EP0321809B1 - Process for combustion of liquid fuel in a burner - Google Patents

Process for combustion of liquid fuel in a burner Download PDF

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Publication number
EP0321809B1
EP0321809B1 EP88120667A EP88120667A EP0321809B1 EP 0321809 B1 EP0321809 B1 EP 0321809B1 EP 88120667 A EP88120667 A EP 88120667A EP 88120667 A EP88120667 A EP 88120667A EP 0321809 B1 EP0321809 B1 EP 0321809B1
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EP
European Patent Office
Prior art keywords
burner
fuel
liquid fuel
interior
cone
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
EP88120667A
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German (de)
French (fr)
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EP0321809A1 (en
Inventor
Jakob Dr. Keller
Thomas Dr. Sattelmayer
Daniel Styner
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General Electric Switzerland GmbH
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BBC Brown Boveri AG Switzerland
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Publication date
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Priority to AT88120667T priority Critical patent/ATE63628T1/en
Publication of EP0321809A1 publication Critical patent/EP0321809A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C1/00—Combustion apparatus specially adapted for combustion of two or more kinds of fuel simultaneously or alternately, at least one kind of fuel being either a fluid fuel or a solid fuel suspended in a carrier gas or air
    • 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
    • F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
    • F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
    • F23R3/02—Continuous combustion chambers using liquid or gaseous fuel characterised by the air-flow or gas-flow configuration
    • F23R3/04—Air inlet arrangements
    • F23R3/10—Air inlet arrangements for primary air
    • F23R3/12—Air inlet arrangements for primary air inducing a vortex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/07002—Premix burners with air inlet slots obtained between offset curved wall surfaces, e.g. double cone burners

Definitions

  • the present invention relates to a method for the combustion of liquid fuel in a burner without a premix section according to the preamble of claim 1. It also relates to a burner for carrying out this method.
  • a burner is known from EP-A1-0 210 462, which is formed from at least two double-curved hollow partial cone bodies acted upon with tangential air entry. These bodies are folded in the direction of flow along diagonals that open outwards in the shape of a cone. One curved fold side forms an inner cone with an increasing cone inclination in the outflow direction, while the other curved fold side forms an outer cone with a decreasing cone inclination in the outflow direction. At their ends, the inner cones each carry a fuel line along their entire axial extent for the supply of the gaseous fuel which flows through several fuel nozzles into the interior of the burner in order to mix there with the tangentially flowing combustion air.
  • the burner also has a separate supply of a liquid fuel, which is a dual burner.
  • the injection of the liquid fuel is directed axially onto the outer cone in such a way that, depending on the strength of the injection, a different length of fuel film is formed.
  • weighty mixing is carried out by the tangentially introduced combustion air, which rolls up the fuel film in layers due to its swirling movement in the axial direction, making the generation of a strong mixture superfluous. Because the impulse of the injection of liquid fuel is adapted to the load of the machine, the mixture is never too lean or too rich.
  • this burner results in a vortex flow which is low in swirl in the center but has an excess of axial speed. Because the number of swirls increases strongly in the axial direction and reaches the breakdown value or the critical value at the end of the burner, this results in a positionally stable vortex backflow.
  • the oil injection is structurally relatively complex. But the design of the folded cone sections and their coordination with each other is not easy to handle.
  • the object of the invention is to simplify the physical configuration of the burner in a method and a burner of the types mentioned at the beginning and at the same time to minimize the NO x emission values from the premixed combustion of liquid fuel, without changing the flow field in the burner with the stable vortex backflow zone.
  • Another advantage of the invention results from the possibility that the burner according to the invention can also be used in gas turbines, the pressure ratio of which is so high over approximately 12 that, due to the principle, no pre-evaporation of the liquid fuel is possible because the fuel has previously ignited would. Finally, the burner according to the invention can also be used in those cases in which no or only insufficient air preheating for evaporation can be achieved.
  • an essential advantage of the invention is that the burner according to the invention consists of a few components that are easy to manufacture and assemble.
  • FIGS. 2-4 In order to better understand the structure of the burner, it is advantageous if the reader uses the individual sections according to FIGS. 2-4 simultaneously with FIG. 1. Furthermore, in order not to make Fig. 1 unnecessarily confusing, the baffles 21a, 21b shown schematically according to Figs. 2-4 have only been hinted at. In the description of FIG. 1 below, the remaining FIGS. 2-4 are optionally referred to as required.
  • the burner according to FIG. 1 consists of two half hollow tapered bodies 1, 2 which are offset from one another.
  • the offset of the respective central axis 1b, 2b of the partial cone bodies 1, 2 to each other creates a tangential air inlet slot 19, 20 on both sides in a mirror-image arrangement (FIGS. 2-4), through which the combustion air 15 enters the interior of the burner, ie flows into the cone cavity 14.
  • the two partial cone bodies 1, 2 each have a cylindrical initial part 1 a, 2 a, which likewise run offset from one another analogously to the partial cone bodies 1, 2, so that the tangential air inlet slots 19, 20 are present from the beginning.
  • a nozzle 3 is accommodated, the fuel injection 4 of which coincides with the narrowest cross section of the conical cavity 14 formed by the two partial cone bodies 1, 2.
  • the burner can be made purely conical, that is to say without cylindrical initial parts 1a, 2a.
  • Both partial cone bodies 1, 2 each have a fuel line 8, 9, which are provided with openings 17 through which the gaseous fuel 13 is mixed with the combustion air 15 flowing through the tangential air inlet slots 19, 20. The position of these fuel lines 8, 9 is shown schematically in FIGS.
  • the fuel lines 8, 9 are attached to the end of the tangential air inlet slots 19, 20, so that the admixture 16 of the gaseous fuel 13 with the incoming combustion air 15 also takes place there .
  • the burner On the combustion chamber side 22, the burner has a collar-shaped anchoring for the partial cone body 1, 2 serving end plate 10 with a number of holes 11 through which, if necessary, dilution air or cooling air 18 can be supplied to the front part of the combustion chamber 22 or its wall.
  • the liquid fuel 12 flowing through the nozzle 3 is injected into the cone cavity 14 at an acute angle, in such a way that the most homogeneous conical fuel spray is obtained in the burner outlet plane, it being very important to ensure that the inner walls of the partial cone bodies 1, 2 injected liquid fuel 12 are not wetted.
  • the fuel injector 4 can be an air-assisted nozzle or a pressure atomizer.
  • the conical liquid fuel profile 5 is enclosed by a rotating combustion air stream 15 flowing in tangentially. In the axial direction, the concentration of the liquid fuel 12 is continuously reduced by the mixed-in combustion air 15. If gaseous fuel 13/16 is burned, the mixture is formed with the combustion air 15 directly at the end of the air inlet slots 19, 20.
  • the nitrogen oxide and carbon monoxide emissions are low if the excess air is at least 60%. In the case of complete evaporation before entering the combustion zone, the pollutant emission values are lowest. The same also applies to near-stoichiometric operation when the excess air is replaced by recirculating exhaust gas.
  • the partial cone bodies 1, 2 with regard to the taper inclination and the width of the tangential air inlet slots 19, 20, narrow limits must be observed so that the desired flow field of the air with its return flow zone 6 is established in the area of the burner mouth for flame stabilization.
  • the backflow zone 6 which is once geometrically fixed, is inherently position-stable, because the swirl number increases in the direction of flow in the region of the cone shape of the burner.
  • the design of the burner is particularly suitable, given the given overall length of the burner, of changing the size of the tangential air inlet slots 19, 20 by fixing the partial cone bodies 1, 2 to the end plate 10 by means of a releasable connection.
  • the distance between the two central axes 1b, 2b decreases or increases as a result of radial displacement of the two partial cone bodies 1, 2 to and from one another, and the gap size of the tangential air inlet slots 19, 20 changes accordingly, as can be seen particularly well from FIGS. 2-4 emerges.
  • the partial cone bodies 1, 2 can also be displaced relative to one another in another plane, as a result of which even an overlap thereof can be controlled. Yes, it is even possible to spirally move the partial cone bodies 1, 2 with one another by means of a counter-rotating movement. It is therefore in your hand to vary the shape and size of the tangential air inlets 19, 20 as desired, so that the burner can be used universally without changing its overall length.
  • 2-4 also shows the position of the guide plates 21a, 21b. They have flow introduction functions, whereby they, of different lengths, extend the respective end of the partial cone bodies 1 and 2 in the direction of flow of the combustion air 15.
  • the channeling of the combustion air into the cone cavity 14 can be optimized by opening or closing the guide plates 21a, 21b around the pivot point 23, in particular this is necessary if the original gap size of the tangential air inlet slots 19, 20 is changed.

Abstract

In the premix combustion of liquid fuel in a burner without premixing section, there is formed in the interior (14) of the burner a conical liquid fuel column (5) which widens in the direction of flow and which is surrounded by a rotating combustion air flow (15) which flows tangentially into the burner. Ignition of the mixture takes place at the outlet of the burner, a backflow zone (6) being formed in the region of the burner mouth. The burner itself consists of at least two hollow part cone members (1, 2) positioned on one another, which have a cone inclination which increases in the direction of flow. The part cone members (1, 2) are staggered in relation to one another, as a result of which tangential air inlet slots (19, 20) are formed. A nozzle (3) placed on the burner head ensures the injection of the liquid fuel (12) into the interior (14) of the burner. <IMAGE>

Description

Die vorliegende Erfindung betrifft ein Verfahren für die Verbrennung von flüssigem Brennstoff in einem Brenner ohne Vormischstrecke gemäss Oberbegriff des Anspruchs 1. Sie betrifft auch ein Brenner zur Durchführung dieses Verfahrens.The present invention relates to a method for the combustion of liquid fuel in a burner without a premix section according to the preamble of claim 1. It also relates to a burner for carrying out this method.

STAND DER TECHNIKSTATE OF THE ART

Aus EP-A1-0 210 462 ist ein Brenner bekannt geworden, welcher aus mindestens zwei mit tangentialem Lufteintritt beaufschlagten doppelgekrümmten hohlen Teilkegelkörpern gebildet ist. Diese Körper sind in Strömungsrichtung entlang von kegelstrahlig nach aussen hin sich öffnenden Diagonalen gefalzt. Dabei bildet die eine gekrümmte Falzseite einen Innenkegel mit in Abströmungsrichtung zunehmender Kegelneigung, während die andere gekrümmte Falzseite einen Aussenkegel bildet, mit in Abströmungsrichtung abnehmender Kegelneigung. Die Innenkegel tragen endseitig, auf ihrer ganzen axialen Ausdehnung, je eine Brennstoffleitung für die Zuführung des gasförmigen Brennstoffes, der durch mehrere Brennstoffdüsen in den Innenraum des Brenners strömt, um sich dort mit der tangential einströmenden Verbrennungsluft zu vermischen. Der Brenner weist des weiteren eine separate Zuführung eines flüssigen Brennstoffes auf, womit man hier mit einem Dualbrenner zu tun. Die Eindüsung des flüssigen Brennstoffes ist axial auf die Aussenkegel gerichtet, dergestalt, dass sich dort, je nach Stärke der Eindüsung, einen verschieden langen Brennstoffilm bildet. Nebst der natürlichen Verdampfung des flüssigen Brennstoffes durch die dort herrschende Strahlungswärme, wird eine gewichtige Vermischung durch die tangential herangeführte Verbrennungsluft übernommen, welche durch ihre Drallbewegung in axialer Richtung den Brennstoffilm schichtenweise aufrollt, wodurch die Erzeugung einer starken Vermischung überflüssig wird. Dadurch, dass der Impuls der Eindüsung von flüssigem Brennstoff der Last der Maschine angepasst wird, ist das Gemisch nie zu mager oder zu fett.A burner is known from EP-A1-0 210 462, which is formed from at least two double-curved hollow partial cone bodies acted upon with tangential air entry. These bodies are folded in the direction of flow along diagonals that open outwards in the shape of a cone. One curved fold side forms an inner cone with an increasing cone inclination in the outflow direction, while the other curved fold side forms an outer cone with a decreasing cone inclination in the outflow direction. At their ends, the inner cones each carry a fuel line along their entire axial extent for the supply of the gaseous fuel which flows through several fuel nozzles into the interior of the burner in order to mix there with the tangentially flowing combustion air. The burner also has a separate supply of a liquid fuel, which is a dual burner. The injection of the liquid fuel is directed axially onto the outer cone in such a way that, depending on the strength of the injection, a different length of fuel film is formed. In addition to the natural evaporation of the liquid fuel due to the radiant heat prevailing there, weighty mixing is carried out by the tangentially introduced combustion air, which rolls up the fuel film in layers due to its swirling movement in the axial direction, making the generation of a strong mixture superfluous. Because the impulse of the injection of liquid fuel is adapted to the load of the machine, the mixture is never too lean or too rich.

Zwei Ziele lassen sich damit unmittelbar erreichen:

  • Die Vorzüge eines Vormischbrenners, nämlich wenig NOx und CO, stellen sich ein.
  • Eine gute Flammenstabilität in einem weiteren Betriebsbereich ist gewährleistet.
Two goals can be achieved immediately:
  • The advantages of a premix burner, namely little NO x and CO, come about.
  • Good flame stability is guaranteed in another operating area.

Des weiteren ergibt sich aus der konstruktiven Gestaltung dieses Brenners eine Wirbelströmung, welche im Zentrum drallarm ist, aber einen Axialgeschwindigkeitsüberschuss aufweist. Weil nun die Drallzahl in axialer Richtung stark zunimmt und am Ende des Brenners den Breakdown-Wert bzw. den kritischen Wert erreicht, ergibt dies eine positionsstabile Wirbelrückströmung.Furthermore, the structural design of this burner results in a vortex flow which is low in swirl in the center but has an excess of axial speed. Because the number of swirls increases strongly in the axial direction and reaches the breakdown value or the critical value at the end of the burner, this results in a positionally stable vortex backflow.

Obwohl die Vorteile des hier gewürdigten Brenners nicht wegzuleugnen sind, hat es sich doch gezeigt, dass die NOx- und CO-Emissionswerte, obwohl sie durch seinen Einsatz bereits tiefer liegen gegenüber den gesetzlichen Grenzwerten, zukünftig substantiell vermindert werden müssen. Des weiteren hat es sich auch gezeigt, dass Verkokungsprobleme des Aussenkegels aus der Oelverbrennung nicht auszuschliessen sind, und die Brennstoffeindüsung nicht einfach zu handhaben ist.Although the advantages of the burner recognized here cannot be denied, it has been shown that the NO x and CO emission values, although their use is already lower than the legal limit values, will have to be substantially reduced in the future. Furthermore it has It has also been shown that coking problems of the outer cone cannot be ruled out from the oil combustion and that the fuel injection is not easy to handle.

Des weiteren ist die Oeleindüsung konstruktiv relativ aufwendig gelöst. Aber auch die Gestaltung der gefalzten Kegelabschnitte und deren Abstimmung zueinander ist nicht einfach zu handhaben.Furthermore, the oil injection is structurally relatively complex. But the design of the folded cone sections and their coordination with each other is not easy to handle.

AUFGABE DER ERFINDUNGOBJECT OF THE INVENTION

Hier greift die Erfindung ein. Der Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, liegt die Aufgabe zugrunde, bei einem Verfahren sowie einem Brenner der eingangs genannten Arten die körperliche Ausgestaltung des Brenners zu vereinfachen und gleichzeitig die NOx-Emissionswerte aus der vormischartigen Verbrennung von flüssigem Brennstoff zu minimieren, ohne das Strömungsfeld im Brenner mit der stabilen Wirbelrückströmzone zu verändern.This is where the invention intervenes. The object of the invention, as characterized in the claims, is to simplify the physical configuration of the burner in a method and a burner of the types mentioned at the beginning and at the same time to minimize the NO x emission values from the premixed combustion of liquid fuel, without changing the flow field in the burner with the stable vortex backflow zone.

Die wesentlichen Vorteile der Erfindung hinsichtlich der Ausgestaltung sind darin zu sehen, dass im Fehlen der sonst üblichen Vormischzone keine Gefahr eines Rückzündens in den Brenner zu befürchten ist. Des weiteren entfallen die wohlbekannten Probleme bei der Einsetzung von Drallerzeugern im Gemischstrom, beispielsweise jene Unzulänglichkeiten, die durch Abbrennen von Belägen mit Zerstörung der Drallschaufeln entstehen.The essential advantages of the invention with regard to the configuration are to be seen in the fact that, in the absence of the otherwise usual premixing zone, there is no fear of reignition in the burner. Furthermore, the well-known problems in the use of swirl generators in the mixture flow, for example those inadequacies which arise from the burning off of deposits with destruction of the swirl vanes, are eliminated.

Der wesentliche Vorteil der Erfindung hinsichtlich der NOx-Emissionswerte ist darin zu sehen, dass diese schlagartig auf einen Bruchteil dessen sinken, was man bis heute als maximal erreichbar betrachtet hat. Die Verbesserung weist also nicht bloss ein paar Prozentpunkte auf, sondern man bewegt sich nun in der Grössenordnung von verschwindend kleinen 10 - 15 % der gesetzlichen Grenzwerte, womit eine ganz neue Qualitätsstufe erreicht ist.The main advantage of the invention with regard to the NO x emission values can be seen in the fact that these suddenly drop to a fraction of what has hitherto been considered to be attainable to the maximum. So the improvement is not just a few percentage points, but you are now in the order of a tiny 10 - 15% of the legal limit values, which has reached a whole new level of quality.

Ein weiterer Vorteil der Erfindung ergibt sich aus der Möglichkeit heraus, dass der erfindungsgemässe Brenner auch in Gasturbinen eingesetzt werden kann, deren Druckverhältnis _ über etwa 12 _ so hoch ist, dass prinzipbedingt keine Vorverdampfung des Flüssigbrennstoffes mehr möglich ist, weil zuvor Selbstzündung des Brennstoffes einsetzen würde. Schliesslich ist der erfindungsgemässe Brenner auch noch in solchen Fällen einsetzbar, in denen keine oder nur eine für die Verdampfung unzureichende Luftvorerwärmung erreicht werden kann.Another advantage of the invention results from the possibility that the burner according to the invention can also be used in gas turbines, the pressure ratio of which is so high over approximately 12 that, due to the principle, no pre-evaporation of the liquid fuel is possible because the fuel has previously ignited would. Finally, the burner according to the invention can also be used in those cases in which no or only insufficient air preheating for evaporation can be achieved.

Nicht zuletzt ist ein wesentlicher Vorteil der Erfindung auch darin zu sehen, dass der erfindungsgemässe Brenner aus wenigen Bestandteilen besteht, die einfach herzustellen und zu montieren sind.Last but not least, an essential advantage of the invention is that the burner according to the invention consists of a few components that are easy to manufacture and assemble.

Vorteilhafte und zweckmässige Weiterbildungen der erfindungsgemässen Aufgabenlösung sind in den abhängigen Ansprüchen gekennzeichnet.Advantageous and expedient developments of the task solution according to the invention are characterized in the dependent claims.

Im folgenden wird anhand der Zeichnung ein Ausführungsbeispiel der Erfindung erläutert. Alle für das unmittelbare Verständnis der Erfindung nicht erforderlichen Elemente sind fortgelassen. Die Strömungsrichtungen der verschiedenen Medien sind mit Pfeilen angegeben. In den verschiedenen Figuren sind jeweils gleiche Elemente mit den gleichen Bezugszeichen versehen.In the following an embodiment of the invention will be explained with reference to the drawing. All elements not necessary for the immediate understanding of the invention have been omitted. The flow directions of the different media are indicated by arrows. In the various figures, the same elements are provided with the same reference symbols.

KURZE BESCHREIBUNG DER ERFINDUNGBRIEF DESCRIPTION OF THE INVENTION

Es zeigt:

  • Fig. 1 einen Brenner in perspektivischer Darstellung, entsprechend aufgeschnitten und
  • Fig. 2, 3, 4 entsprechende Schnitte durch die Ebenen II-II (Fig. 2), III-III (Fig. 3) und IV-IV (Fig. 4), wobei diese Schnitte nur eine schematische, vereinfachte Darstellung des Brenners sind.
It shows:
  • Fig. 1 a burner in a perspective view, cut accordingly and
  • Fig. 2, 3, 4 corresponding sections through the planes II-II (Fig. 2), III-III (Fig. 3) and IV-IV (Fig. 4), these sections only a schematic, simplified representation of the burner are.

BESCHREIBUNG DER AUSFÜHRUNGSBEISPIELEDESCRIPTION OF THE EMBODIMENTS

Um den Aufbau des Brenners besser zu verstehen, ist es von Vorteil, wenn der Leser gleichzeitig zu Fig. 1 die einzelnen Schnitte nach Fig. 2-4 heranzieht. Des weiteren, um Fig. 1 nicht unnötig unübersichtlich zu gestalten, sind in ihr die nach Fig. 2-4 schematisch gezeigten Leitbleche 21a, 21b nur andeutungsweise aufgenommen worden. Im folgenden werden auch bei der Beschreibung von Fig. 1 wahlweise, nach Bedarf, auf die restlichen Fig. 2-4 hingewiesen.In order to better understand the structure of the burner, it is advantageous if the reader uses the individual sections according to FIGS. 2-4 simultaneously with FIG. 1. Furthermore, in order not to make Fig. 1 unnecessarily confusing, the baffles 21a, 21b shown schematically according to Figs. 2-4 have only been hinted at. In the description of FIG. 1 below, the remaining FIGS. 2-4 are optionally referred to as required.

Der Brenner gemäss Fig. 1 besteht aus zwei halben hohlen Teikegelkörpern 1, 2, die versetzt zueinander aufeinander liegen. Die Versetzung der jeweiligen Mittelachse 1b, 2b der Teilkegelkörper 1, 2 zueinander schafft auf beiden Seiten in spiegelbildlicher Anordnung jeweils einen tangentialen Lufteintrittsschlitz 19, 20 frei, (Fig. 2-4), durch welche die Verbrennungsluft 15 in den Innenraum des Brenners, d.h. in den Kegelhohlraum 14 strömt. Die beiden Teilkegelkörper 1, 2 haben je einen zylindrischen Anfangsteil 1a, 2a, die ebenfalls analog den Teilkegelkörpern 1, 2 versetzt zueinander verlaufen, so dass die tangentialen Lufteintrittsschlitze 19, 20 vom Anfang an vorhanden sind. In diesem zylindrischen Anfangsteil 1a, 2a ist eine Düse 3 untergebracht, deren Brennstoffeindüsung 4 mit dem engsten Querschnitt des durch die zwei Teilkegelkörper 1, 2 gebildeten kegeligen Hohlraumes 14 zusammenfällt. Sebstverständlich kann der Brenner rein kegelig, also ohne zylindrische Anfangsteile 1a, 2a, ausgeführt sein. Beide Teilkegelkörper 1, 2 weisen je eine Brennstoffleitung 8, 9 auf, die mit Oeffnungen 17 versehen sind, durch welche der gasförmige Brennstoff 13, der durch die tangentialen Lufteintrittsschlitze 19, 20 strömenden Verbrennungsluft 15 zugemischt wird. Die Lage dieser Brennstoffleitungen 8, 9 geht schematisch aus Fig. 2-4 hervor: Die Brennstoffleitungen 8, 9 sind am Ende der tangentialen Lufteintrittsschlitze 19, 20 angebracht, so dass dort auch die Zumischung 16 des gasförmigen Brennstoffes 13 mit der einströmenden Verbrennungsluft 15 stattfindet. Brennraumseitig 22 weist der Brenner eine kragenförmige als Verankerung für die Teilkegelkörper 1, 2 dienende Abschlussplatte 10 mit einer Anzahl Bohrungen 11 auf, durch welche nötigenfalls Verdünnungsluft bzw. Kühlluft 18 dem vorderen Teil des Brennraumes 22 bzw. dessen Wand zugeführt werden kann. Der durch die Düse 3 strömende flüssige Brennstoff 12 wird in einem spitzen Winkel in den Kegelhohlraum 14 eingedüst, dergestalt, dass sich in der Brenneraustrittsebene ein möglichst homogener kegeliger Brennstoffspray einstellt, wobei streng darauf zu achten ist, dass die Innenwände der Teilkegelkörper 1, 2 vom eingedüsten flüssigen Brennstoff 12 nicht benetzt werden. Bei der Brennstoffeindüsung 4 kann es sich um eine luftunterstützte Düse oder um einen Druckzerstäuber handeln. Das kegelige Flüssigbrennstoffprofil 5 wird von einem tangential einströmenden rotierenden Verbrennungsluftstrom 15 umschlossen. In axialer Richtung wird die Konzentration des Flüssigbrennstoffes 12 fortlaufend durch die eingemischte Verbrennungsluft 15 abgebaut. Wird gasförmiger Brennstoff 13/16 verbrannt, geschieht die Gemischbildung mit der Verbrennungsluft 15 direkt am Ende der Lufteintrittsschlitze 19, 20. Bei der Eindüsung von flüssigem Brennstoff 12 wird im Bereich des Wirbelaufplatzens, also im Bereich der Rückströmzone 6, die optimale, homogene Brennstoffkonzentration über den Querschnitt erreicht. Die Zündung erfolgt an der Spitze der Rückströmzone 6. Erst an dieser Stelle kann eine stabile Flammenfront 7 entstehen. Ein Rückschlag der Flamme ins Innere des Brenners, wie dies bei Vormischstrecken latent der Fall ist, wogegen dort mit komplizierten Flammenhaltern Abhilfe gesucht wird, ist hier nicht zu befürchten. Ist die Verbrennungsluft 15 vorgeheizt, so stellt sich eine natürliche Verdampfung des flüssigen Brennstoffes 12 ein, bevor der Punkt am Ausgang des Brenners erreicht ist, an dem die Zündung des Gemisches stattfinden kann. Der Grad der Verdampfung ist selbstverständlich von der Grösse des Brenners, der Tropfengrössenverteilung und der Temperatur der Verbrennungsluft 15 abhängig. Unabhängig aber davon, ob neben der homogenen Tropfenvormischung durch Verbrennungsluft 15 niedriger Temperatur oder zusätzlich nur eine partielle oder die vollständige Tropfenverdampfung durch vorgeheizte Verbrennungsluft 15 erreicht wird, fallen die Stickoxid- und Kohlenmonoxidemissionen niedrig aus, wenn der Luftüberschuss mindestens 60 % beträgt. Im Falle der vollständigen Verdampfung vor dem Eintritt in die Verbrennungszone sind die Schadstoffemissionswerte am niedrigsten. Gleiches gilt auch für den nahstöchiometrischen Betrieb, wenn die Ueberschussluft durch rezirkulierendes Abgas ersetzt wird. Bei der Gestaltung der Teilkegelkörper 1, 2 hinsichtlich Kegelneigung und der Breite der tangentialen Lufteintrittsschlitze 19, 20 sind enge Grenzen einzuhalten, damit sich das gewünschte Strömungsfeld der Luft mit ihrer Rückströmzone 6 im Bereich der Brennermündung zur Flammenstabilisierung einstellt. Allgemein ist zu sagen, dass eine Verkleinerung der Lufteintrittsschlitze 19, 20 die Rückströmzone 6 weiter stromaufwärts verschiebt, wodurch dann allerdings das Gemisch früher zur Zündung käme. Immerhin ist hier zu sagen, dass die einmal geometrisch fixierte Rückströmzone 6 an sich positionsstabil ist, denn die Drallzahl nimmt in Strömungsrichtung im Bereich der Kegelform des Brenners zu. Die Konstruktion des Brenners eignet sich vorzüglich, bei vorgegebener Baulänge des Brenners, die Grösse der tangentialen Lufteintrittsschllitze 19, 20 zu verändern, indem die Teilkegelkörper 1, 2 anhand einer lösbaren Verbindung mit der Abschlussplatte 10 fixiert sind. Durch radiale Verschiebung der beiden Teilkegelkörper 1, 2 zu- oder auseinander verkleinert bzw. vergrössert sich der Abstand der beiden Mittelachsen 1b, 2b, und dementsprechend verändert sich die Spaltgrösse der tangentialen Lufteintrittsschlitze 19, 20, wie dies aus Fig. 2-4 besonders gut hervorgeht. Selbstverständlich sind die Teilkegelkörper 1, 2 auch in einer anderen Ebene zueinander verschiebbar, wodurch sogar eine Ueberlappung derselben angesteuert werden kann. Ja, es ist sogar möglich, die Teilkegelkörper 1, 2 durch eine gegenläufige drehende Bewegung spiralartig eineinander zu verschieben. Somit hat man es in der Hand, die Form und die Grösse der tangentialen Lufteintritte 19, 20 beliebig zu variieren, womit der Brenner ohne Veränderung seiner Baulänge universell einsetzbar ist.The burner according to FIG. 1 consists of two half hollow tapered bodies 1, 2 which are offset from one another. The offset of the respective central axis 1b, 2b of the partial cone bodies 1, 2 to each other creates a tangential air inlet slot 19, 20 on both sides in a mirror-image arrangement (FIGS. 2-4), through which the combustion air 15 enters the interior of the burner, ie flows into the cone cavity 14. The two partial cone bodies 1, 2 each have a cylindrical initial part 1 a, 2 a, which likewise run offset from one another analogously to the partial cone bodies 1, 2, so that the tangential air inlet slots 19, 20 are present from the beginning. In this cylindrical initial part 1a, 2a, a nozzle 3 is accommodated, the fuel injection 4 of which coincides with the narrowest cross section of the conical cavity 14 formed by the two partial cone bodies 1, 2. Of course, the burner can be made purely conical, that is to say without cylindrical initial parts 1a, 2a. Both partial cone bodies 1, 2 each have a fuel line 8, 9, which are provided with openings 17 through which the gaseous fuel 13 is mixed with the combustion air 15 flowing through the tangential air inlet slots 19, 20. The position of these fuel lines 8, 9 is shown schematically in FIGS. 2-4: The fuel lines 8, 9 are attached to the end of the tangential air inlet slots 19, 20, so that the admixture 16 of the gaseous fuel 13 with the incoming combustion air 15 also takes place there . On the combustion chamber side 22, the burner has a collar-shaped anchoring for the partial cone body 1, 2 serving end plate 10 with a number of holes 11 through which, if necessary, dilution air or cooling air 18 can be supplied to the front part of the combustion chamber 22 or its wall. The liquid fuel 12 flowing through the nozzle 3 is injected into the cone cavity 14 at an acute angle, in such a way that the most homogeneous conical fuel spray is obtained in the burner outlet plane, it being very important to ensure that the inner walls of the partial cone bodies 1, 2 injected liquid fuel 12 are not wetted. The fuel injector 4 can be an air-assisted nozzle or a pressure atomizer. The conical liquid fuel profile 5 is enclosed by a rotating combustion air stream 15 flowing in tangentially. In the axial direction, the concentration of the liquid fuel 12 is continuously reduced by the mixed-in combustion air 15. If gaseous fuel 13/16 is burned, the mixture is formed with the combustion air 15 directly at the end of the air inlet slots 19, 20. When liquid fuel 12 is injected, the optimal, homogeneous fuel concentration is in the area of the vortex bursting, ie in the area of the backflow zone 6 reached the cross section. The ignition takes place at the top of the return flow zone 6. Only at this point can a stable flame front 7 arise. A flashback of the flame into the interior of the burner, as is latently the case with premixing sections, while remedial measures are sought there with complicated flame holders is not to be feared here. If the combustion air 15 is preheated, natural evaporation of the liquid fuel 12 occurs before the point at the burner outlet at which the ignition of the mixture can take place is reached. The degree of evaporation is of course dependent on the size of the burner, the drop size distribution and the temperature of the combustion air 15. Regardless of whether, in addition to the homogeneous drop premixing by combustion air 15 at a low temperature or only a partial one or complete drop evaporation is achieved by preheated combustion air 15, the nitrogen oxide and carbon monoxide emissions are low if the excess air is at least 60%. In the case of complete evaporation before entering the combustion zone, the pollutant emission values are lowest. The same also applies to near-stoichiometric operation when the excess air is replaced by recirculating exhaust gas. When designing the partial cone bodies 1, 2 with regard to the taper inclination and the width of the tangential air inlet slots 19, 20, narrow limits must be observed so that the desired flow field of the air with its return flow zone 6 is established in the area of the burner mouth for flame stabilization. In general, it can be said that a reduction in the size of the air inlet slots 19, 20 shifts the backflow zone 6 further upstream, which would cause the mixture to ignite earlier, however. After all, it must be said here that the backflow zone 6, which is once geometrically fixed, is inherently position-stable, because the swirl number increases in the direction of flow in the region of the cone shape of the burner. The design of the burner is particularly suitable, given the given overall length of the burner, of changing the size of the tangential air inlet slots 19, 20 by fixing the partial cone bodies 1, 2 to the end plate 10 by means of a releasable connection. The distance between the two central axes 1b, 2b decreases or increases as a result of radial displacement of the two partial cone bodies 1, 2 to and from one another, and the gap size of the tangential air inlet slots 19, 20 changes accordingly, as can be seen particularly well from FIGS. 2-4 emerges. Of course, the partial cone bodies 1, 2 can also be displaced relative to one another in another plane, as a result of which even an overlap thereof can be controlled. Yes, it is even possible to spirally move the partial cone bodies 1, 2 with one another by means of a counter-rotating movement. It is therefore in your hand to vary the shape and size of the tangential air inlets 19, 20 as desired, so that the burner can be used universally without changing its overall length.

Aus Fig. 2-4 geht auch die Lage der Leitbleche 21a, 21b hervor. Sie haben Strömungseinleitungsfunktionen, wobei sie, verschieden lang, das jeweilige Ende der Teilkegelkörper 1 und 2 in Anströmungsrichtung der Verbrennungsluft 15 verlängern. Die Kanalisierung der Verbrennungsluft in den Kegelhohlraum 14 kann durch Oeffnung bzw. Schliessung der Leitbleche 21a, 21b um den Drehpunkt 23 optimiert werden, insbesondere ist dies dann vonnöten, wenn die ursprüngliche Spaltgrösse der tangentialen Lufteintrittsschlitze 19, 20 verändert wird.2-4 also shows the position of the guide plates 21a, 21b. They have flow introduction functions, whereby they, of different lengths, extend the respective end of the partial cone bodies 1 and 2 in the direction of flow of the combustion air 15. The channeling of the combustion air into the cone cavity 14 can be optimized by opening or closing the guide plates 21a, 21b around the pivot point 23, in particular this is necessary if the original gap size of the tangential air inlet slots 19, 20 is changed.

Claims (8)

1. Process for combustion of liquid fuel in a burner without a premixing section, wherein, in the interior (14) of the burner, a conical column (5) of liquid fuel, which widens in the direction of flow and does not wet the walls of the interior (14) and which is surrounded by a rotating stream (15) of combustion air which flows tangentially into the burner is formed, ignition of the mixture starts at the burner outlet, and the flame is stabilised in the region of the burner outlet by means of a backflow zone (6).
2. Burner for carrying out the process according to Claim 1, consisting of hollow part-cone bodies making up a complete body, having tangential air inlet slots and feed channels for gaseous and liquid fuels, characterised in that the centre axes (1b, 2b) of the hollow part-cone bodies (1, 2) have a cone angle increasing in the direction of flow and run in the longitudinal direction at a mutual offset, in that a fuel nozzle (3), the fuel injection (4) of which is located in the middle of the connecting line of the mutually offset centre axes (1b, 2b) of the part-cone bodies (1, 2), is placed at the burner head in the conical interior (14) formed by the part-cone bodies (1, 2).
3. Process according to Claim 1, characterised in that gaseous fuel (13/16) is fed to the combustion air stream (15) before the latter flows into the interior (14) of the burner.
4. A process according to Claim 1, characterised in that, in near-stoichiometric operation, the excess air in the combustion air stream (15) is replaced by recirculating exhaust gas.
5. Burner according to Claim 2, characterised in that the part-cone bodies (1, 2) are displaceable towards or away from each other.
6. Burner according to Claim 2, characterised in that the fuel injection (4) is an air-assisting nozzle.
7. Burner according to Claim 2, characterised in that the nozzle (3) is a pressure atomiser.
8. Burner according to Claim 2, characterised in that the part-cone bodies (1, 2) are provided with movable baffles (21a, 21b) on the inflow side.
EP88120667A 1987-12-21 1988-12-10 Process for combustion of liquid fuel in a burner Expired - Lifetime EP0321809B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88120667T ATE63628T1 (en) 1987-12-21 1988-12-10 PROCESS FOR COMBUSTION OF LIQUID FUEL IN A BURNER.

Applications Claiming Priority (2)

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CH4980/87 1987-12-21
CH4980/87A CH674561A5 (en) 1987-12-21 1987-12-21

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EP0321809A1 EP0321809A1 (en) 1989-06-28
EP0321809B1 true EP0321809B1 (en) 1991-05-15

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EP (1) EP0321809B1 (en)
JP (1) JP2608320B2 (en)
KR (1) KR0129752B1 (en)
AT (1) ATE63628T1 (en)
CA (1) CA1312816C (en)
CH (1) CH674561A5 (en)
DE (1) DE3862854D1 (en)

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ATE63628T1 (en) 1991-06-15
US4932861A (en) 1990-06-12
KR890010487A (en) 1989-08-09
DE3862854D1 (en) 1991-06-20
JP2608320B2 (en) 1997-05-07
EP0321809A1 (en) 1989-06-28
KR0129752B1 (en) 1998-04-09
CH674561A5 (en) 1990-06-15
JPH01203809A (en) 1989-08-16
CA1312816C (en) 1993-01-19

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