EP0433789A1 - Method for a premix burning of a liquid fuel - Google Patents

Method for a premix burning of a liquid fuel Download PDF

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Publication number
EP0433789A1
EP0433789A1 EP90123494A EP90123494A EP0433789A1 EP 0433789 A1 EP0433789 A1 EP 0433789A1 EP 90123494 A EP90123494 A EP 90123494A EP 90123494 A EP90123494 A EP 90123494A EP 0433789 A1 EP0433789 A1 EP 0433789A1
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EP
European Patent Office
Prior art keywords
burner
fuel
flame
interior
mixture
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP90123494A
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German (de)
French (fr)
Inventor
Jürgen Dr. Haumann
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
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ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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Application filed by ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0433789A1 publication Critical patent/EP0433789A1/en
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    • 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
    • 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 
    • 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 premix combustion according to claim 1. It also relates to a burner for carrying out the method according to claim 1.
  • a burner has become known, in the interior of which a fuel nozzle is placed, from which a conical fuel column that extends in the direction of flow is formed and which extends tangentially into the hollow partial cone body, which is positioned one on top of the other, with a cone opening increasing in the direction of flow and with Rotating combustion air flow flowing into the existing burner, which is offset from one another, is mixed.
  • the ignition of the air / fuel mixture takes place at the outlet of the burner, a "backflow zone" forming in the area of the burner mouth, which prevents the flame from flashing back into the burner from the combustion chamber.
  • Ignition delay time is related to the flame radiation: At high pressure the flame radiation (H2O, CO) will be very strong; a significant part of the radiation is absorbed by the fuel droplets (opaque mist). This mechanism of energy transfer to the liquid fuel leads to a drastic reduction in the ignition delay time.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, is based on the object of preventing the interaction between flame radiation and fuel droplets, which leads to early ignition of the mixture, in a method of the type mentioned.
  • the main advantage of the invention can be seen in the fact that the injection and vaporization of the fuel is shielded from the flame radiation in such a way that the fuel only enters the radiation area of the flame after it has evaporated. Since a vaporized fuel hardly absorbs flame radiation, the danger of the mixture igniting prematurely is averted.
  • FIGS. 1 and 2 are interpreted simultaneously when studying the description. Furthermore, in order not to confuse the individual figures, partial aspects of the burner have been distributed to the individual figures, reference being made to this fact in the description of these figures.
  • the core body of the burner shown in Fig. 1 consists of two half hollow partial cone bodies 1, 2, which are offset from one another.
  • the offset of the respective central axes creates a tangential entry slot 1c, 2c (FIG. 2) on both sides in an axially symmetrical arrangement, through which an air / fuel mixture 6 flows into the interior 3 of the burner, ie into the cone cavity.
  • a tangential entry slot 1c, 2c FIG. 2
  • the conical shape of the partial conical bodies 1, 2 shown in the flow direction has a certain fixed angle.
  • the partial cone bodies 1, 2 can describe an increasing cone inclination (convex shape) or a decreasing cone inclination (concave shape) in the direction of flow.
  • the last two forms are not included in the drawing, since they can easily be traced.
  • the form shown in the drawing is preferably used.
  • the tangential entry slot width is a measure that results from the displacement of the two central axes (1b, 2b from FIG. 2) with respect to one another.
  • the two partial cone bodies 1, 2 each have a cylindrical initial part 1a, 2a, which, similarly to the partial cone bodies 1, 2 mentioned, also run offset from one another, so that the tangential air inlets 1c, 2c (FIG. 2) over the entire length of the BV Brenners are present.
  • the BV burner can be designed to be purely conical, that is to say without a cylindrical initial part.
  • the BV burner has a wall 9 which, for example, forms the inlet front of an annular combustion chamber or a furnace. The air / fuel mixture 6 flowing through the tangential air inlets 1c, 2c (FIG.
  • Fig. 2 is a section through the BV burner along the plane II-II, where there are also two fuel nozzles 4a, 4b.
  • the number and size of the fuel nozzles provided in the flow direction of the BV burner depend on the power to be provided by this BV burner. Accordingly, the fuel 4c, 4d is introduced via an arrangement of fuel nozzles 4a, 4b, which are preferably designed as injector nozzles when using a liquid fuel, in inlet channels 7a, 7b before the actual entry into the interior 3 of the double-cone burner and pre-evaporated there .
  • the speed of the combustion air 5 and the distance of the fuel nozzles from the inlet slots 1d, 2d into the interior 3 of the burner must thus depend on the temperature of the combustion air 5, on the properties of the fuel 4c, 4d and, in the case of liquid fuel, the maximum size of the fuel droplets be matched that the fuel is pre-evaporated in the mixture 6 before reaching the entry slots 1d, 2d, because from this passage point the mixture 6 is in "visual contact" with the flame, ie with the flame front 12.
  • combustion air 5 is an air / exhaust gas mixture: this recirculation of a quantity of a partially cooled exhaust gas, which originally has a temperature of approx. 950 ° C., is also necessary for optimal operation of the double-cone burner when it is used in atmospheric combustion plants is used for near-stoichiometric driving.
  • the optimal mass flow ratio i.e. the ratio between recirculated exhaust gas and fresh air supplied is about 0.7.

Abstract

In premix-type burning of liquid fuel at high pressure, to prevent early ignition of the liquid/gaseous mixture in the burner itself, the injection of the fuel (4c, 4d) and its evaporation with a gaseous medium (5) are carried out at a place where the droplets of the fuel from the fuel nozzles (4a, 4b) are shielded from the flame radiation from the flame front of the burner. As soon as the fuel (4c, 4d) is pre-evaporated, i.e. leaves, as a mixture (6), the duct (7a, 7b) via the inlet slots (1d, 2d) in the direction of the interior (3) of the burner, it hardly absorbs any more flame radiation. …<IMAGE>…

Description

Die vorliegende Erfindung betrifft ein Verfahren für eine Vormischverbrennung nach Anspruch 1. Sie betrifft auch einen Brenner zur Durchführung des Verfahrens nach Anspruch 1.The present invention relates to a method for premix combustion according to claim 1. It also relates to a burner for carrying out the method according to claim 1.

STAND DER TECHNIKSTATE OF THE ART

Aus EP-A1-0321 809 ist ein Brenner bekanntgeworden, in dessen Innenraum eine Brennstoffdüse plaziert ist, aus welcher sich eine in Strömungsrichtung ausbreitende kegelförmige Brennstoffsäule bildet, welche von einem tangential in den aus zwei aufeinander positionierten hohlen Teilkegelkörper mit in Strömungsrichtung zunehmender Kegelöffnung und mit zueinander versetzten Mittelachsen bestehenden Brenner einströmenden rotierenden Verbrennungsluftstrom vermischt wird. Die Zündung des Luft/Brennstoff-Gemisches findet am Ausgang des Brenners statt, wobei sich im Bereich der Brennermündung eine "Rückströmzone" bildet, welche verhindert, dass ein Rückschlag der Flamme vom Brennraum in den Brenner erfolgen kann.From EP-A1-0321 809 a burner has become known, in the interior of which a fuel nozzle is placed, from which a conical fuel column that extends in the direction of flow is formed and which extends tangentially into the hollow partial cone body, which is positioned one on top of the other, with a cone opening increasing in the direction of flow and with Rotating combustion air flow flowing into the existing burner, which is offset from one another, is mixed. The ignition of the air / fuel mixture takes place at the outlet of the burner, a "backflow zone" forming in the area of the burner mouth, which prevents the flame from flashing back into the burner from the combustion chamber.

Kommt nun bei einer Brennerkammer mit einem hohen Druckverhältnis als Brennstoff Dieselöl zum Einsatz, so hat sich gezeigt, dass dieses bei hohen Druckverhältnissen sofort nach dessen Einmischung in den Brenner zünden kann. Aus diesem Grund kann ein vormischartiger Betrieb bei höheren Druckverhältnissen mit flüssigen Brennstoffen nicht immer erreicht werden. Der Grund für die starken Abweichungen bezüglich Zündverzugszeit hängt mit der Flammenstrahlung zusammen: Bei hohem Druck wird die Flammenstrahlung (H₂O, CO) sehr stark ausfallen; ein nennenswerter Teil der Strahlung wird von den Brennstofftröpfchen (undurchsichtiger Nebel) absorbiert. Dieser Mechanismus der Energieübertragung auf den flüssigen Brennstoff führt zu einer drastischen Reduktion der Zündverzugszeit.If diesel oil is now used as the fuel in a burner chamber with a high pressure ratio, it has been shown that this can ignite at high pressure conditions immediately after it has been mixed into the burner. For this reason, premixed operation cannot always be achieved with liquid fuels at higher pressure ratios. The reason for the large variations in terms Ignition delay time is related to the flame radiation: At high pressure the flame radiation (H₂O, CO) will be very strong; a significant part of the radiation is absorbed by the fuel droplets (opaque mist). This mechanism of energy transfer to the liquid fuel leads to a drastic reduction in the ignition delay time.

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 Verfahren der eingangs genannten Art die Wechselwirkung zwischen Flammenstrahlung und Brennstofftröpfchen, welche zu einer Frühzündung des Gemisches führt, zu unterbinden.The invention seeks to remedy this. The invention, as characterized in the claims, is based on the object of preventing the interaction between flame radiation and fuel droplets, which leads to early ignition of the mixture, in a method of the type mentioned.

Der wesentliche Vorteil der Erfindung ist darin zu sehen, dass die Eindüsung und Verdampfung des Brennstoffes von der Flammenstrahlung abgeschirmt wird, dergestalt, dass der Brennstoff erst nach dessen Verdampfung im Strahlungsbereich der Flamme tritt. Da ein verdampfter Brennstoff kaum noch Flammenstrahlung absorbiert, ist die Gefahr einer Frühzündung des Gemisches damit gebannt.The main advantage of the invention can be seen in the fact that the injection and vaporization of the fuel is shielded from the flame radiation in such a way that the fuel only enters the radiation area of the flame after it has evaporated. Since a vaporized fuel hardly absorbs flame radiation, the danger of the mixture igniting prematurely is averted.

Vorteilhafte und zweckmässige Weiterbildungen der erfindungsgemässen Aufgabenlösung sind in den weiteren abhängigen Ansprüchen gekennzeichnet.Advantageous and expedient developments of the task solution according to the invention are characterized in the further 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 Strömungsichtung der Medien ist mit Pfeilen angegeben. In den verschiedenen Figuren sind gleiche Elemente jeweils 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 direction of flow of the media is indicated by arrows. In the different figures, the same elements are each provided with the same reference symbols.

KURZE BESCHREIBUNG DER FIGURENBRIEF DESCRIPTION OF THE FIGURES

Es zeigt:

Fig.1
eine perspektivische Darstellung des Brennerkörpers, entsprechend aufgeschnitten, mit angedeuteter tangentialer Luftzuführung und
Fig.2
eine schematische Darstellung der Luftzuführung im Bereich einer Brennstoffdüse als Schnitt II-II aus Fig. 1.
It shows:
Fig. 1
a perspective view of the burner body, cut open accordingly, with indicated tangential air supply and
Fig. 2
2 shows a schematic representation of the air supply in the area of a fuel nozzle as section II-II from FIG. 1.

BESCHREIBUNG DER AUSFÜHRUNGSBEISPIELEDESCRIPTION OF THE EMBODIMENTS

Um den Aufbau des Brenners besser zu erfassen, ist es von Vorteil, wenn die Fig. 1 und 2 beim Studium der Beschreibung gleichzeitig ausgelegt werden. Des weiteren, um die einzelnen Figuren nicht unübersichtlich zu gestalten, sind Teilaspekte des Brenners auf die einzelnen Figuren verteilt worden, wobei bei der Beschreibung dieser Figuren auf diesen Tatbestand hingewiesen wird.In order to better grasp the structure of the burner, it is advantageous if FIGS. 1 and 2 are interpreted simultaneously when studying the description. Furthermore, in order not to confuse the individual figures, partial aspects of the burner have been distributed to the individual figures, reference being made to this fact in the description of these figures.

Der Kernkörper des in Fig. 1 gezeigten Brenners besteht aus zwei halben hohlen Teilkegelkörpern 1, 2, die versetzt zueinander aufeinander liegen. Die Versetzung der jeweiligen Mittelachsen schafft auf beiden Seiten in achsensymmetrischer Anordnung jeweils einen tangentialen Eintrittsschlitz 1c, 2c (Fig. 2) frei, durch welche ein Luft/Brennstoff-Gemisch 6 in den Innenraum 3 des Brenners, d.h. in den Kegelhohlraum, strömt. Im Lichte der Form dieses Brenners wird er nachfolgend auch "Doppelkegelbrenner" oder "BV-Brenner" genannt.The core body of the burner shown in Fig. 1 consists of two half hollow partial cone bodies 1, 2, which are offset from one another. The offset of the respective central axes creates a tangential entry slot 1c, 2c (FIG. 2) on both sides in an axially symmetrical arrangement, through which an air / fuel mixture 6 flows into the interior 3 of the burner, ie into the cone cavity. In the light of the shape of this burner, it is also called "double-cone burner" or "BV burner" below.

Die Kegelform der gezeigten Teilkegelkörper 1, 2 in Strömungsrichtung weist einen bestimmten festen Winkel auf. Selbstverständlich können die Teilkegelkörper 1, 2 in Strömungsrichtung eine zunehmende Kegelneigung (konvexe Form) oder eine abnehmende Kegelneigung (konkave Form) beschreiben. Die beiden letztgenannten Formen sind zeichnerisch nicht erfasst, da sie ohne weiteres nachempfindbar sind.The conical shape of the partial conical bodies 1, 2 shown in the flow direction has a certain fixed angle. Of course, the partial cone bodies 1, 2 can describe an increasing cone inclination (convex shape) or a decreasing cone inclination (concave shape) in the direction of flow. The last two forms are not included in the drawing, since they can easily be traced.

Welche Form schlussendlich zum Einsatz gelangt, hängt von den verschiedenen Parametern des Verbrennungsprozesses ab. Vorzugsweise wird die zeichnerisch gezeigte Form eingesetzt. Die tangentiale Eintrittsschlitzbreite ist ein Mass, das aus der Versetzung der beiden Mittelachsen (1b, 2b aus Fig. 2) zueinander resultiert.Which form is ultimately used depends on the various parameters of the combustion process. The form shown in the drawing is preferably used. The tangential entry slot width is a measure that results from the displacement of the two central axes (1b, 2b from FIG. 2) with respect to one another.

Die beiden Teilkegelkörper 1, 2 haben je einen zylindrischen Anfangsteil 1a, 2a, die ebenfalls, analog den genannten Teilkegelkörpern 1, 2, versetzt zueinander verlaufen, so dass die tangentialen Lufteintritte 1c, 2c (Fig. 2) über die ganze Länge des BV-Brenners an vorhanden sind. Selbstverständlich kann der BV-Brenner rein kegelig ausgeführt sein, also ohne einen zylindrischen Anfangsteil. Brennraumseitig 8 weist der BV-Brenner eine Wand 9 auf, welche beispielsweise die Eintrittsfront einer Ringbrennkammer oder einer Feuerungsanlage bildet. Das durch die tangentialen Lufteintritte 1c, 2c (Fig. 2) in den Innenraum 3 des BV-Brenners einströmende Luft/Brennstoff-Gemisch 6 bildet, entsprechend dem Verlauf des BV-Brenners, ein kegeliges Gemisch-Profil 10, das sich wirbelmässig in Strömungsrichtung windet. Im Bereich des Wirbelaufplatzens, also am Ende des BV-Brenners, wo sich eine Rückströmzone 11 bildet, wird die optimale, homogene Brennstoffkonzentration über den Querschnitt erreicht, also ein sehr gleichförmiges Brennstoff/Luft-Gemisch liegt im Bereich der Rückströmzone 11 vor. Die Zündung selbst erfolgt an der Spitze der Rückströmzone 11; erst an dieser Stelle kann eine stabile Flammenfront 12 entstehen. Ein Rückschlag der Flamme ins Innere des BV-Brenners, wie dies bei bekannten Vormischstrecken stets zu befürchten ist, wogegen dort mit komplizierten Flammenhaltern Abhilfe gesucht wird, ist hier nicht zu befürchten: Erstens, bei der Gestaltung der Teilkegelkörper 1, 2 hinsichtlich ihrer Kegelwinkel und der Breite der tangentialen Lufteintritte sind enge Grenzen einzuhalten, damit sich das gewünschte Strömungsfeld des Gemisches 6 mit seiner Rückströmzone 11 im Bereich der Brennermümdung zur Flammenstabilisierung einstellt.The two partial cone bodies 1, 2 each have a cylindrical initial part 1a, 2a, which, similarly to the partial cone bodies 1, 2 mentioned, also run offset from one another, so that the tangential air inlets 1c, 2c (FIG. 2) over the entire length of the BV Brenners are present. Of course, the BV burner can be designed to be purely conical, that is to say without a cylindrical initial part. On the combustion chamber side 8, the BV burner has a wall 9 which, for example, forms the inlet front of an annular combustion chamber or a furnace. The air / fuel mixture 6 flowing through the tangential air inlets 1c, 2c (FIG. 2) into the interior 3 of the BV burner forms, according to the course of the BV burner, a conical mixture profile 10 which swirls in the direction of flow twists. In the area of the vortex runout, i.e. at the end of the BV burner, where a backflow zone 11 forms, the optimal, homogeneous fuel concentration is achieved over the cross section, that is to say a very uniform fuel / air mixture is present in the area of the backflow zone 11. The ignition itself takes place at the top of the backflow zone 11; Only at this point can a stable flame front 12 arise. A flashback of the flame into the interior of the BV burner, as is the case with known premixing sections There is always to be fear, against which remedies are sought with complicated flame holders, there is no fear here: First, when designing the partial cone bodies 1, 2 with regard to their cone angle and the width of the tangential air inlets, narrow limits must be observed so that the desired flow field of the Mixture 6 with its backflow zone 11 in the area of the burner trough for flame stabilization.

Zweitens, indem die Eindüsung des Brennstoffes und Verdampfung desselben von der Flammenstrahlung der Flammenfront 12 abgeschirmt ist, wie dies aus Fig. 2 schematisch besonders gut ersichtlich ist, findet zwischen Flammenstrahlung und Brennstofftröpfchen keine Wechselwirkung statt, demnach ist auch mithin die Gefahr einer Frühzündung des Gemisches 6 gebannt. Im Falle der Verdampfung vor dem Eintritt in die Verbrennungszone im Bereich der Flammmenfront 12 sind die Schadstoffemissionswerte am niedrigsten.Secondly, since the fuel injection and vaporization are shielded from the flame radiation from the flame front 12, as can be seen particularly well from FIG. 2, there is no interaction between flame radiation and fuel droplets, and consequently there is also a risk of the mixture igniting prematurely 6 banned. In the case of evaporation before entering the combustion zone in the area of the flame front 12, the pollutant emission values are the lowest.

Fig. 2 ist ein Schnitt durch den BV-Brenner entlang der Ebene II-II, wo sich auch zwei Brennstoffdüsen 4a, 4b befinden. Die Anzahl und Gösse der in Strömungsrichtung des BV-Brenners vorgesehenen Brennstoffdüsen hängt von der durch diesen BV-Brenner zu erbringenden Leistung ab. Demnach, der Brennstoff 4c, 4d wird über eine Anordnung von Brennstoffdüsen 4a, 4b, die beim Einsatz eines flüssigen Brennstoffes vorzugsweise als Injektordüsen ausgebildet sind, in Einlauf-Kanälen 7a, 7b vor dem eigentlichen Eintritt in den Innenraum 3 des Doppelkegelbrenners eingebracht und dort vorverdampft. Die Geschwindigkeit der Verbrennungsluft 5 und der Abstand der Brennstoffdüsen von den Eintrittsschlitzen 1d, 2d in den Innenraum 3 des Brenners müssen derart auf die Temperatur der Verbrennungsluft 5, auf die Eigenschaften des Brennstoffes 4c, 4d und, beim flüssigen Brennstoff, die maximale Grösse der Brennstofftröpfchen abgestimmt sein, dass der Brennstoff im Gemisch 6 vor dem Erreichen der Eintrittsschlitze 1d, 2d vorverdampft ist, denn ab dieser Durchgangsstelle befindet sich das Gemisch 6 im "Sichtkontakt" mit der Flamme, d.h. mit der Flammenfront 12.Fig. 2 is a section through the BV burner along the plane II-II, where there are also two fuel nozzles 4a, 4b. The number and size of the fuel nozzles provided in the flow direction of the BV burner depend on the power to be provided by this BV burner. Accordingly, the fuel 4c, 4d is introduced via an arrangement of fuel nozzles 4a, 4b, which are preferably designed as injector nozzles when using a liquid fuel, in inlet channels 7a, 7b before the actual entry into the interior 3 of the double-cone burner and pre-evaporated there . The speed of the combustion air 5 and the distance of the fuel nozzles from the inlet slots 1d, 2d into the interior 3 of the burner must thus depend on the temperature of the combustion air 5, on the properties of the fuel 4c, 4d and, in the case of liquid fuel, the maximum size of the fuel droplets be matched that the fuel is pre-evaporated in the mixture 6 before reaching the entry slots 1d, 2d, because from this passage point the mixture 6 is in "visual contact" with the flame, ie with the flame front 12.

Vorteilhaft ist es, wenn die Verbrennungsluft 5 ein Luft/Abgas-Gemisch ist: Diese Rückführung einer Menge eines teilgekühlten Abgases, das ursprünglich eine Temperatur von ca. 950 °C aufweist ist auch für einen optimalen Betrieb des Doppelkegelbrenners erforderlich, wenn dieser in atmosphärischen Feuerungsanlagen bei nahstöchiometrischer Fahrweise eingesetzt ist. Das optimale Massenstromverhältnis, d.h. das Verhältnis zwischen rückgeführtem Abgas und zugeführter Frischluft, beträgt etwa 0,7.It is advantageous if the combustion air 5 is an air / exhaust gas mixture: this recirculation of a quantity of a partially cooled exhaust gas, which originally has a temperature of approx. 950 ° C., is also necessary for optimal operation of the double-cone burner when it is used in atmospheric combustion plants is used for near-stoichiometric driving. The optimal mass flow ratio, i.e. the ratio between recirculated exhaust gas and fresh air supplied is about 0.7.

Bei einer Frischlufttemperatur von beispielsweise 15 °C und einer Abgastemperatur von ca. 950 °C wird eine Mischtemperatur des Luft/Abgas-Gemisches, das nun an Stelle der Verbrennungsluft 5 eingeführt wird, von ca. 400 °C erreicht. Diese Verhältnisse führen bei einem Doppelkegelbrenner von etwa 100 - 200 KW thermischer Leistung zu optimalen Verdampfungsbedingungen für den flüssigen Brennstoff, zu einer Minimierung der NOx/CO/UHC-Emissionen, womit auch die Gefahr einer Rückzündung wegen der Wechselwirkung zwischen Flammstrahlung und Brennstofftröpfchen inexistent wird.At a fresh air temperature of, for example, 15 ° C. and an exhaust gas temperature of approximately 950 ° C., a mixed temperature of the air / exhaust gas mixture, which is now introduced instead of the combustion air 5, of approximately 400 ° C. is reached. With a double-cone burner with a thermal output of around 100 - 200 KW, these conditions lead to optimal evaporation conditions for the liquid fuel, to a minimization of NO x / CO / UHC emissions, which also means that there is no danger of reignition due to the interaction between flame radiation and fuel droplets .

Claims (4)

Verfahren für eine Vormischverbrennung eines flüssigen Brennstoffes in einem Brenner, dadurch gekennzeichnet, dass die Eindüsung und Verdampfung des Brennstoffes mit einem gasförmigen Medium von der direkten Flammenstrahlung aus der Flammenfront des Brenners abgeschirmt werden.Method for premix combustion of a liquid fuel in a burner, characterized in that the injection and evaporation of the fuel are shielded from the direct flame radiation from the flame front of the burner with a gaseous medium. Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass die Verdampfung des Brennstoffes mit einem Luft/Abgas-Gemisch durchgeführt wird.A method according to claim 1, characterized in that the evaporation of the fuel is carried out with an air / exhaust gas mixture. Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass das Verhältnis zwischen rückgeführtem Abgas und zugeführter Luft 0,7 beträgt.A method according to claim 1, characterized in that the ratio between recirculated exhaust gas and air supplied is 0.7. Brenner zur Durchführung des Verfahrens nach Anspruch 1, dadurch gekennzeichnet, dass der Brenner aus zwei aufeinander positionierten Teilkegelkörper (1, 2) mit einer in Strömungsrichtung sich öffnenden Kegelform besteht, dass die Mittelachsen (1b, 2b) dieser Teilkegelkörper (1, 2) in Längsrichtung zueinander versetzt verlaufen, dergestalt, dass über die Länge des Brenners tangentiale Einlauföffnungen (1c, 2c) zum Innenraum (3) des Brenners entstehen, dass oberhalb jeder Einlauföffnung (1c, 2c) in einem ausserhalb des durch die Teilkegelkörper (1, 2) gebildeten Brenners in den Innenraum (3) dieses Brenners mündenden Kanal (7a, 7b) mindestens eine Brennstoffdüse (4a, 4b) vorhanden ist, deren Brennstoff (4c, 4d) im Kanal (7a, 7b) mit einem gasförmigen Medium (5) vermischbar ist.Burner for carrying out the method according to claim 1, characterized in that the burner consists of two partial cone bodies (1, 2) positioned one on top of the other with a conical shape opening in the flow direction, that the central axes (1b, 2b) of these partial cone bodies (1, 2) in The longitudinal direction is offset from one another in such a way that over the length of the burner there are tangential inlet openings (1c, 2c) to the interior (3) of the burner that above each inlet opening (1c, 2c) in an outside of the through the partial cone body (1, 2) formed burner in the interior (3) of this burner opening channel (7a, 7b) there is at least one fuel nozzle (4a, 4b), the fuel (4c, 4d) in the channel (7a, 7b) can be mixed with a gaseous medium (5) is.
EP90123494A 1989-12-19 1990-12-07 Method for a premix burning of a liquid fuel Withdrawn EP0433789A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH4543/89 1989-12-19
CH4543/89A CH680946A5 (en) 1989-12-19 1989-12-19

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EP0433789A1 true EP0433789A1 (en) 1991-06-26

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US (1) US5085575A (en)
EP (1) EP0433789A1 (en)
JP (1) JPH03294707A (en)
CA (1) CA2032202A1 (en)
CH (1) CH680946A5 (en)
PL (1) PL288224A1 (en)

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EP0503319A2 (en) * 1991-03-12 1992-09-16 Asea Brown Boveri Ag Burner for a premixing combustion of a liquid and/or a gaseous fuel
DE19502796A1 (en) * 1995-01-30 1996-08-01 Abb Management Ag burner
EP0777081A3 (en) * 1995-12-02 1998-10-21 Abb Research Ltd. Premix burner
EP0981019A1 (en) * 1998-08-20 2000-02-23 Asea Brown Boveri AG Method and burner for combustion of liquid fuels
EP0981016A1 (en) * 1998-08-19 2000-02-23 Asea Brown Boveri AG Burner and method for operating an internal combustion engine

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US5450724A (en) * 1993-08-27 1995-09-19 Northern Research & Engineering Corporation Gas turbine apparatus including fuel and air mixer
DE4330083A1 (en) * 1993-09-06 1995-03-09 Abb Research Ltd Method of operating a premix burner
US5408825A (en) * 1993-12-03 1995-04-25 Westinghouse Electric Corporation Dual fuel gas turbine combustor
DE10049205A1 (en) * 2000-10-05 2002-05-23 Alstom Switzerland Ltd Process for supplying fuel to a premix burner for operating a gas turbine comprises introducing premix gas separately via two axially divided regions along the burner shell
DE10051221A1 (en) * 2000-10-16 2002-07-11 Alstom Switzerland Ltd Burner with staged fuel injection
US20050032012A1 (en) * 2003-05-16 2005-02-10 Eil Louis Van Method and apparatus for detecting a burner flame of a gas appliance
WO2006094939A1 (en) * 2005-03-09 2006-09-14 Alstom Technology Ltd Burner comprising a premix for combustion chamber
US8622053B2 (en) 2009-03-16 2014-01-07 Planika Sp. Z O.O. Burner and method of its operation
US8418469B2 (en) 2010-09-27 2013-04-16 General Electric Company Fuel nozzle assembly for gas turbine system
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CN103032873A (en) * 2013-01-22 2013-04-10 江苏索尔自动化设备有限公司 Cyclone type oxygen supply distributor
US9964043B2 (en) 2014-11-11 2018-05-08 General Electric Company Premixing nozzle with integral liquid evaporator
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EP0503319A2 (en) * 1991-03-12 1992-09-16 Asea Brown Boveri Ag Burner for a premixing combustion of a liquid and/or a gaseous fuel
EP0503319A3 (en) * 1991-03-12 1993-02-24 Asea Brown Boveri Ag Burner for a premixing combustion of a liquid and/or a gaseous fuel
DE19502796A1 (en) * 1995-01-30 1996-08-01 Abb Management Ag burner
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DE19502796B4 (en) * 1995-01-30 2004-10-28 Alstom burner
EP0777081A3 (en) * 1995-12-02 1998-10-21 Abb Research Ltd. Premix burner
EP0981016A1 (en) * 1998-08-19 2000-02-23 Asea Brown Boveri AG Burner and method for operating an internal combustion engine
EP0981019A1 (en) * 1998-08-20 2000-02-23 Asea Brown Boveri AG Method and burner for combustion of liquid fuels

Also Published As

Publication number Publication date
PL288224A1 (en) 1991-12-02
JPH03294707A (en) 1991-12-25
CA2032202A1 (en) 1991-06-20
US5085575A (en) 1992-02-04
CH680946A5 (en) 1992-12-15

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