EP0433790B1 - Burner - Google Patents

Burner

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Publication number
EP0433790B1
EP0433790B1 EP90123495A EP90123495A EP0433790B1 EP 0433790 B1 EP0433790 B1 EP 0433790B1 EP 90123495 A EP90123495 A EP 90123495A EP 90123495 A EP90123495 A EP 90123495A EP 0433790 B1 EP0433790 B1 EP 0433790B1
Authority
EP
European Patent Office
Prior art keywords
burner
fuel
injector
duct
inlet
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
EP90123495A
Other languages
German (de)
French (fr)
Other versions
EP0433790A1 (en
Inventor
Jakob Dr. Keller
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 Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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Filing date
Publication date
Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0433790A1 publication Critical patent/EP0433790A1/en
Application granted granted Critical
Publication of EP0433790B1 publication Critical patent/EP0433790B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F23D2210/00—Noise abatement

Definitions

  • the present invention relates to a burner according to the preamble of claim 1. It also relates to a method for operating such a burner.
  • a burner is known from EP-A1-0 321 809, which consists of two half-hollow partial cone bodies which are offset from one another.
  • the cone shape of the partial cone body shown in the figure extends over a certain fixed angle in the flow direction.
  • the aforementioned displacement of the partial cone bodies relative to one another creates on both sides of the burner body a tangential entry slot over the entire length of the burner, the width of which corresponds to the respective offset of the central axes of the partial cone bodies to one another, and through which the combustion air flows into the interior of the burner.
  • a fuel nozzle is placed in the interior at the beginning of the burner, the fuel injection of which preferably starts in the center of the mutually offset central axes of the partial cone bodies. Further fuel nozzles are provided in the area of the tangential inlet slots. Liquid fuel is preferably supplied through the central fuel nozzle, while the fuel nozzles in the region of the tangential inlet slots are preferably operated with a gaseous fuel. If such a burner is now operated with a medium-calorific gas, which generally contains highly flammable hydrogen, there is a concrete risk that the combustion air that is brought in is present and mix this gas so strongly already in the entry area, at the point of their meeting, that the mixture may ignite prematurely.
  • a medium-calorific gas which generally contains highly flammable hydrogen
  • the invention seeks to remedy this.
  • the invention is based on the object of providing measures in a burner of the type mentioned at the outset which make it possible to ignite the mixture prematurely when a medium-calorific gas is used as fuel.
  • the measures should also enable the mixing process to be stabilized.
  • the main advantage of the invention is that the NO x emissions remain low because there is no premature ignition.
  • the injector which forms the solution according to the task, makes it possible not to significantly change the flow field of the burner used, despite the high mass flow share of the medium-calorific gas in the air / gas mixture.
  • This is achieved with the aid of a suitable distribution of a number of injector bores of the same size or with the aid of an arrangement of bores whose diameter varies in a suitable manner.
  • the Density of the gas inlet holes (P GB ) proportional to the radially averaged combustion air inlet speed through the tangential air inlet slots of the burner.
  • the injector according to the invention does not allow shear layers to arise during the mixing process: these shear layers, which always arise when the velocity of the gaseous fuel at the mixing location is greater than the air velocity, cause strong turbulence, which triggers instability in the system.
  • these shear layers which always arise when the velocity of the gaseous fuel at the mixing location is greater than the air velocity, cause strong turbulence, which triggers instability in the system.
  • the mixing process is designed for full load with regard to the flow rate of the gaseous fuel: the gaseous fuel is "breathed" into the air flow almost without pressure.
  • Another advantage of the invention can be seen in the fact that, in suitable temperature and pressure ranges, even combustion of gases with a low calorific value is conceivable.
  • FIGS. 1 and 2 should be used simultaneously. Furthermore, so that FIG. 1 remains clear, the injectors shown in FIG. 2 have not been included.
  • Fig. 1 shows a burner 1, which consists of two half, hollow partial cone bodies 2, 3, which are offset from one another.
  • the conical shape of the partial conical bodies 2, 3 shown has a certain fixed angle in the flow direction.
  • the partial cone bodies 2, 3 can have an increasing taper (convex shape) or a decreasing taper (concave shape) in the direction of flow.
  • the latter two forms are not recorded in the drawing, since they can be easily traced. Which form is ultimately used depends on the various parameters of the combustion process.
  • the form shown in the drawing is preferably used.
  • the offset of the respective central axis 2a, 3a see FIG.
  • the entry slot width S is a measure that results from the displacement of the two central axes 2a, 3a of the partial cone bodies 2, 3.
  • the two partial cone bodies 2, 3 each have a cylindrical initial part 2c, 3c, which, like the partial cone bodies 2, 3, also run offset from one another, so that the tangential entry slots 2b, 3b are present from the start.
  • the burner 1 can of course describe a purely conical shape, that is to say without a cylindrical starting body.
  • a nozzle is accommodated in this cylindrical starting body, which is preferably operated with a liquid fuel 5 and whose fuel injection 15 is preferably placed in the center of the two central axes 2a, 3a.
  • the two partial cone bodies 2, 3 each have a fuel line 10, 11, which are provided with openings 21 in the flow direction, which are distributed over the entire length of the fuel lines.
  • a gaseous fuel 6 is preferably introduced through the fuel lines 10, 11, this fuel being injected in the region of the tangential inlet slots 2b, 3b, as can be seen particularly well from FIG. 2.
  • the burner 1 also has a fuel supply, preferably a gaseous fuel 4, which takes place via injectors 12, 13, which also act in the region of the tangential inlet slots 2b, 3b via a number of gas bores 14, as can be seen comprehensively from FIG. 2.
  • a fuel supply preferably a gaseous fuel 4
  • FIG. 2 It is basically the case that the burner 1 can be operated via individual fuel feeds or through a mixed operation with the available fuel options.
  • the burner 1 On the combustion chamber side 22, the burner 1 has a collar-shaped wall 20, through which holes, not shown, are provided, through which dilution air or cooling air is supplied to the front part of the combustion chamber 22.
  • This fuel injection 15 can be an air-assisted atomization or a pressure atomization.
  • the conical liquid fuel profile 16 is enclosed by a trangentially flowing combustion air stream 8 and an axially brought in further air stream 7a. About the composition of the tangential inflowing air / fuel mixture 8 is discussed in more detail in the description of FIG. 2. In the axial direction of the burner 1, the concentration of the injected liquid fuel 5 is continuously reduced by an air flow or by the air / fuel mixture 8.
  • gaseous fuel 6 is used via the two fuel lines 10, 11, the mixture formation begins with the invisible air supply (see FIG. 2, item 7) directly in the region of the tangential inlet slots 2b, 3b, corresponding to the fuel openings 21 provided there
  • the combustion process of each air / fuel mixture then begins at the top of this backflow zone 18. Only at this point can a stable flame front 19 arise. A flashback of the flame inside the burner 1 like this With known premixing sections, there is always no need to worry, whereas complex flame holders are sought to remedy this situation.
  • the air used (see FIG. 2, item 7) is preheated at most, accelerated, holistic evaporation of the liquid fuel 5 occurs before the point at the outlet of the burner 1 is reached at which the combustion process of the mixture begins.
  • the degree of evaporation is dependent on the size of the burner 1, the drop size and the temperature of the air streams 7a, 7 respectively. of the air / fuel mixture 8 dependent.
  • the nitrogen oxide and carbon monoxide emissions are low if the excess air is at least 60%, which means an additional one precaution to minimize NOx emissions is available.
  • the geometrically fixed return flow zone 18 is inherently position-stable, because the swirl number increases in the direction of flow in the region of the cone shape of the burner 1.
  • the axial speed leaves further influence each other by axially feeding the already mentioned air flow 7a.
  • the design of the burner 1 is ideally suited, given a given overall length of a burner 1, to adapt the size of the tangential entry slots 2b, 3b to the requirements by pushing the partial cone bodies 2, 3 towards or away from one another, as a result of which the distance between the two central axes 2a, 3a reduced or increases, and accordingly the entry slot width S also changes, as can be seen particularly well from FIG. 2.
  • the partial cone bodies 2, 3 can also be moved relative to one another in another plane. Seen in this way, the burner 1 can be individually adapted without changing its focal length.
  • the injector 12, 13 is designed in such a way that the gaseous fuel 4, which is preferably used, flows from a gas supply pipe 12a, 13a through which a gas can flow, via a number of gas bores 14, into a gas injector channel (injection channel) 12b, 13b. This extends into the area of the tangential entry slot 2b, 3b.
  • the width of the injector 12, 13 is designed such that the air 7 that is brought in flows along the flanks of the injector 12, 13 and begins to mix with the gaseous fuel 4 in the region of the tangential inlet slot 2b, 3b, whereupon the air / Fuel mixture 8 is formed.
  • the property of the injector 12, 13 of not significantly changing the flow field of the burner 1 despite the high mass flow portion of the medium-calorific gas used in the air / gas mixture. This is achieved with the help of a suitable distribution of the gas holes 14 of the same size or with the help an arrangement of holes, the diameter of which varies in a suitable manner.
  • the density of the gas holes is proportional to the radially averaged speed of the air 7 in the inlet slots 2b, 3b of the burner 1, and follows the following formula: where ⁇ is the opening angle of the burner 1 (see FIG. 1), S denotes the entry slot width and R is the mean radius of the position of the entry slot 2b, 3b in question (see FIG. 1).
  • the directions of the gas bores 14 should preferably coincide with the prevailing flow direction in the inlet slot 2b, 3b. It is important that the gaseous fuel 4 undergoes the actual throttling when it enters the gas bores 14 from the gas supply channel 12a, 13a.
  • the gas holes 14 are to be designed in such a way that they cannot be freely blown into the interior 17 of the burner 1. These gas holes 14 open into a gas injector channel 12b, 13b, which extends as far as the inlet slot 2b, 3b. It is advantageous if this channel is divided several times in the longitudinal direction by flow plates that cannot be seen, so that the gaseous fuel 4 is channeled in the direction of the combustion air flow under design conditions, for example full load. Furthermore, aid is provided that the gaseous fuel 4 blows at the respective speed of the air 7 brought in in the area of the inlet slots 2b, 3b.
  • the transition from the gas holes 14 to the subsequent gas injector channels 12b, 13b is preferably designed as a Borda-Carnot extension.
  • the minimum length of the gas injector channel is concerned, the usual rule of 3-5 hydraulic diameters resp. 6 - 10 gap width used.

Abstract

A burner (1), with a conical shape opening in the direction of flow, is composed of two part cone members (2, 3) which are positioned on top of one another and the central axes (2a, 3a) of which run in a displaced manner in relation to one another in the longitudinal direction. From this displacement, a tangential inlet slot to the interior (17) of the burner (1) is in each case formed over the length of the burner (1). The fuel supply takes place centrally via a nozzle (9) and tangentially in the region of the inlet slots via a fuel pipe (10, 11) in each case, which is provided with fuel openings (21) which there take on the injection of the fuel (6). Above each inlet slot, a duct is formed, which is equipped with an injector (12, 13). Additional fuel (4) is introduced by this injector. The air/fuel mixture with fuel from the injector (12, 13) and/or fuel from the fuel pipe (10, 11) flows generally in the form of an air/fuel mixture (8) through the tangential inlet slots into the interior (17) of the burner (1). There, if necessary, further mixing with the fuel (5) from the nozzle (9) takes place. <IMAGE>

Description

Die vorliegende Erfindung betrifft einen Brenner gemäss Oberbegriff des Anspruchs 1. Sie betrifft auch ein Verfahren zum Betrieb eines solchen Brenners.The present invention relates to a burner according to the preamble of claim 1. It also relates to a method for operating such a burner.

STAND DER TECHNIKSTATE OF THE ART

Aus EP-A1-0 321 809 ist ein Brenner bekanntgeworden, der aus zwei halben hohlen Teilkegelkörper besteht, die versetzt zueinander aufeinander liegen. Die Kegelform der in der dortigen Figur gezeigten Teilkegelkörper erstreckt sich in Strömungsrichtung über einen bestimmten festen Winkel. Die erwähnte Versetzung der Teilkegelkörper zueinander schafft auf beiden Seiten des Brennerkörpers jeweils einen über die ganze Länge des Brenners tangentialen Eintrittsschlitz, dessen Breite der jeweiligen Versetzung der Mittelachsen der Teilkegelkörper zueinander entspricht, und durch welchen die Verbrennungsluft in den Innenraum des Brenners strömt.A burner is known from EP-A1-0 321 809, which consists of two half-hollow partial cone bodies which are offset from one another. The cone shape of the partial cone body shown in the figure extends over a certain fixed angle in the flow direction. The aforementioned displacement of the partial cone bodies relative to one another creates on both sides of the burner body a tangential entry slot over the entire length of the burner, the width of which corresponds to the respective offset of the central axes of the partial cone bodies to one another, and through which the combustion air flows into the interior of the burner.

Im Innenraum am Anfang des Brenners ist eine Brennstoffdüse plaziert, deren Brennstoffeindüsung vorzugsweise mittig der zueinander versetzten Mittelachsen der Teilkegelkörper ausgeht. Im Bereich der tangentialen Eintrittsschlitze sind weitere Brennstoffdüsen vorgesehen. Durch die zentrale Brennstoffdüse wird vorzugsweise flüssiger Brennstoff herangeführt, während die Brennstoffdüsen im Bereich der tangentialen Eintrittsschlitze vorzugsweise mit einem gasförmigen Brennstoff betrieben werden. Wird nun ein solcher Brenner mit einem mittelkalorischen Gas, das in der Regel leicht entzündlichen Wasserstoff enthält, betrieben, so besteht die konkrete Gefahr, dass sich die herangeführte Verbrennungsluft und dieses Gas bereits im Eintrittsbereich, am Ort ihres Zusammentreffens, derart stark vermischen, dass es zu einer verfrühten Zündung des Gemisches kommen kann. Dies wiederum würde zu einer diffusionsartigen Verbrennung mit stark erhöhter NOx-Emission führen. Danebst ist feststellbar, dass bei einer solchen Vermischung Luft/Gas leicht Scherschichten entstehen können, worauf eine Instabilität des Mischvorganges infolge starker Verwirbelungen die Folge ist. Kommt es auf die Zuführung des Gases wegen obengenannter Instabilität zu Druckpulsationen, so führt dies, darüber hinaus, zu starken Schwingungen im System.A fuel nozzle is placed in the interior at the beginning of the burner, the fuel injection of which preferably starts in the center of the mutually offset central axes of the partial cone bodies. Further fuel nozzles are provided in the area of the tangential inlet slots. Liquid fuel is preferably supplied through the central fuel nozzle, while the fuel nozzles in the region of the tangential inlet slots are preferably operated with a gaseous fuel. If such a burner is now operated with a medium-calorific gas, which generally contains highly flammable hydrogen, there is a concrete risk that the combustion air that is brought in is present and mix this gas so strongly already in the entry area, at the point of their meeting, that the mixture may ignite prematurely. This in turn would lead to a diffusion-like combustion with a greatly increased NO x emission. In addition, it can be ascertained that with such a mixture of air / gas, shear layers can easily arise, which results in instability of the mixing process as a result of strong turbulence. If there is pressure pulsation due to the instability mentioned above, this also leads to strong vibrations in the system.

AUFGABE DER ERFINDUNGOBJECT OF THE INVENTION

Hier will die Erfindung Abhilfe schaffen. Der Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, liegt die Aufgabe zugrunde, bei einem Brenner der eingangs genannten Art Massnahmen vorzusehen, die bei Verwendung eines mittelkalorischen Gases als Brennstoff eine Frühzündung des Gemisches verunmöglichen. Die Massnahmen sollen auch eine Stabilisierung des Mischvorganges ermöglichen.The invention seeks to remedy this. The invention, as characterized in the claims, is based on the object of providing measures in a burner of the type mentioned at the outset which make it possible to ignite the mixture prematurely when a medium-calorific gas is used as fuel. The measures should also enable the mixing process to be stabilized.

Der wesentliche Vorteil der Erfindung ist darin zu sehen, dass die NOx-Emissionen, da es zu keiner verfrühten Zündung kommt, tief bleiben.The main advantage of the invention is that the NO x emissions remain low because there is no premature ignition.

Ein weiterer wesentlicher Vorteil der Erfindung ist darin zu sehen, dass der Injektor, der die aufgabengemässe Lösung bildet, ermöglicht, das Strömungsfeld des zum Einsatz kommenden Brenners, trotz des hohen Massenstromanteils des mittelkalorischen Gases am Luft/Gas-Gemisch, nicht nennenswert zu verändern. Dies gelingt mit Hilfe einer geeigneten Verteilung einer Anzahl von Injektorbohrungen gleicher Grösse oder mit Hilfe einer Anordnung von Bohrungen, deren Druchmesser in geeigneter Weise variiert. Dabei ist die Dichte der Gaseintrittsbohrungen (PGB) proportional zur radial gemittelten Verbrennungslufteintrittsgeschwindigkeit durch die tangentialen Lufteintrittsschlitze des Brenners.Another important advantage of the invention is that the injector, which forms the solution according to the task, makes it possible not to significantly change the flow field of the burner used, despite the high mass flow share of the medium-calorific gas in the air / gas mixture. This is achieved with the aid of a suitable distribution of a number of injector bores of the same size or with the aid of an arrangement of bores whose diameter varies in a suitable manner. Here is the Density of the gas inlet holes (P GB ) proportional to the radially averaged combustion air inlet speed through the tangential air inlet slots of the burner.

Der erfindungsgemässe Injektor lässt des weiteren Scherschichten beim Mischvorgang nicht entstehen: Diese Scherschichten, die immer dann entstehen, wenn die Geschwindigkeit des gasförmigen Brennstoffes am Mischort grösser als die Luftgeschwindigkeit ist, bewirken starke Verwirbelungen, welche eine Instabilität des Systems auslösen. Indem nun der Injektor so ausgelegt ist, dass am Mischort die beiden Medien mit nahezu gleicher Geschwindigkeit aufeinander treffen, treten dort keine Turbulenzen auf; auch entstehen dort keine Druckpulsationen, welche eine negative Auswirkung auf den Misch- und Brennvorgang hätten, so dass Schwingungen auf das System ausgeschlossen sind. Der Mischvorgang ist bezüglich Strömungsgeschwindigkeit des gasförmigen Brennstoffes auf Vollast ausgelegt: Der gasförmige Brennstoff wird annähernd drucklos in die Luftströmung "eingehaucht". Weitere Vorteile der Erfindung betreffen die Vermeidung der akustischen Härte bei der Eindüsung des Brennstoffes: Indem die Spaltbreite und die Länge des Injektors entsprechend ausgelegt ist, kann sich die Strömung vor Verlassen des Injektors soweit erholen, dass die erwähnte akustische Härte nicht entstehen kann.Furthermore, the injector according to the invention does not allow shear layers to arise during the mixing process: these shear layers, which always arise when the velocity of the gaseous fuel at the mixing location is greater than the air velocity, cause strong turbulence, which triggers instability in the system. By designing the injector so that the two media meet at the mixing location at almost the same speed, there is no turbulence; there are also no pressure pulsations which would have a negative effect on the mixing and burning process, so that vibrations on the system are excluded. The mixing process is designed for full load with regard to the flow rate of the gaseous fuel: the gaseous fuel is "breathed" into the air flow almost without pressure. Further advantages of the invention relate to the avoidance of the acoustic hardness when the fuel is injected: by designing the gap width and the length of the injector accordingly, the flow can recover before leaving the injector to such an extent that the acoustic hardness mentioned cannot arise.

Ein weiterer Vorteil der Erfindung ist darin zu sehen, dass in geeigneten Temperatur- und Druckbereichen sogar eine Verbrennung von Gasen mit niedrigem Heizwert denkbar ist.Another advantage of the invention can be seen in the fact that, in suitable temperature and pressure ranges, even combustion of gases with a low calorific value is conceivable.

Vorteilhafte und zweckmässige Wetierbildungen der erfindungsgemässen Aufgabenlösung sind in den weiteren Ansprüchen gekennzeichnet.Advantageous and expedient forms of watering of the task solution according to the invention are characterized in the further claims.

Im folgenden wird anhand der Zeichnung ein Ausführungsbeispiel der Erfindung näher erläutert. Alle für das unmittelbare Verständnis der Erfindung nicht erforderlichen Elemente sind fortgelassen. Die Strömungsrichtung der verschiedenen Medien ist mit Pfeilen angegeben. In den verschiedenen Figuren sind gleiche Elemente jeweils mit den gleichen Bezugszeichen versehen.An exemplary embodiment of the invention is explained in more detail below with reference to the drawing. All elements not necessary for the immediate understanding of the invention have been omitted. The direction of flow of the different media is indicated by arrows. In the different figures, the same elements are provided with the same reference numerals.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Es zeigt:

Fig.1
eine perspektivische Darstellung des Brenners, entsprechend aufgeschnitten, mit angedeuteter tangentialer Luftzuführung und
Fig.2
einen Schnitt durch die Ebene II-II von Fig. 1, in einer schematischen, vereinfachten Darstellung.
It shows:
Fig. 1
a perspective view of the burner, cut open accordingly, with indicated tangential air supply and
Fig. 2
a section through the plane II-II of Fig. 1, in a schematic, simplified representation.

BESCHREIBUNG DES AUSFÜHRUNGSBEISPIELSDESCRIPTION OF THE EMBODIMENT

Um den Aufbau des Brenners 1 besser zu verstehen, sollen die Fig. 1 und 2 gleichzeitig herangezogen werden. Des weiteren, damit Fig. 1 übersichtlich bleibt, sind die nach Fig. 2 gezeigten Injektoren nicht darin aufgenommen worden.In order to better understand the structure of the burner 1, FIGS. 1 and 2 should be used simultaneously. Furthermore, so that FIG. 1 remains clear, the injectors shown in FIG. 2 have not been included.

Fig. 1 zeigt einen Brenner 1, welcher aus zwei halben, hohlen Teilkegelkörpern 2, 3 besteht, die versetzt zueinander aufeinander liegen. Die Kegelform der gezeigten Teilkegelkörper 2, 3 weist in Strömungsrichtung einen bestimmten festen Winkel auf. Selbstverständlich können die Teilkegelkörper 2, 3 in Strömungsrichtung eine zunehmende Kegelneigung (konvexe Form) oder eine abnehmende Kegelneigung (konkave Form) aufweisen. Die beiden letztgenannten Formen sind zeichnerisch nicht erfasst, da sie ohne weiteres nachempfindbar sind. Welche Form schlussendlich zum Einsatz gelangt, hängt von den verschiedenen Parametern des Verbrennungsprozesses ab. Vorzugsweise wird die zeichnerisch gezeigte Form eingesetzt. Die Versetzung der jeweiligen Mittelachse 2a, 3a (siehe Fig. 2) der Teilkegelkörper 2, 3 zueinander schafft auf beiden Seiten des Brenners 1 in Strömungsrichtung je einen tangentialen Eintrittsschlitz 2b, 3b, mit einer bestimmten Eintrittsschlitzbreite S frei (siehe Fig. 2), durch welche die Verbrennungsluft 8 (Luft/Brennstoff-Gemisch) im Innenraum 17 des Brenners 1 strömt. Die Eintrittsschlitzbreite S ist ein Mass, das aus der Versetzung der beiden Mittelachsen 2a, 3a der Teilkegelkörper 2, 3 resultiert. Die beiden Teilkegelkörper 2, 3 haben je einen zylindrischen Anfangsteil 2c, 3c, die analog den Teilkegelkörpern 2, 3, auch versetzt zueinander verlaufen, so dass die tangentialen Eintrittsschlitze 2b, 3b von Anfang an vorhanden sind. Selbstverständlich kann der Brenner 1 eine rein kegelige Form beschreiben, also ohne einen zylindrischen Anfangskörper. In diesem zylindrischen Anfangskörper ist eine Düse untergebracht, welche vorzugsweise mit einem flüssigen Brennstoff 5 betrieben wird, und deren Brenn- stoffeindüsung 15 vorzugsweise mittig zu den beiden Mittelachsen 2a, 3a plaziert ist. Als weitere Brennstoffzuführung weisen beide Teilkegelkörper 2, 3 je eine Brennstoffleitung 10, 11 auf, welche in Strömungsrichtung mit Öffnungen 21, die über die gesamte Länge der Brennstoffleitungen verteilt sind, versehen sind. Durch die Brennstoffleitungen 10, 11, wird vorzugsweise ein gasförmiger Brennstoff 6 herangeführt, wobei dieser Brennstoff im Bereich der tangentialen Eintrittsschlitze 2b, 3b eingedüst wird, wie dies aus Fig. 2 besonders gut hervorgeht. Der Brenner 1 weist des weiteren eine Brennstoffzuführung auf, vorzugsweise eines gasförmigen Brennstoffes 4, die über Injektoren 12, 13 stattfindet, welche auch im Bereich der tangentialen Eintrittsschlitze 2b, 3b über eine Anzahl Gasbohrungen 14 wirken, wie dies umfassend aus Fig. 2 hervorgeht. Für die diesbezügliche Beschreibung wird auf Fig. 2 verwiesen. Grundsätzlich ist es so, dass der Betrieb des Brenners 1 über einzelne Brenntoffzuführungen oder durch einen Mischbetrieb mit den vorhandenen Brennstoff-Möglichkeiten möglich ist. Brennraumseitig 22 weist der Brenner 1 eine kragenförmige Wand 20 auf, durch welche, allenfalls, nicht dargestellte Bohrungen vorgesehen werden, durch welche Verdünnungsluft oder Kühlluft dem vorderen Teil des Brennraumes 22 zugeführt wird. Der durch die Düse 9 vorzugsweise in den Brenner 1 eingebrachte flüssige Brennstoff 5 wird unter einem spitzen Winkel in den Innenraum 17 eingedüst, dergestalt, dass sich in der Brenneraustrittsebene ein möglichst homogenes kegeliges Sprühbild einstellt. Bei dieser Brennstoffeindüsung 15 kann es sich um eine luftunterstützte Zerstäubung oder eine Druckzerstäubung handeln. Das kegelige Flüssigbrennstoffprofil 16 wird von einem trangential einströmenden Verbrennungsluftstrom 8 und einem achsial herangeführten weiteren Luftstrom 7a umschlossen. Über die Zusamensetzung des tangentialen einströmenden Luft/Brennstoff-Gemisches 8 wird in der Beschreibung von Fig. 2 näher eingetreten. In axialer Richtung des Brenners 1, wird die Konzentration des eingedüsten flüssigen Brennstoffes 5 fortlaufend durch eine Luftströmung oder durch das Luft/Brennstoff-Gemisch 8 abgebaut. Wird gasförmiger Brennstoff 6 über die beiden Brennstoffleitungen 10, 11 eingesetzt, beginnt die Gemischbildung mit der nicht ersichtlichen Luftzuführung (siehe Fig. 2, Pos. 7) direkt im Bereich der tangentialen Eintrittsschlitze 2b, 3b, entsprechend den dort vorgesehenen Brennstofföffnungen 21. Bei der Eindüsung von flüssigem Brennstoff 5 über die Düse 9 wird im Bereich des Wirbelaufplatzens, also im Bereich einer sich bildenden Rückströmzone 18, die optimale, homogene Brennstoffkonzentration über den Querschnitt erreicht. Der Verbrennungsvorgang jedes Luft/Brennstoff-Gemisches beginnt dann an der Spitze dieser Rückströmzone 18. Erst an dieser Stelle kann eine stabile Flammenfront 19 entstehen. Ein Rückschlag der Flamme ins Innere des Brenners 1, wie dies bei bekannten Vormischstrecken immer gegeben sein kann, wogegen dort mit komplizierten Flammenhaltern Abhilfe gesucht wird, ist hier nicht zu befürchten. Wird allgemein die eingesetzte Luft (siehe Fig. 2, Pos. 7) allenfalls vorgewärmt, so stellt sich eine beschleunigte ganzheitliche Verdampfung des flüssigen Brennstoffes 5 ein, bevor der Punkt am Ausgang des Brenners 1 erreicht ist, an dem der Verbrennungsvorgang des Gemisches beginnt. Der Grad der Verdampfung ist von der Grösse des Brenners 1, von der Tropfengrösse und von der Temperatur der Luftströme 7a, 7 resp. des Luft/Brennstoff-Gemisches 8 abhängig. Unabhängig davon, ob neben der homogenen Tropfenvermischung durch einen Verbrennungsluftrom niedriger Temperatur oder zusätzlich eine partielle oder die vollständige Tropfenverdampfung durch vorgeheizte Verbrennungsluft erreicht wird, fallen die Stickoxid-und Kohlenmonoxid-Emissionen niedrig aus, wenn der Luftüberschuss mindestens 60 % beträgt, womit hier eine zusätzliche Vorkehrung zur Minimierung der NOx-Emissionen zur Verfügung steht. Im Falle der vollständigen Verdampfung des eingesetzten Brennstoffes vor dem Eintritt in die Verbrennungszone sind die Schadstoffemissionswerte am niedrigsten. Gleiches gilt auch für den nahstöchiometrischen Betrieb, wenn die Überschussluft durch rezirkulierendes Rauchgas ersetzt wird. Bei der Gestaltung der Teilkegelkörper 2, 3 hinsichtlich Kegelwinkels und Breite der tangentialen Eintrittsschlitze 2b, 3b sind enge Grenzen einzuhalten, damit sich das gewünschte Strömungsfeld der Luft mit ihrer Rückströmzone 18 im Bereich der Brennermündung zur Flammenstabilisierung einstellt. Allgemein ist zu sagen, dass eine Verkleinerung der tangentialen Eintrittsschlitze 2b, 3b, d.h. eine Verkleinerung der Eintrittsbreite S (siehe Fig.2) die Rückströmzone 18 weiter stromaufwärts verschiebt, wodurch dann allerdings das Gemisch früher zur Zündung käme. Indessen ist festzuhalten, dass die einmal geometrisch fixierte Rückströmzone 18 an sich positionsstabil ist, denn die Drallzahl nimmt in Strömungsrichtung im Bereich der Kegelform des Brenners 1 zu. Die Achsialgeschwindigkeit lässt sich des weiteren durch axiale Zuführung des bereits erwähnten Luftstromes 7a beeinflussen. Die Konstruktion des Brenners 1 eignet sich vorzüglich, bei vorgegebener Baulänge eines Brenners 1, die Grösse der tangentialen Eintrittsschlitze 2b, 3b dem Bedarf anzupassen, indem die Teilkegelkörper 2, 3 zu- oder auseinander geschoben werden, wodurch sich der Abstand der beiden Mittelachsen 2a, 3a verkleinert resp. vergrössert, und dementsprechend sich auch die Eintrittsschlitzbreite S verändert, wie dies aus Fig. 2 besonders gut hervorgeht. Selbstverständlich sind die Teilkegelkörper 2, 3 auch in einer anderen Ebene zueinander verschiebbar. So gesehen kann der Brenner 1, ohne Veränderung seiner Brennlänge, individuell angepasst werden.Fig. 1 shows a burner 1, which consists of two half, hollow partial cone bodies 2, 3, which are offset from one another. The conical shape of the partial conical bodies 2, 3 shown has a certain fixed angle in the flow direction. Of course, the partial cone bodies 2, 3 can have an increasing taper (convex shape) or a decreasing taper (concave shape) in the direction of flow. The latter two forms are not recorded in the drawing, since they can be easily traced. Which form is ultimately used depends on the various parameters of the combustion process. The form shown in the drawing is preferably used. The offset of the respective central axis 2a, 3a (see FIG. 2) of the partial cone bodies 2, 3 relative to one another creates a tangential entry slot 2b, 3b with a certain entry slot width S on both sides of the burner 1 in the flow direction (see FIG. 2), through which the combustion air 8 (air / fuel mixture) flows in the interior 17 of the burner 1. The entry slot width S is a measure that results from the displacement of the two central axes 2a, 3a of the partial cone bodies 2, 3. The two partial cone bodies 2, 3 each have a cylindrical initial part 2c, 3c, which, like the partial cone bodies 2, 3, also run offset from one another, so that the tangential entry slots 2b, 3b are present from the start. The burner 1 can of course describe a purely conical shape, that is to say without a cylindrical starting body. A nozzle is accommodated in this cylindrical starting body, which is preferably operated with a liquid fuel 5 and whose fuel injection 15 is preferably placed in the center of the two central axes 2a, 3a. As a further fuel supply, the two partial cone bodies 2, 3 each have a fuel line 10, 11, which are provided with openings 21 in the flow direction, which are distributed over the entire length of the fuel lines. A gaseous fuel 6 is preferably introduced through the fuel lines 10, 11, this fuel being injected in the region of the tangential inlet slots 2b, 3b, as can be seen particularly well from FIG. 2. The burner 1 also has a fuel supply, preferably a gaseous fuel 4, which takes place via injectors 12, 13, which also act in the region of the tangential inlet slots 2b, 3b via a number of gas bores 14, as can be seen comprehensively from FIG. 2. For the description in this regard, reference is made to FIG. 2. It is basically the case that the burner 1 can be operated via individual fuel feeds or through a mixed operation with the available fuel options. On the combustion chamber side 22, the burner 1 has a collar-shaped wall 20, through which holes, not shown, are provided, through which dilution air or cooling air is supplied to the front part of the combustion chamber 22. The liquid fuel 5, which is preferably introduced into the burner 1 through the nozzle 9, is injected into the interior 17 at an acute angle, in such a way that the most conical spray pattern is obtained in the burner outlet plane. This fuel injection 15 can be an air-assisted atomization or a pressure atomization. The conical liquid fuel profile 16 is enclosed by a trangentially flowing combustion air stream 8 and an axially brought in further air stream 7a. About the composition of the tangential inflowing air / fuel mixture 8 is discussed in more detail in the description of FIG. 2. In the axial direction of the burner 1, the concentration of the injected liquid fuel 5 is continuously reduced by an air flow or by the air / fuel mixture 8. If gaseous fuel 6 is used via the two fuel lines 10, 11, the mixture formation begins with the invisible air supply (see FIG. 2, item 7) directly in the region of the tangential inlet slots 2b, 3b, corresponding to the fuel openings 21 provided there The injection of liquid fuel 5 through the nozzle 9 in the area of the vortex run, ie in the area of a backflow zone 18 that is formed, the optimum, homogeneous fuel concentration is achieved over the cross section. The combustion process of each air / fuel mixture then begins at the top of this backflow zone 18. Only at this point can a stable flame front 19 arise. A flashback of the flame inside the burner 1 like this With known premixing sections, there is always no need to worry, whereas complex flame holders are sought to remedy this situation. If, in general, the air used (see FIG. 2, item 7) is preheated at most, accelerated, holistic evaporation of the liquid fuel 5 occurs before the point at the outlet of the burner 1 is reached at which the combustion process of the mixture begins. The degree of evaporation is dependent on the size of the burner 1, the drop size and the temperature of the air streams 7a, 7 respectively. of the air / fuel mixture 8 dependent. Regardless of whether, in addition to homogeneous droplet mixing by means of a low-temperature combustion air flow or, in addition, partial or complete droplet evaporation is achieved by preheated combustion air, the nitrogen oxide and carbon monoxide emissions are low if the excess air is at least 60%, which means an additional one precaution to minimize NOx emissions is available. In the case of complete vaporization of the fuel used before entering the combustion zone, the pollutant emission values are lowest. The same applies to near-stoichiometric operation when the excess air is replaced by recirculating flue gas. When designing the partial cone bodies 2, 3 with regard to the cone angle and the width of the tangential inlet slots 2b, 3b, narrow limits must be observed so that the desired flow field of the air with its return flow zone 18 is established in the area of the burner mouth for flame stabilization. In general, it can be said that a reduction in the tangential inlet slots 2b, 3b, that is to say a reduction in the inlet width S (see FIG. 2), shifts the backflow zone 18 further upstream, which would cause the mixture to ignite earlier, however. In the meantime, it should be noted that the geometrically fixed return flow zone 18 is inherently position-stable, because the swirl number increases in the direction of flow in the region of the cone shape of the burner 1. The axial speed leaves further influence each other by axially feeding the already mentioned air flow 7a. The design of the burner 1 is ideally suited, given a given overall length of a burner 1, to adapt the size of the tangential entry slots 2b, 3b to the requirements by pushing the partial cone bodies 2, 3 towards or away from one another, as a result of which the distance between the two central axes 2a, 3a reduced or increases, and accordingly the entry slot width S also changes, as can be seen particularly well from FIG. 2. Of course, the partial cone bodies 2, 3 can also be moved relative to one another in another plane. Seen in this way, the burner 1 can be individually adapted without changing its focal length.

Fig. 2 ist ein Schnitt etwa in der Mitte des Brenners 1, gemäss Schnittebene II-II aus Fig. 1. Die achsensymmetrisch angeordneten Einläufe 23, 24, welche in den Innenraum 17 des Brenners 1 münden, beinhalten je einen Injektor 12, 13, der sich über die ganze tangentiale Länge des Brenners 1 erstreckt. Der Injektor 12, 13 ist so konzipiert, dass der vorzugsweise eingesetzte gasförmige Brennstoff 4 von einem durchströmbaren Gaszuführrohr 12a, 13a aus, über eine Anzahl von Gasbohrungen 14 in einen Gasinjektorkanal (Einblaskanal) 12b, 13b strömt. Dieser erstreckt sich bis in den Bereich des tangentialen Eintrittsschlitzes 2b, 3b. Die Breite des Injektors 12, 13 ist so ausgelegt, dass die herangeführte Luft 7 entlang der Flanken des Injektors 12, 13 strömt, und sich im Bereich des tangentialen Eintrittsschlitzes 2b, 3b mit dem gasförmigen Brennstoff 4 zu vermischen beginnt, worauf erst das Luft/Brennstoff-Gemisch 8 entsteht. Von grundlegender Bedeutung ist die Eigenschaft des Injektors 12, 13, das Strömungsfeld des Brenners 1 trotz des hohen Massenstromanteils des eingesetzten mittelkalorischen Gases am Luft/Gas-Gemisch nicht nennenswert zu verändern. Dies gelingt mit Hilfe einer geeigneten Verteilung der Gasbohrungen 14 gleicher Grösse oder mit Hilfe einer Anordnung von Bohrungen, deren Durchmesser in geeigneter Weise variiert. Die Dichte der Gasbohrungen, ρGB genannt, ist dabei proportional zur radial gemittelten Geschwindigkeit der Luft 7 in den Eintrittsschlitzen 2b, 3b des Brenners 1, und folgt folgender Formel:

Figure imgb0001

wobei α der Öffnungswinkel des Brenners 1 (Siehe Fig. 1) ist, S die Eintrittsschlitzbreite bezeichnet und R der mittlere Radius der jeweils betrachteten Stelle des Eintrittsschlitzes 2b, 3b ist (Siehe Fig. 1). Die Richtungen der Gasbohrungen 14 sollten vorzugsweise mit der vorherrschenden Strömungrichtung im Eintrittsschlitz 2b, 3b zusammenfallen. Dabei ist es wichtig, dass das gasförmige Brennstoff 4 die eigentliche Drosselung beim Eintritt aus dem Gaszufuhrkanal 12a, 13a in die Gasbohrungen 14 erfährt. Da mittelkalorische Gase in der Regel leicht entzündlichen Wasserstoff enthalten, sind die Gasbohrungen 14 so auszulegen, das sie nicht frei in den Innenraum 17 des Brenners 1 ausblasen können. Diese Gasbohrungen 14 münden in einen Gasinjektorkanal 12b, 13b, der sich bis zum Eintrittsschlitz 2b, 3b erstreckt. Vorteilhaft ist es, wenn dieser Kanal in Längsrichtung mehrfach durch nicht ersichtliche Strömungsbleche unterteilt ist, damit das gasförmige Brennstoff 4 unter Auslegebedingungen, beispielsweise Vollast, in Richtung der Verbrennungsluftströmung kanalisiert wird. Des weiteren wird damit Beihilfe geleistet, dass das gasförmige Brennstoff 4 mit der jeweiligen Geschwindigkeit der herangeführten Luft 7 im Bereich der Eintrittsschlitze 2b, 3b bläst. Damit wird verhindert, dass sich die Luft 7 und das zum Einsatz gelangende mittelkalorische Gas 4 bereits im Eintrittsbereich in den Innenraum 17 des Brenners 1 stark durchmischen kann, denn dies würde zwangsläufig zu einer verfrühten Zündung führen, welche eine diffusionsartige Verbrennung mit stark erhöhten NOx-Emissionen nach sich zieht. Um diese angestrebten Ziele zu erreichen, wird der Übergang von den Gasbohrungen 14 zum nachfolgenden Gasinjektorkanal 12b, 13b vorzugsweise als Borda-Carnot-Erweiterung ausgebildet. Was die Mindestlänge des Gasinjektorkanals betrifft, so wird hier mit Vorteil auf die übliche Regel der 3 - 5 hydraulischen Durchmesser resp. 6 - 10 Spaltbreite zurückgegriffen. Bei einer solchen Auslegung ist Gewähr vorhanden, dass sich die beruhigte Gasströmung 4 "hauchartig" mit der Luftströmung 7 vermischen kann, wodurch auch die akustische Härte beim Mischvorgang vermieden wird.2 is a section approximately in the middle of the burner 1, according to section plane II-II from FIG. 1. The inlets 23, 24, which are arranged axially symmetrically and which open into the interior 17 of the burner 1, each contain an injector 12, 13, which extends over the entire tangential length of the burner 1. The injector 12, 13 is designed in such a way that the gaseous fuel 4, which is preferably used, flows from a gas supply pipe 12a, 13a through which a gas can flow, via a number of gas bores 14, into a gas injector channel (injection channel) 12b, 13b. This extends into the area of the tangential entry slot 2b, 3b. The width of the injector 12, 13 is designed such that the air 7 that is brought in flows along the flanks of the injector 12, 13 and begins to mix with the gaseous fuel 4 in the region of the tangential inlet slot 2b, 3b, whereupon the air / Fuel mixture 8 is formed. Of fundamental importance is the property of the injector 12, 13 of not significantly changing the flow field of the burner 1 despite the high mass flow portion of the medium-calorific gas used in the air / gas mixture. This is achieved with the help of a suitable distribution of the gas holes 14 of the same size or with the help an arrangement of holes, the diameter of which varies in a suitable manner. The density of the gas holes, called ρ GB , is proportional to the radially averaged speed of the air 7 in the inlet slots 2b, 3b of the burner 1, and follows the following formula:
Figure imgb0001
where α is the opening angle of the burner 1 (see FIG. 1), S denotes the entry slot width and R is the mean radius of the position of the entry slot 2b, 3b in question (see FIG. 1). The directions of the gas bores 14 should preferably coincide with the prevailing flow direction in the inlet slot 2b, 3b. It is important that the gaseous fuel 4 undergoes the actual throttling when it enters the gas bores 14 from the gas supply channel 12a, 13a. Since medium-calorific gases generally contain highly flammable hydrogen, the gas holes 14 are to be designed in such a way that they cannot be freely blown into the interior 17 of the burner 1. These gas holes 14 open into a gas injector channel 12b, 13b, which extends as far as the inlet slot 2b, 3b. It is advantageous if this channel is divided several times in the longitudinal direction by flow plates that cannot be seen, so that the gaseous fuel 4 is channeled in the direction of the combustion air flow under design conditions, for example full load. Furthermore, aid is provided that the gaseous fuel 4 blows at the respective speed of the air 7 brought in in the area of the inlet slots 2b, 3b. This prevents the air 7 and the medium-calorific gas 4 used can already be mixed thoroughly in the inlet area into the interior 17 of the burner 1, because this would inevitably lead to premature ignition, which entails diffusion-like combustion with greatly increased NO x emissions. In order to achieve these desired goals, the transition from the gas holes 14 to the subsequent gas injector channels 12b, 13b is preferably designed as a Borda-Carnot extension. As far as the minimum length of the gas injector channel is concerned, the usual rule of 3-5 hydraulic diameters resp. 6 - 10 gap width used. With such a design, there is a guarantee that the calmed gas flow 4 can "breathy" mix with the air flow 7, which also avoids the acoustic hardness during the mixing process.

Claims (6)

  1. Burner, essentially consisting of at least two partial-conical bodies positioned one upon the other and having a conical shape opening in the flow direction, the centrelines of these partial-conical bodies extending offset relative to one another in the longitudinal direction in such a way that tangential inlet slots to the internal space of the burner form over the length of the burner, of a nozzle for introducing liquid fuel, of a fuel line for injecting gaseous fuel in the region of the tangential inlet slots and of a duct for combustion air to enter, characterized in that in the duct (23, 24) is located an injector (12, 13) for an additional gaseous fuel (4), which flows out of the injector (12, 13) in the region of the tangential inlet clot (2b, 3b) and can there be mixed with the airflow (7) flowing through the duct (23, 24).
  2. Burner Claim 1, characterized in that the injector (12, 13) consists of a supply duct (12a, 13a) for the fuel (4) extending in the flow direction of the burner (1), characterized in that the supply duct (12a, 13a) has a number of holes (14) in the flow direction of the fuel (4), and in that the holes (14) enter an injector duct (12b, 13b) extending in the region of the inlet slot (2b, 3b).
  3. Burner according to Claim 2, characterized in that the transition from the holes (14) to the subsequent injector duct (12b, 13b) is formed by a Borda-Carnot expansion.
  4. Burner according to Claim 2, characterized in that the number (PGB) of holes (14) per unit area is proportional to the radially averaged inlet velocity of the air (7) in the region of the inlet slot (2b, 3b) of the burner (1), in accordance with the following equation:
    Figure imgb0003
     where Á is the included angle of the conical burner (1), S signifies the inlet velocity and R is the average radius of the particular position considered of the inlet slot (2b, 3b).
  5. Burner according to Claim 2, characterized in that flow aids for the fuel (4) for matching to the flow direction of the airflow (7) and the combustion air (8) are available in the injector duct (12b, 13b).
  6. Method of operating a burner according to Claim 1, characterized in that the inlet velocity of the gaseous fuel (4) into the internal space (17) of the burner (1) is equal to or smaller than the velocity of the airflow (7) flowing from the duct (23, 24).
EP90123495A 1989-12-22 1990-12-07 Burner Expired - Lifetime EP0433790B1 (en)

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CH4602/89 1989-12-22

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Cited By (11)

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WO1993017279A1 (en) * 1992-02-26 1993-09-02 United Technologies Corporation Premix gas nozzle
EP0641971A2 (en) * 1993-09-06 1995-03-08 Abb Research Ltd. Method for operating a premix burner
EP0683219A2 (en) * 1994-05-19 1995-11-22 Abb Research Ltd. Process for air blast gasification of carbonaceous fuels
US5588826A (en) * 1994-10-01 1996-12-31 Abb Management Ag Burner
US5645410A (en) * 1994-11-19 1997-07-08 Asea Brown Boveri Ag Combustion chamber with multi-stage combustion
US5588824A (en) * 1994-12-19 1996-12-31 Abb Management Ag Injection nozzle
US5674066A (en) * 1995-01-30 1997-10-07 Asea Brown Boveri Ag Burner
US6390805B1 (en) 1998-09-16 2002-05-21 Asea Brown Boveri Ag Method of preventing flow instabilities in a burner
EP1262714A1 (en) 2001-06-01 2002-12-04 ALSTOM (Switzerland) Ltd Burner with exhausts recirculation
US6672863B2 (en) 2001-06-01 2004-01-06 Alstom Technology Ltd Burner with exhaust gas recirculation
US8801429B2 (en) 2006-03-30 2014-08-12 Alstom Technology Ltd Burner arrangement

Also Published As

Publication number Publication date
ATE119650T1 (en) 1995-03-15
DE59008639D1 (en) 1995-04-13
PL288225A1 (en) 1991-12-16
CH680467A5 (en) 1992-08-31
JPH04136606A (en) 1992-05-11
EP0433790A1 (en) 1991-06-26
RU2011117C1 (en) 1994-04-15
JP3011775B2 (en) 2000-02-21
US5169302A (en) 1992-12-08
CA2032562A1 (en) 1991-06-23

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