EP1730447A1 - Burner - Google Patents

Burner

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Publication number
EP1730447A1
EP1730447A1 EP05729532A EP05729532A EP1730447A1 EP 1730447 A1 EP1730447 A1 EP 1730447A1 EP 05729532 A EP05729532 A EP 05729532A EP 05729532 A EP05729532 A EP 05729532A EP 1730447 A1 EP1730447 A1 EP 1730447A1
Authority
EP
European Patent Office
Prior art keywords
fuel
burner
combustion air
fuel injection
air 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.)
Withdrawn
Application number
EP05729532A
Other languages
German (de)
French (fr)
Inventor
Christian Oliver Paschereit
Bruno Schuermans
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP1730447A1 publication Critical patent/EP1730447A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
    • 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
    • F23D2210/00—Noise abatement

Definitions

  • the invention relates to a burner according to the preamble of the first claim.
  • the fluid mechanical stability of a burner is of crucial importance for the occurrence of thermoacoustic vibrations. Fluid mechanics see instability waves that arise at the burner, lead to the formation of vortices, so-called coherent structures, which influence the combustion and can lead to periodic heat release with the associated pressure fluctuations. These high amplitude pressure fluctuations can limit the operating range and can increase the emissions associated with combustion. These problems occur particularly in combustion systems with low acoustic damping, as are often represented by modern gas turbines. In the lean combustion area in particular, there may be a periodic loss of flame stabilization, which likewise leads to pulsations. Coherent structures play a crucial role in mixing processes between air and fuel. The spatial and temporal dynamics of these structures influence combustion and heat release.
  • a method was known from EP 0 918 152 A1, in which means for acoustically exciting the working gas were arranged in the area of the burner in order to counteract the formation of coherent structures. The intention was to excite the shear layer formed in the area of the burner in order to require as little excitation energy as possible. To determine the excitation energy to be introduced and its frequency, the instantaneous acoustic excitation of the shear layer was phase-coupled with a signal measured in the combustion system. However, this method requires considerable means to control the thermoacoustic vibrations z_u.
  • Adjusting the mixture profile in the burner can also have a direct impact on pulsations and emissions.
  • a burner with a stepped injection is known from DE 100 64 893 A1, the fuel outlet openings being divided into at least three groups and the fuel mass flow of the groups being able to be regulated independently of one another axially symmetrically via valves. Opposing nozzles are combined and not controlled independently.
  • the flame shape and position can be changed by essentially changing the mixture profile. This can reduce the influence of flow instabilities as well as time delay effects. This minimizes one changes the occurrence of fluctuations in the heat release and thus the thermoacoustic oscillation.
  • the object of the invention is to suppress thermoacoustic vibrations even more effectively in a burner of the type mentioned at the outset.
  • the essence of the invention is therefore that the injection of the fuel into the combustion air via the injection means is asymmetrical.
  • the advantages of the invention include the fact that pulsations can be prevented even more effectively by the asymmetrical injection of fuel.
  • the asymmetry relates to pairs of injection openings located opposite each other in the direction of flow.
  • the asymmetry can take place statically in that no injection opening is arranged in the area opposite an injection opening. However, this can also be done by individually regulating the fuel supply to the fuel injection openings which are symmetrical per se.
  • Opposing fuel injection openings ⁇ are then fed by means of the control different amounts of fuel and thus an asymmetrical fuel profile is achieved in the swirl chamber of the swirl generator.
  • Figure 1 is a perspective view of a burner, partially cut away.
  • Figure 2 shows a section through the plane II-II in Figure 1;
  • FIG. 3 shows a section through the plane III-III in FIG. 1;
  • Figure 4 is a section through the plane IV-IV in Figure 1; 5 shows a burner according to the invention in a perspective illustration and with an illustration of the half shells;
  • Fig. 8 shows an inverted double cone burner with individually controllable fuel nozzles.
  • the burner according to FIG. 1 consists of a swirl generator 30 which is essentially constructed from two half-hollow partial cone bodies 1, 2 which are offset from one another. Such a burner is called a double-cone burner.
  • the offset of the respective central axis 1b, 2b of the partial cone bodies 1, 2 to one another creates a tangential air inlet slot 19, 20 (FIGS. 2-4) through both sides in a mirror-image arrangement, through which the combustion air 15 enters the interior of the Brenners, ie flows into the cone cavity 14 or also called swirl space.
  • 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 Bren ner can be designed purely conical, that is, without cylindrical starting 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, which is mixed with the combustion air 15 flowing through the tangential air inlet slots 19, 20.
  • 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 takes place there, in the combustion chamber 22 on the combustion chamber side the burner has at the burner outlet 29 a collar-shaped end plate 10 serving as anchoring for the partial cone bodies 1, 2 with a number of bores 11 through which, if necessary, dilution air or cooling air 18 passes to the front part of the combustion chamber of the combustion chamber 22 or its wall can be supplied.
  • 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 are not wetted by the injected liquid fuel 12.
  • 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 is burned, the mixture formation takes place 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 percent. 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 cone inclination and the width of the tangential air inlet slots 19, 20 have to be kept within narrow limits so that the desired flow field of the air with its return flow zone 6 is established in the area of the burner mouth to the flame rod.
  • Flow initiation functions wherein 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 21 a, 21 b about the pivot point 23.
  • the swirl generator 30, consisting of the partial cone body 1 with the fuel line 8 and the partial cone body 2 with the fuel line 9, is in the operating position on the left-hand side and in a comparative position on the right-hand side in order to compare the configuration of the two partial cone bodies , shown.
  • the openings 17a of the fuel line 8 are arranged asymmetrically with respect to the openings 17b of the fuel line 9.
  • Fuel openings IT'a thus lie opposite areas of the fuel line 9 in which no fuel openings are arranged, and fuel openings 17b thus lie opposite areas of the fuel line 8 in which no fuel openings are arranged. This creates an asymmetrical fuel profile when the fuel is injected into the combustion air.
  • Pulsations are suppressed by this asymmetrical arrangement of the fuel openings 17a and 17a and the asymmetrical fuel profile generated thereby.
  • the type and strength of the asymmetry generated must be adapted to the special case. Burner system with few pulsations can cause a slight asymmetry of the fuel nozzle, in systems with high pulsations, the asymmetry must be increased.
  • the asymmetry is set in a test facility in accordance with the method described in FIG. 7 below.
  • the setting can e.g. by trying it out or by means of an optimization algorithm.
  • the asymmetry is set in this way, e.g. by means of valves that the pulsations are minimal and the pollutant emission is at an acceptable level.
  • the swirl chamber 14 is formed by the partial cone shells 1 and 2.
  • the combustion air flows through the air inlet slots 19 and 20 into the swirl chamber 14.
  • the resulting fuel-air mixture is transported into the combustion chamber and ignited.
  • the double-cone burner has eight fuel injection ovens 17a and 17b at each air inlet slot 19, 20, which are individually supplied with fuel via a line.
  • a valve 31 to 38 or respectively 41 to 48 is arranged in each of these lines, wherein each of these valves can be regulated independently of the other.
  • Fuel injection openings 17a and 17b are controlled by means of the valves 31 and -41, 32 and 42, 33 and 43, etc., in such a way that at least one of the eight opposite pairs of fuel openings has a different fuel mass flow with respect to the fuel opening opposite them, and thus an asymmetrical one Fuel is supplied.
  • the degree of pulsations can be determined via sensors in the combustion chamber 22 and the degree of asymmetry can be adapted to the conditions by means of the fuel injection openings 17a and IT 'and the associated valve pairs 31 and 41, etc.
  • This asymmetry control can of course be combined with a staged combustion according to the disclosure of DE 100 64 893 A1 in order to prevent harmful pulsations even more effectively.
  • the asymmetry for specific systems is set in a test facility with the aid of electrically controllable valves. These are controlled by a control and regulation unit, e.g. controlled a computer. This computer also processes the measured pulsations and pollutant emissions. Using an algorithm, the valves are set so that the pulsations are minimized and the pollutant emissions remain below a defined level.
  • the algorithm can also be adapted for the specific system.
  • FIG. 1 Another type of swirl-generating burner, a so-called inverted double-cone burner, is shown in FIG.
  • the swirl generator is formed here from hollow partial cylinder bodies 50, 51 which are arranged offset with respect to one another and into whose interior projects a conical body 49 converging in the direction of flow.
  • the combustion air also enters the swirl chamber 14 through the inlet slots 19 and 23. Due to the cone body protruding into the interior space formed by the partial cylinder bodies, the combustion air entering the swirl chamber is also set in rotation here.
  • the double 7 are also arranged in the area of the air inlet slots, fuel openings 17a and 17b, through which fuel is injected into the combustion air. The resulting fuel-air mixture is transported into the combustion chamber and ignited.
  • the inverted double-cone burner has eight fuel injection openings 17a and 17b, which are individually supplied with fuel via a line.
  • a valve 31 to 38 or respectively 41 to 48 is arranged in each of these lines, wherein each of these valves can be regulated independently of the other.
  • opposite fuel injection openings 17a and 17b are now controlled by means of valves 31 and 41, 32 and 42, 33 and 43, etc., so that at least one of the eight opposite pairs of fuel openings has a different fuel mass flow with respect to the opposite one Has fuel opening and so an asymmetrical fuel supply takes place.
  • the invention is not limited to the exemplary embodiment shown and described.
  • the embodiment according to FIG. 5 can of course also be combined with the embodiment according to FIG. 7 and that according to FIG. 8. This can minimize the active control of the valves.
  • the number of fuel openings and thus the number of valves can be adjusted as required.
  • the burner can also have other shapes than shown in the exemplary embodiment and other types of burners can also be used.
  • the burner shown can with respect to
  • Shape and the size of the tangential air inlets 19, 20 can be varied as desired.

Abstract

Disclosed is a burner which substantially comprises a swirl generator (30) for a flow of combustion air (15), means (17, 17a, 17b, 31-38, 41-48) for introducing fuel into said flow of combustion air (15), and air inlet slots (19, 20). The flow of combustion air (15) enters an swirl chamber (14) of the swirl generator (30) via air inlet slots. The fuel is sprayed into the combustion air in an asymmetric manner via the spraying means (17, 17a, 17b, 31-38, 41-48).

Description

Brenner burner
Technisches GebietTechnical field
Die Erfindung geht aus von eine Brenner nach dem Oberbegriff des ersten Anspruches.The invention relates to a burner according to the preamble of the first claim.
Stand der TechnikState of the art
Die strömungsmechanische Stabilität eines Brenners ist von entscheidender Bedeutung für das Auftreten thermoakustischer Schwingungen. Strömungsmechani- sehe Instabilitätswellen, die am Brenner entstehen, führen zur Ausbildung von Wirbeln, sogenannten kohärenten Strukturen, die die Verbrennung beeinflussen und zu periodischer Wärmefreisetzung mit den damit verbundenen Druckschwankungen führen können. Diese Druckschwankungen hoher Amplitude können zu einer Einschränkung des Betriebsbereiches führen und können die mit der Verbrennung verbundenen Emissionen erhöhen. Diese Probleme treten besonders in Verbrennungssystemen mit geringer akustischer Dämpfung, wie sie moderne Gasturbinen oft darstellen, auf. Insbesondere im mageren Bereich der Verbrennung kann es zu einem periodischen Verlust der Flammenstabilisierung kommen, der ebenfalls zu Pulsationen führt. Kohärente Strukturen spielen eine entscheidende Rolle bei Mischungsvorgängen zwischen Luft und Brennstoff. Die räumliche und zeitliche Dynamik dieser Strukturen beeinflußt die Verbrennung und die Wärmefreisetzung. Aus der EP 0 918 152 A1 wurde ein Verfahren bekannt, bei dem im Bereich des Brenners Mittel zur a- kustischen Anregung des Arbeitsgases angeordnet wurden, um der Ausbildung kohärenter Strukturen entgegenzuwirken. Vorgesehen wurde dabei, die sich im Bereich des Brenners ausgebildete Scherschicht anzuregen, um möglichst wenig Anregungsenergie zu benötigen. Zu r Bestimmung der einzubringenden Anregungsenergie und deren Frequenz wurde die momentane akustische Anregung der Scherschicht mit einem in dem Verbrennungssystem gemessenen Signal phasengekoppelt. Dieses Verfahren benötigt jedoch erhebliche Mittel um die thermoakustischen Schwingungen z_u kontrollieren.The fluid mechanical stability of a burner is of crucial importance for the occurrence of thermoacoustic vibrations. Fluid mechanics see instability waves that arise at the burner, lead to the formation of vortices, so-called coherent structures, which influence the combustion and can lead to periodic heat release with the associated pressure fluctuations. These high amplitude pressure fluctuations can limit the operating range and can increase the emissions associated with combustion. These problems occur particularly in combustion systems with low acoustic damping, as are often represented by modern gas turbines. In the lean combustion area in particular, there may be a periodic loss of flame stabilization, which likewise leads to pulsations. Coherent structures play a crucial role in mixing processes between air and fuel. The spatial and temporal dynamics of these structures influence combustion and heat release. A method was known from EP 0 918 152 A1, in which means for acoustically exciting the working gas were arranged in the area of the burner in order to counteract the formation of coherent structures. The intention was to excite the shear layer formed in the area of the burner in order to require as little excitation energy as possible. To determine the excitation energy to be introduced and its frequency, the instantaneous acoustic excitation of the shear layer was phase-coupled with a signal measured in the combustion system. However, this method requires considerable means to control the thermoacoustic vibrations z_u.
Aus der DE 100 56 124 A1 ist es bekannt, mittels einer gestuften Eindusung des Brennstoffes die Flammenposition zu beeinflussen und damit den Einfluss von Strömungsinstabilitäten als auch Zeϊtverzugseffekten zu vermindern. Dazu sind Messwertaufnehmer zur Erfassung der Pulsationen und Emissionen der Verbrennung sowie Kontrolleinrichtungen, welche die gestuften Eindüsungen ansteuern, notwendig.From DE 100 56 124 A1 it is known to influence the flame position by means of a graduated injection of the fuel and thus to reduce the influence of flow instabilities and time delay effects. For this purpose, measuring sensors for recording the pulsations and emissions of the combustion as well as control devices that control the staged injections are necessary.
Auch die Anpassung des Mischungsprofils im Brenner kann einen direkten Einfluss auf die Pulsationen und Emissionen haben. Aus der DE 100 64 893 A1 ist ein Brenner mit einer gestuften Eindusung bekannt, wobei die Brennstoff- Austrittsöffnungen in wenigstens drei Gruppen unterteilt sind und der Brennstoffmassenstrom der Gruppen über Ventile unabhängig voneinander axialsymmetrisch regelbar ist. Gegenüberliegende Düsen werden dabei zusammengefasst und nicht unabhängig voneinander angesteuert. Durch die im wesentlichen beliebiga Änderung des Mischungsprofils lassen sich Flammenform und Flammenlage ändern. Damit lässt sich der Einfluss von Strömungsinstabilitäten als auch Zeitverzugseffekten vermindern. Hierdurch vermin- dert man das Auftreten von Fluktuationen in der Wärmefreisetzung und damit die thermoakustische Schwingung.Adjusting the mixture profile in the burner can also have a direct impact on pulsations and emissions. A burner with a stepped injection is known from DE 100 64 893 A1, the fuel outlet openings being divided into at least three groups and the fuel mass flow of the groups being able to be regulated independently of one another axially symmetrically via valves. Opposing nozzles are combined and not controlled independently. The flame shape and position can be changed by essentially changing the mixture profile. This can reduce the influence of flow instabilities as well as time delay effects. This minimizes one changes the occurrence of fluctuations in the heat release and thus the thermoacoustic oscillation.
Darstellung der ErfindungPresentation of the invention
Der Erfindung liegt die Aufgabe zugrunde, bei einem Brenner der eingangs ge- nannten Art, thermoakustische Schwingungen noch wirkungsvoller zu unterdrücken.The object of the invention is to suppress thermoacoustic vibrations even more effectively in a burner of the type mentioned at the outset.
Erfindungsgemäss wird dies durch die Merkmale des ersten Anspruches erreicht.According to the invention, this is achieved by the features of the first claim.
Kern der Erfindung ist es also, dass die Eindusung des Brennstoffes in die Verbrennungsluft über die Eindusungs-Mittel asymmetrisch ist.The essence of the invention is therefore that the injection of the fuel into the combustion air via the injection means is asymmetrical.
Die Vorteile der Erfindung sind unter anderem darin zu sehen, dass durch die asymmetrische Eindusung von Brennstoff Pulsationen noch wirkungsvoller unterbunden werden können. Die Asymmetrie bezieht sich dabei auf sich in Strömungsrichtung gegenüberliegende Paare von Eindüsungsöffnungen. Die Asymmetrie kann dabei statisch erfolgen, indem im einer Eindüsungsöffnung gegenüberliegenden Bereich keine Eindüsungsöffnung angeordnet ist. Dies kann jedoch auch durch eine individuelle Regelung der Brennstoffzufuhr zu den an sich symmetrisch voriiegenden Brennstoffeindüsungsöffnungen erfolgen. Sich gegenüberliegende Brennstoffeindüsungsöffnungen ^werden dann mittels der Regelung unterschiedliche Mengen von Brennstoff zugeführt und so ein asymmetrisches Brennstoffprofil im Drallraum des Drallerzeugers erzielt. Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen und der Beschreibung.The advantages of the invention include the fact that pulsations can be prevented even more effectively by the asymmetrical injection of fuel. The asymmetry relates to pairs of injection openings located opposite each other in the direction of flow. The asymmetry can take place statically in that no injection opening is arranged in the area opposite an injection opening. However, this can also be done by individually regulating the fuel supply to the fuel injection openings which are symmetrical per se. Opposing fuel injection openings ^ are then fed by means of the control different amounts of fuel and thus an asymmetrical fuel profile is achieved in the swirl chamber of the swirl generator. Further advantageous embodiments of the invention result from the subclaims and the description.
Kurze Beschreibung der ZeichnungBrief description of the drawing
Im folgenden werden anhand der Zeichnungen /Xusführungsbeispiele der Erfin- düng näher erläutert. Gleiche Elemente sind in en verschiedenen Figuren mit den gleichen Bezugszeichen versehen. Die Strömungsrichtung der Medien ist mit Pfeilen angegeben.The drawings / exemplary embodiments of the invention are explained in more detail below. Identical elements are provided with the same reference symbols in different figures. The direction of flow of the media is indicated by arrows.
Es zeigen:Show it:
Fig. 1 einen Brenner in perspektivischer Darstellung, teilweise aufgeschnitten;Figure 1 is a perspective view of a burner, partially cut away.
Fig. 2 einen Schnitt durch die Ebene II-II in Fig.1 ;Figure 2 shows a section through the plane II-II in Figure 1;
Fig. 3 einen Schnitt durch die Ebene lll-lll in Fig.1 ;3 shows a section through the plane III-III in FIG. 1;
Fig. 4 einen Schnitt durch die Ebene IV-IV in Fig.1 ; Fig. 5 einen erfindungsgemässen Brenner in perspektivischer Darstellung und mit Darstellung der Halbschalen;Figure 4 is a section through the plane IV-IV in Figure 1; 5 shows a burner according to the invention in a perspective illustration and with an illustration of the half shells;
Fig. 6 Darstellung Grad der Asymmetrie gege n Pulsationen;6 shows the degree of asymmetry against pulsations;
Fig. 7 einen Doppelkegelbrenner mit individuell regelbaren Brennstoffdüsen;7 shows a double-cone burner with individually controllable fuel nozzles;
Fig. 8 einen umgekehrten Doppelkegelbrenner mit individuell regelbaren Brennstoffdüsen.Fig. 8 shows an inverted double cone burner with individually controllable fuel nozzles.
Es sind nur die für das unmittelbare Verständnis der Erfindung wesentlichen Elemente gezeigt, die Schnitte sind nur eine schemstische, vereinfachte Darstellung des Brenners. Weg zur Ausführung der ErfindungOnly the elements essential for the immediate understanding of the invention are shown; the sections are only a schematic, simplified representation of the burner. Way of carrying out the invention
Der Brenner gemäss Fig. 1 besteht aus einem Drallerzeuger 30 welcher im wesentlichen aus zwei halben hohlen Teilkegelkörpern 1 , 2, die versetzt zueinander aufeinander liegen, aufgebaut ist. Ein solcher Brenner wird als Doppelkegelbrenner bezeichnet. Die Versetzung der jeweiligen Mittelachse 1 b, 2b der Teilkegel- körper 1 , 2 zueinander schafft auf beiden Seiten in spiegelbi Idlicher Anordnung jeweils einen tangentialen Lufteintrittsschlitz 19, 20, (Fig. 2 - 4), durch welche die Verbrennungsluft 15 in den Innenraum des Brenners, d.h. in den Kegelhohlraum 14 oder auch Drallraum genannt 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 zylindrisch! en Anfangsteil 1 a, 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. Selbstverständlich kann der Bren ner rein kegelig, also ohne zylindrische Anfangsteile 1a, 2a, ausgeführt sein. Beide Teilkegelkörper 1 , 2 weisen je eine Brennstoffleitung 8, 9 auf, die mit Öffnungen "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 Brenn- Stoffleitungen 8, 9 sind am Ende der tangentialen Lufteintrittsschlitze 19, 20 angebracht, so dass dort die Zumischung 16 des gasförmigen Brennstoffes 13 mit der einströmenden Verbrennungsluft 15 stattfindet. Brennraumseitig in der Brennkammer 22 weist der Brenner am Brenneraustritt 29 eine kragenförmige, als Verankerung für die Teilkegelkörper 1 , 2 dienende, Abschlussplatte 10 mit einer An- zahl Bohrungen 11 auf, durch welche nötigenfalls Verdünnungsluft bzw. Kühlluft 18 dem vorderen Teil des Brennraumes der Brennkammer 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 Teil- kegelkörper 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 verbrannt, geschieht die Gemischbildu ng mit der Verbrennungsluft 15 direkt am Ende der Lufteintrittsschlitze 19, 20. Bei der Eindusung 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 Vormisctistrecken latent der Fall ist, ist hier prinzipiell 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 Grosse des Brenners, der Tropfengrössenverteilung und der Temperatur der Verbrennungsluft 15 abhängig. Unabhängig aber davon, ob neben der homogenen Tropfenvormischung durch Verbrennungsluft 1 5 niedriger Temperatur oder zusätzlich nur eine partielle oder die vollständige Tropfenverdampfung durch vorgeheizte Verbrennungsluft 15 erreicht wird, fallen die Stickoxid- und Kohlen- monoxidemissionen niedrig aus, wenn der Luftüberschuss mindestens 60 Prozent beträgt. Im Falle der vollständigen Verdampfung vor dem Eintritt in die Verbrennungszone sind die Schadstoffemissionswerte am niedrigsten. Gleiches gilt auch für den nahstochiometrischen Betrieb, wenn die Ueberschussluft durch rezirkulierendes Abgas ersetzt wird. Bei der Gestaltung der Teilkegelkörper 1 , 2 hinsieht- lieh 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 Flammenstab ϊlisie- rung einstellt. Allgemein ist zu sagen, dass eine Verkleinerung der Lufteintritts- schlitze 19, 20 die Rückströmzone 6 weiter stromaufwärts verschiebt, wod urch dann allerdings das Gemisch früher zur Zündung käme. Immerhin ist hier zu sagen, dass die einmal geometrisch fixierte Rückströmzone 6 an sich positio nsstabil ist, denn die Drallzahl nimmt in Strömungsrichtung im Bereich der Kegelform des Brenners zu. Aus Fig. 2 - 4 geht auch die Lage der Leitbleche 21a, 21 b hervor. Sie habenThe burner according to FIG. 1 consists of a swirl generator 30 which is essentially constructed from two half-hollow partial cone bodies 1, 2 which are offset from one another. Such a burner is called a double-cone burner. The offset of the respective central axis 1b, 2b of the partial cone bodies 1, 2 to one another creates a tangential air inlet slot 19, 20 (FIGS. 2-4) through both sides in a mirror-image arrangement, through which the combustion air 15 enters the interior of the Brenners, ie flows into the cone cavity 14 or also called swirl space. 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! In the initial part 1 a, 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 Bren ner can be designed purely conical, that is, without cylindrical starting 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, which is mixed with the combustion air 15 flowing through the tangential air inlet slots 19, 20. The location of these fuel lines 8, 9 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 takes place there, in the combustion chamber 22 on the combustion chamber side the burner has at the burner outlet 29 a collar-shaped end plate 10 serving as anchoring for the partial cone bodies 1, 2 with a number of bores 11 through which, if necessary, dilution air or cooling air 18 passes to the front part of the combustion chamber of the combustion chamber 22 or its wall can be supplied. 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 are not wetted by the injected liquid fuel 12. 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 is burned, the mixture formation takes place 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 greater than that in the area of vortex bursting, that is to say in the area of the backflow zone 6 Cross section reached. The ignition takes place at the top of the return flow zone 6. Only at this point can a stable flame front 7 arise. In principle, there is no fear of the flame returning to the interior of the burner, as is latently the case with pre-miscist sections. 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 low temperature or only partial or complete drop evaporation by preheated combustion air 15, the nitrogen oxide and carbon monoxide emissions are low if the excess air is at least 60 percent. 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, The cone inclination and the width of the tangential air inlet slots 19, 20 have to be kept within narrow limits so that the desired flow field of the air with its return flow zone 6 is established in the area of the burner mouth to the flame rod. 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 once-geometrically fixed return flow zone 6 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 position of the guide plates 21a, 21b also appears from FIGS. 2-4. They have
Strömungseinleitungsfunktionen, wobei sie, verschieden lang, das jeweiligje 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 21 a, 21 b um den Drehpunkt 23 optimiert werden.Flow initiation functions, wherein 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 21 a, 21 b about the pivot point 23.
In Fig. 5 ist der Drallerzeuger 30 bestehend aus dem Teilkegelkörper 1 mit der Brennstoffleitung 8 und dem Teilkegelkörper 2 mit der Brennstoffleitung 9 auf der linken Seite in Betriebsposition und auf der rechten Seite in einer Vergleicthsposi- tion, um die Ausgestaltung der beiden Teilkegelkörper zu vergleichen, dargestellt. Die Öffnungen 17a der Brennstoffleitung 8 sind gegenüber den Öffnungen 17b der Brennstoffleitung 9 asymmetrisch angeordnet. Brennstofföffnungen IT'a liegen somit Bereichen der Brennstoffleitung 9 gegenüber, in denen keine Brennstofföffnungen angeordnet sind und Brennstofföffnungen 17b liegen somit Bereichen der Brennstoffleitung 8 gegenüber, in denen keine Brennstofföffnungen angeordnet sind. Dadurch wird bei der Eindusung des Brennstoffes in die Brennluft ein asymmetrisches Brennstoffprofil erzeugt. Durch diese asymmetrische Anordnung der Brennstofföffnungen 17a und 17a und das dadurch erzeugte asymmetrische Brennstoffprofil werden Pulsationen unterdrückt. Die Art und Stärke der erzeugten Asymmetrie muss dabei jeweils dem Spezialfall angepasst werden. Brennersystem mit wenigen Pulsationen können eine geringe Asymmetrie der Brennstoffein- düsung aufweisen, bei Systemen mit hohen Pulsationen muss die Asymmetrie verstärkt werden.5, the swirl generator 30, consisting of the partial cone body 1 with the fuel line 8 and the partial cone body 2 with the fuel line 9, is in the operating position on the left-hand side and in a comparative position on the right-hand side in order to compare the configuration of the two partial cone bodies , shown. The openings 17a of the fuel line 8 are arranged asymmetrically with respect to the openings 17b of the fuel line 9. Fuel openings IT'a thus lie opposite areas of the fuel line 9 in which no fuel openings are arranged, and fuel openings 17b thus lie opposite areas of the fuel line 8 in which no fuel openings are arranged. This creates an asymmetrical fuel profile when the fuel is injected into the combustion air. Pulsations are suppressed by this asymmetrical arrangement of the fuel openings 17a and 17a and the asymmetrical fuel profile generated thereby. The type and strength of the asymmetry generated must be adapted to the special case. Burner system with few pulsations can cause a slight asymmetry of the fuel nozzle, in systems with high pulsations, the asymmetry must be increased.
Die Einstellung der Asymmetrie erfolgt entsprechend dem bei der nachfolgenden Figur 7 beschriebenen Verfahren in einer Versuchseinrichtung. Die Einstellung kann z.B. durch Ausprobieren oder mittels eines Optimierungs-Algorithmus erfolgen. Die Asymmetrie wird so eingestellt, z.B. mittels Ventilen, dass die Pulsatio- neπ minimal sind und die Schadstoffemission auf einem akzeptierbaren Niveau liegt.The asymmetry is set in a test facility in accordance with the method described in FIG. 7 below. The setting can e.g. by trying it out or by means of an optimization algorithm. The asymmetry is set in this way, e.g. by means of valves that the pulsations are minimal and the pollutant emission is at an acceptable level.
In der Fig. 6 ist auf der X-Achse der Grad der Asymmetrie und auf der Y-Acr»se der Wert der Pulsationen dargestellt. Deutlich ist erkennbar, dass mit zunehmender Asymmetrie die Pulsationen abnehmen und somit die Pulsationen und Ernis- sionen verringert werden können. Somit können durch die Änderung der Bre nn- stoffverteilung, d.h. durch eine asymmetrische Brennstoffeindüsung, die Pulsationen und Emissionen optimiert werden.6 shows the degree of asymmetry on the X-axis and the value of the pulsations on the Y-axis. It can be clearly seen that the pulsations decrease with increasing asymmetry and thus the pulsations and results can be reduced. Thus, by changing the distribution of nitrogen, i.e. through an asymmetrical fuel injection, the pulsations and emissions are optimized.
In Fig. 7 ist eine weitere erfindungsgemasse Ausführung des Doppelkegelbrenners dargestellt. Der Drallraum 14 wird durch die Teilkegelschalen 1 und 2 gebildet. Die Verbrennungsluft strömt über die Lufteintrittsschlitze 19 und 20 in den Drallraum 14. Im Bereich der Lufteintrittsschlitze 19, 20 sind Brennstofföffnungen 17a und 17b angeordnet, über die Brennstoff in die Verbrennungsluft eingedüst werden kann. Das so entstehende Brennstoff-Luft-Gemisch wird in die Brennkammer transportiert und entzündet. An jedem Lufteintrittsschlitz 19, 20 weist der Doppelkegelbrenner in diesem Beispiel jeweils acht Brennstoffeindüsungsöf nun- gen 17a und 17b auf, weiche individuell über eine Leitung mit Brennstoff versorgt werden. In jeder dieser Leitungen ist jeweils ein Ventil 31 bis 38, respektive 41 bis 48 angeordnet, wobei jedes dieser Ventile unabhängig vom anderen geregelt werden kann. Um eine Asymmetrie zu erzeugen, werden nun gegenüberliegende Brennstoffeindüsungsöffnungen 17a und 17b mittels der Ventile 31 und -41 , 32 und 42, 33 und 43, usw. so angesteuert, dass zumindest eines der acht gegenüberliegenden Paare von Brennstofföffnungen einen unterschiedlichen Brennstoffmassenstrom bezüglich der ihr gegenüberliegenden Brennstofföffnu g auf- weist und so eine asymmetrische Brennstoffzufuhr erfolgt.7 shows another embodiment of the double-cone burner according to the invention. The swirl chamber 14 is formed by the partial cone shells 1 and 2. The combustion air flows through the air inlet slots 19 and 20 into the swirl chamber 14. In the area of the air inlet slots 19, 20 there are fuel openings 17a and 17b, through which fuel can be injected into the combustion air. The resulting fuel-air mixture is transported into the combustion chamber and ignited. In this example, the double-cone burner has eight fuel injection ovens 17a and 17b at each air inlet slot 19, 20, which are individually supplied with fuel via a line. A valve 31 to 38 or respectively 41 to 48 is arranged in each of these lines, wherein each of these valves can be regulated independently of the other. In order to create an asymmetry, opposite are now Fuel injection openings 17a and 17b are controlled by means of the valves 31 and -41, 32 and 42, 33 and 43, etc., in such a way that at least one of the eight opposite pairs of fuel openings has a different fuel mass flow with respect to the fuel opening opposite them, and thus an asymmetrical one Fuel is supplied.
Über Sensoren in der Brennkammer 22 kann der Grad der Pulsationen festgestellt werden und mittels der Brennstoffeindüsungsöffnungen 17a und IT' und den zugehörigen Ventilpaaren 31 und 41 , usw. der Grad der Asymmetrie den Verhältnissen angepasst werden. Diese Steuerung der Asymmetrie kann natürlich mit einer gestuften Verbrennung entsprechend der Offenbarung der DE 100 64 893 A1 kombiniert werden, um schädliche Pulsationen noch wirkungsvoller zu unterbinden.The degree of pulsations can be determined via sensors in the combustion chamber 22 and the degree of asymmetry can be adapted to the conditions by means of the fuel injection openings 17a and IT 'and the associated valve pairs 31 and 41, etc. This asymmetry control can of course be combined with a staged combustion according to the disclosure of DE 100 64 893 A1 in order to prevent harmful pulsations even more effectively.
Die Einstellung der Asymmetrie für spezifische Anlagen erfolgt in einer Ver- Suchseinrichtung unter Zuhilfenahme von elektrisch ansteuerbaren Venti len. Di e- se werden durch eine Steuer- und Regelungseinheit, z.B. einen Computer angesteuert. Dieser Computer verarbeitet auch die gemessenen Pulsationen und Schadstoffemissionen. Mittels eines Algorithmus werden die Ventile so eingestellt, dass die Pulsationen minimiert werden und die Schadstoffemissio en unter einem definierten Niveau bleiben. Der Algorithmus kann so auch für die spezifische Anlage angepasst werden.The asymmetry for specific systems is set in a test facility with the aid of electrically controllable valves. These are controlled by a control and regulation unit, e.g. controlled a computer. This computer also processes the measured pulsations and pollutant emissions. Using an algorithm, the valves are set so that the pulsations are minimized and the pollutant emissions remain below a defined level. The algorithm can also be adapted for the specific system.
In Fig. 8 ist eine andere Bauart eines drallerzeugenden Brenners, eines soge- nannten umgekehrten Doppelkegelbrenners, dargestellt. Der Drallerzeuger wird hier aus hohlen Teilzylinderkörpem 50, 51 gebildet, welche zueinander versetzt angeordnet sind, und in deren Innenraum ein in Strömungsrichtung zusammenlaufender Kegelkörper 49 hineinragt. Durch die Eintrittsschlitze 19 und 23 tritt hier auch die Brennluft in den Drallraum 14 ein. Durch den, in den durch die Teilzylin- derkorper gebildeten Innenraum, hineinragenden Kegelkorperwird hier die in den Drallraum eintretende Brennluft ebenfalls in Rotation versetzt. Wie beim Doppel- kegelbrenner nach Fig. 7 sind hier auch im Bereich der Lufteintrittsschlitze Brenn- stofföffnungen 17a und 17b angeordnet, über die Brennstoff in die Verbrennungsluft eingedüst wird. Das so entstehende Brennstoff-Luft-Gemisch wird in die Brennkammer transportiert und entzündet. An jedem Lufteintrittsschlitz 19, 20 weist der umgekehrte Doppelkegelbrenner jeweils acht Brennstoffeindüsungsöffnungen 17a und 17b auf, welche individuell über eine Leitung mit Brennstoff versorgt werden. In jeder dieser Leitungen ist jeweils ein Ventil 31 bis 38, respektive 41 bis 48 angeordnet, wobei jedes dieser Ventile unabhängig vom anderen geregelt werden kann. Um eine Asymmetrie zu erzeugen, werden nun gegenüberlie- gende Brennstoffeindüsungsöffnungen 17a und 17b mittels der Ventile 31 und 41 , 32 und 42, 33 und 43, usw. so angesteuert, dass zumindest eines der acht gegenüberliegenden Paare von Brennstofföffnungen einen unterschiedlichen Brennstoffmassenstrom bezüglich der gegenüberliegenden Brennstofföffnung aufweist und so eine asymmetrische Brennstoffzufuhr erfolgt. Bezüglich der Steuerung der Asymmetrie gilt das Gleiche wie unter Fig. 7Another type of swirl-generating burner, a so-called inverted double-cone burner, is shown in FIG. The swirl generator is formed here from hollow partial cylinder bodies 50, 51 which are arranged offset with respect to one another and into whose interior projects a conical body 49 converging in the direction of flow. The combustion air also enters the swirl chamber 14 through the inlet slots 19 and 23. Due to the cone body protruding into the interior space formed by the partial cylinder bodies, the combustion air entering the swirl chamber is also set in rotation here. As with the double 7 are also arranged in the area of the air inlet slots, fuel openings 17a and 17b, through which fuel is injected into the combustion air. The resulting fuel-air mixture is transported into the combustion chamber and ignited. At each air inlet slot 19, 20, the inverted double-cone burner has eight fuel injection openings 17a and 17b, which are individually supplied with fuel via a line. A valve 31 to 38 or respectively 41 to 48 is arranged in each of these lines, wherein each of these valves can be regulated independently of the other. In order to create an asymmetry, opposite fuel injection openings 17a and 17b are now controlled by means of valves 31 and 41, 32 and 42, 33 and 43, etc., so that at least one of the eight opposite pairs of fuel openings has a different fuel mass flow with respect to the opposite one Has fuel opening and so an asymmetrical fuel supply takes place. With regard to the control of the asymmetry, the same applies as in FIG. 7
Selbstverständlich ist die Erfindung nicht auf das gezeigte und beschriebene Ausführungsbeispiel beschränkt. Die Ausführung nach Fig. 5 kann natürlich auch mit der Ausführung nach Fig. 7 und derjenigen nach Fig. 8 verbunden werden. Dadurch kann die aktive Regelung der Ventile minimiert werden. Natürlich kann die Zahl der Brennstofföffnungen und damit die Zahl der Ventile beliebig den Erfordernissen angepasst werden. Der Brenner kann auch andere Formen aufweisen als im Ausführungsbeispiel gezeigt und es können auch ande- re Brennertypen verwendet werden. Der gezeigte Brenner kann bezüglich derOf course, the invention is not limited to the exemplary embodiment shown and described. The embodiment according to FIG. 5 can of course also be combined with the embodiment according to FIG. 7 and that according to FIG. 8. This can minimize the active control of the valves. Of course, the number of fuel openings and thus the number of valves can be adjusted as required. The burner can also have other shapes than shown in the exemplary embodiment and other types of burners can also be used. The burner shown can with respect to
Form und der Grosse der tangentialen Lufteintritte 19, 20 beliebig variiert werden.Shape and the size of the tangential air inlets 19, 20 can be varied as desired.
Bezugszeichenliste Teilkegelkörpera zylindrischer Anfangsteilb Mittelachse Teilkegelkörper 1 Teilkegelkörpera zylindrischer Anfangsteilb Mittelachse Teilkegelkörper 2 Düse Brennstoffeindüsung Flüssigbrennstoffprofil Rückströmzone Flammenfront Brennstoffleitung Brennstoffleitung0 Abschlussplatte1 Bohrungen2 flüssiger Brennstoff3 gasförmiger Brennstoff4 Kegelhohlraum, Drallraum5 Verbrennungsluft6 Zumischung7 Öffnungen7a Öffnungen Brennstoffleitung 87b Öffnungen Brennstoffleitung 98 Kühlluft9 Lufteintrittsschlitz0 Lufteintrittsschlitz1a Leitblech1b Leitblech2 Brennkammer3 Drehpunkt Brenneraustritt Drallerzeuger-38 Ventile der Brennstoffdüsen am ersten Spalt-48 Ventile der Brennstoffdusen am zweiten Spalt Kegel körper, 51 Teiizylinderkorper LIST OF REFERENCE NUMBERS Partial cone bodya cylindrical initial partb central axis partial cone body 1 partial cone bodya cylindrical initial partb central axis partial cone body 2 nozzle fuel injection liquid fuel profile return flow zone flame front fuel line fuel line0 end plate1 holes2 liquid fuel3 gaseous fuel4 cone cavity, swirl chamber5 combustion air6 admixture7 openings7a fuel line fuel inlet slot1 Burner outlet swirl generator-38 valves of the fuel nozzles on the first gap-48 valves of the fuel nozzles on the second gap

Claims

Patentansprüche claims
1. Brenner, im wesentlichen bestehend aus einem Drallerzeuger (30) für einen Verbrennungsluftstrom (15), Mitteln (17, 17a, 17b, 31 -38, 41 -48) zur Einbringung von Brennstoff in den Verbrennungsluftstrom (15) und Luftein- trittsschlitzen (19, 20), über die der Verbrennungsluftstrom (15) in einen Drallraum (14) des Drallerzeugers (30) eintritt, dadurch gekennzeichnet, dass die Eindusung des Brennstoffes in die Verbrennungsluft über die Eindusungs-Mittel (17, 17a, 17b, 31-38, 41 -48) asymmetrisch ist.1. Burner, consisting essentially of a swirl generator (30) for a combustion air flow (15), means (17, 17a, 17b, 31 -38, 41 -48) for introducing fuel into the combustion air flow (15) and air inlet slots (19, 20), via which the combustion air flow (15) enters a swirl chamber (14) of the swirl generator (30), characterized in that the fuel is injected into the combustion air via the injection means (17, 17a, 17b, 31 -38, 41 -48) is asymmetrical.
2. Brenner nach Anspruch 1 , dadurch gekennzeichnet, dass der Drallerzeuger (30) zwei sich bezüglich der Symmetrie des Drall- erzeugers gegenüberliegende Lufteintrittsschlitze (19, 20) aufweist.2. Burner according to claim 1, characterized in that the swirl generator (30) has two air inlet slots (19, 20) opposite one another with respect to the symmetry of the swirl generator.
3. Brenner nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Eindusungs-Mittel (17, 17a, 17b, 31 -38, 41-48) zur Einbringung von Brennstoff in den Verbrennungsluftstrom (15) im Bereich der Lufteintrittsschlitze (19, 20) angeordnet sind.3. Burner according to claim 1 or 2, characterized in that the injection means (17, 17a, 17b, 31 -38, 41-48) for introducing fuel into the combustion air flow (15) in the region of the air inlet slots (19, 20th ) are arranged.
4. Brenner nach Anspruch 1 , 2 oder 3, dadurch gekennzeichnet, dass als Eindusungs-Mittel Brennstoffeindüsungsöffnungen (17a, 17b) im Bereich von sich gegenüberliegenden Lufteintrittsschlitzen (19, 20) zumin- dest teilweise asymmetrisch in Strömungsrichtung angeordnet sind, so dass eine Asymmetrie der Brennstoffeindüsungsöffnungen (17a, 17b) vorliegt.4. Burner according to claim 1, 2 or 3, characterized in that fuel injection openings (17a, 17b) in the region of opposing air inlet slots (19, 20) at least as injection means. are arranged at least partially asymmetrically in the flow direction, so that there is an asymmetry of the fuel injection openings (17a, 17b).
5. Brenner nach Anspruch 1 , 2, 3 oder 4, dadurch gekennzeichnet, dass Brennstoffeindüsungsöffnungen (17a, 17b) individuell durch Regelkörper (31-38, 41-48) mit Brennstoff versorgbar sind, dass zumindest ein Paar von sich im wesentlichen symmetrisch gegenüberliegenden Brenn- stoffeindüsungsöffnungen (17a, 17b) durch zugehörige Regelkörper (31 und 41 , 32 und 42, usw.) so angesteuert sind, dass aus einer der so angesteuerten Brennstoffeindüsungsöffnung (17a) mehr Brennstoff austritt als aus der dem Paar zugehörigen anderen Brennstoffeindüsungsöffnung (17b).5. Burner according to claim 1, 2, 3 or 4, characterized in that the fuel injection openings (17a, 17b) can be supplied with fuel individually by regulating bodies (31-38, 41-48) that at least one pair of substantially symmetrically opposite one another Fuel injection openings (17a, 17b) are controlled by associated control bodies (31 and 41, 32 and 42, etc.) in such a way that more fuel emerges from one of the fuel injection openings (17a) controlled in this way than from the other fuel injection opening (17b) associated with the pair ).
6. Brenner nach Anspruch 5, dadurch gekennzeichnet, dass in einer Brennkammer (22) stromabwärts des Drallerzeugers (30) Sensoren zur Messung von Pulsationen angeordnet sind, und dass der Grad der Asymmetrie der Brennstoffeindüsung der Paare von sich im wesentlichen symmetrisch gegenüberliegenden Brennstoffeindüsungsöffnungen (17a, 17b) entsprechend der Stärke der gemessenen Pulsationen einstellbar ist.6. Burner according to claim 5, characterized in that sensors for measuring pulsations are arranged in a combustion chamber (22) downstream of the swirl generator (30), and that the degree of asymmetry of the fuel injection of the pairs of essentially symmetrically opposed fuel injection openings (17a , 17b) can be adjusted according to the strength of the pulsations measured.
7. Brenner nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass zumindest einige der symmetrisch gegenüberliegenden Paare von Brennstoffeindüsungsöffnungen (17a, 17b) durch die zugehörigen Regelkörper (31 und 41 , 32 und 42, usw.) so angesteuert sind, das ein in Strö- mungsrichtung gestuftes Brennstoffprofil erzeugbar ist. 7. Burner according to claim 5 or 6, characterized in that at least some of the symmetrically opposite pairs of fuel injection openings (17a, 17b) are controlled by the associated regulating body (31 and 41, 32 and 42, etc.) so that a flow - Direction of stepped fuel profile can be generated.
8. Brenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es sich um einen Doppelkegelbrenner mit einem Drallerzeuger (30) aus mindestens zwei aufeinander positionierten hohlen Teilkegelkörpern C . 2) handelt, welche sich in Strömungsrichtung erweitern und zueinander versetzt angeordnet sind, so dass der Verbrennungsluftstrom über die sich so gebildeten Lufteintrittsschlitze (19, 20) in den Drallraum (14) strömt.8. Burner according to one of the preceding claims, characterized in that it is a double-cone burner with a swirl generator (30) made of at least two hollow partial cone bodies C positioned one on top of the other. 2), which expand in the direction of flow and are arranged offset to one another, so that the combustion air flow flows through the air inlet slots (19, 20) thus formed into the swirl chamber (14).
9. Brenner nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass es sich um einen umgekehrten Doppelkegelbrenner mit einem Drallerzeuger (30) aus mindestens zwei aufeinander positionierten hohlen Teil- zylinderlkörpem (50, 51) handelt, welche zueinander versetzt angeordnet sind, so dass der Verbrennungsluftstrom über die sich so gebildeten Luft- eintrittsschlitze (19, 20) in den Drallraum (14) strömt, wobei im Drallraum ein kegelförmiger, in Strömungsrichtung zusammenlaufender Kegelkörper (49) angeordnet ist. 9. Burner according to one of claims 1 to 7, characterized in that it is an inverted double-cone burner with a swirl generator (30) made of at least two hollow part-cylinder bodies (50, 51) positioned one on top of the other, which are arranged offset to one another, so that the combustion air flow flows through the air inlet slots (19, 20) thus formed into the swirl chamber (14), a conical conical body (49) converging in the flow direction being arranged in the swirl chamber.
EP05729532A 2004-03-31 2005-03-23 Burner Withdrawn EP1730447A1 (en)

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