelange pour une chambre de combustion
DE502006007733D1 (de) * 2005-03-09 2010-10-07 Alstom Technology Ltd Vormischbrenner zum erzeugen eines zündfähigen brennstoff-luftgemisches
CA2537685C (fr) * 2006-02-24 2013-05-14 9131-9277 Quebec Inc. Injecteur de combustible, bruleur et methode d'injection
EP1985924A1 (fr) * 2007-04-23 2008-10-29 Siemens Aktiengesellschaft Dispositif de tourbillonnement
US8650881B2 (en) * 2009-06-30 2014-02-18 General Electric Company Methods and apparatus for combustor fuel circuit for ultra low calorific fuels
EP2685160B1 (fr) * 2012-07-10 2018-02-21 Ansaldo Energia Switzerland AG Brûleur de prémélange du type multi-cônes destiné à une turbine à gaz
EP2685161B1 (fr) * 2012-07-10 2018-01-17 Ansaldo Energia Switzerland AG Agencement de chambre de combustion, en particulier pour turbine à gaz
EP2685163B1 (fr) 2012-07-10 2020-03-25 Ansaldo Energia Switzerland AG Brûleur de prémélange du type multi-cônes destiné à une turbine à gaz
KR20150032914A (ko) * 2012-08-01 2015-03-30 쓰리엠 이노베이티브 프로퍼티즈 컴파니 적어도 하나의 다중 입구 포트 및/또는 다중 출구 포트를 가진 연료 분사기 노즐
JP5584260B2 (ja) * 2012-08-08 2014-09-03 日野自動車株式会社 排気浄化装置用バーナー
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CA2830031C (fr) * 2012-10-23 2016-03-15 Alstom Technology Ltd. Bruleur pour chambre de combustion tubulaire unique
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Also Published As

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US6155820A (en) 2000-12-05
JP4130716B2 (ja) 2008-08-06
JPH11223306A (ja) 1999-08-17
ATE244380T1 (de) 2003-07-15
DE59710380D1 (de) 2003-08-07
EP0918191A1 (fr) 1999-05-26

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