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EP0809070A1 - Burner with exhaust gas recirculation - Google Patents

Burner with exhaust gas recirculation Download PDF

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Publication number
EP0809070A1
EP0809070A1 EP96107956A EP96107956A EP0809070A1 EP 0809070 A1 EP0809070 A1 EP 0809070A1 EP 96107956 A EP96107956 A EP 96107956A EP 96107956 A EP96107956 A EP 96107956A EP 0809070 A1 EP0809070 A1 EP 0809070A1
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EP
European Patent Office
Prior art keywords
exhaust gas
mixing channel
gas recirculation
burner
burner according
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.)
Granted
Application number
EP96107956A
Other languages
German (de)
French (fr)
Other versions
EP0809070B1 (en
Inventor
Jakob Keller
Bruno Zumstein
Ulrich Leemann
Philipp Hanimann
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Oertli Technique Thermique
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Oertli Technique Thermique
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.)
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Priority to EP96107956A priority Critical patent/EP0809070B1/en
Priority to AT96107956T priority patent/ATE204972T1/en
Priority to DE59607583T priority patent/DE59607583D1/en
Publication of EP0809070A1 publication Critical patent/EP0809070A1/en
Application granted granted Critical
Publication of EP0809070B1 publication Critical patent/EP0809070B1/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 
    • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
    • F23C9/006—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber the recirculation taking place in the combustion chamber
    • 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
    • F23D11/40—Mixing tubes; Burner heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D17/00—Burners for combustion simultaneously or alternately of gaseous or liquid or pulverulent fuel
    • F23D17/002—Burners for combustion simultaneously or alternately of gaseous or liquid or pulverulent fuel gaseous or liquid fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2202/00—Fluegas recirculation
    • F23C2202/30—Premixing fluegas with combustion air

Definitions

  • the invention relates to a burner with exhaust gas recirculation according to the preamble of claim 1.
  • Burners are known from documents EP-A-0 430 011 and EP-491 079, in which exhaust gas is returned to the primary combustion zone by means of air nozzles. In these cases, the mixing of fresh air and exhaust gas and the primary combustion take place in the same area.
  • a burner has become known from EP-A-0 394 800, which consists of partial cone bodies with tangential combustion air inlet channels, in which air and recirculated exhaust gas are mixed before the actual combustion process. After the mixing of incoming air with recirculated exhaust gas, a premixing of liquid or gaseous fuel with the previously generated exhaust gas / air mixture takes place in a conical cavity. A sufficiently high temperature of the exhaust gas / air mixture also enables the liquid fuel to be pre-evaporated. The latter property is responsible for the blue color of the flame when the burner is operating with liquid fuel.
  • the advantages of a burner with exhaust gas recirculation are that the highest possible combustion temperature, with good mixing of air and exhaust gas before combustion and with sufficient cooling of the recirculated exhaust gas, is greatly reduced. As a direct consequence of the lowering of the maximum combustion temperature, the emission of nitrogen oxides (NOx) is reduced. With good pre-evaporation and premixing, the combustion temperature also very uniform. At the same time, emissions of carbon monoxide (CO) and unburned hydrocarbons (UHC) can be kept low. Finally, soot can be avoided thanks to good pre-evaporation and premixing.
  • NOx nitrogen oxides
  • CO carbon monoxide
  • UHC unburned hydrocarbons
  • the object of the invention is to simplify and expand the design of a burner of the type mentioned at the outset in order to minimize the pollutant emissions and the need for external energy in each operation, both when operating with liquid and with gaseous fuels. According to the invention, this is achieved by the features listed in claim 1.
  • an important advantage of the invention is that particularly intimate mixing of exhaust gas and air takes place before the fuel is injected. Excellent pre-evaporation and premixing of the fuel are also achieved in this way.
  • the construction of the present invention is significantly simpler than, for example, that known from EP-A-0 394 800.
  • Another advantage of the invention is the good efficiency of the annular jet pump, which entrains exhaust gases through the fresh air flow. This efficiency can be improved even further by dividing the fresh air inlet into the mixing duct into a number of separate inlet openings. Thanks to its high jet pump efficiency and its low back pressure after the jet pump, the burner proposed here can be operated with a conventional single-stage fan. In addition, it may be possible to dispense with the start-up measures that are otherwise customary in exhaust gas recirculation burners.
  • the increased temperature of the exhaust gas / air mixture in combination with the flame stabilization in the area of the burner outlet ensures that a mixture of Fresh air, exhaust gas and pre-evaporated fuel is supplied to the combustion.
  • the optimization of the mixture achieved due to the exhaust gas recirculation also influences the flame temperature in the combustion chamber in such a way that no local temperature peaks can occur there, which would lead to increased NOx formation.
  • the premixing of the fuel avoids the occurrence of flame zones with too low a temperature, which would lead to increased CO and UHC emissions.
  • Another advantage of the invention lies in the possibility of special flame stabilization. If, after the narrowing, the outer shell widens to a suitably dimensioned diffuser, the flame front in the vortex flow generated by the jet pump cannot migrate back to the fuel injection. This not only achieves the desired premixing and pre-evaporation, it also succeeds in protecting the fuel injection from soot and overheating. This property helps to reduce the burner's susceptibility to failure.
  • the burner body consists of an essentially rotationally symmetrical outer shell 1 and an inner shell 2 arranged concentrically therewith.
  • the outer shell 1 has a striking narrowing 3 and a diffuser part 4.
  • a mixing channel 5 is delimited by a part 6 of the outer shell 1 and a part 7 of the inner shell 2, the course of the shell parts 6 and 7 being selected such that the cross-sectional area of the jet pump mixing path 5 is measured over a length measured in the main flow direction (ie parallel to the burner axis) of at least twice the radial gap width of the mixing section remains largely constant.
  • the mixing duct 5 begins immediately after the air and exhaust gas have been brought together.
  • the mixing channel 5 is preferably of cylindrical design. In certain cases, however, it is conceivable to use a conical mixing section, for example, for reasons of space.
  • a fuel nozzle 8 ensures the supply of the liquid fuel 9, a spray cone 11 being generated through a central atomizing bore 10.
  • Gaseous fuel 14 is fed to a distributor ring 13 via a feed line 12. The gaseous fuel 14 passes from the distributor ring 13 through a regular arrangement of gas injection bores 15, which are preferably radially outward are directed to the inlet of the jet pump mixing section 5. In certain burner configurations, however, axial gas injection (not shown) may be preferred for reasons of space.
  • the fresh air 16 enters the mixing chamber 5 through an annular arrangement of air bores 17, the axes of the air bores 17 in the case of a cylindrical mixing chamber 5 preferably being skewed to the burner axis A.
  • the alignment of the air bores would be chosen such that their axes run with a slight inclination in the circumferential direction and parallel to the central surface of the mixing chamber.
  • a slight adjustment of the axes of the air bores 17 in the tangential direction contributes to the generation of a vortex flow, which guarantees the flow around the inner shell 2 and stabilization of the flame 18.
  • exhaust gas is sucked into the mixing chamber 5 through an annular and regular arrangement of exhaust gas inlet openings 19.
  • Guide vanes 20 impart a swirl to the incoming exhaust gas flow 21, which together with the air swirl caused by the obliquely oriented air bores 17 generates a swirl of the exhaust gas / air mixture in and after the mixing section 5.
  • air swirl or exhaust gas swirl can be dispensed with in some cases.
  • the ideal exhaust gas recirculation rate is approximately 40% to 70%, based on the fresh air mass flow.
  • the exhaust gas recirculation rate is selected such that the adiabatic combustion temperature in the flame zone 18 is approximately 1350 degrees Celsius. This allows the NOx emissions as well as the CO and UHC emissions to be kept low.
  • the jet pump efficiency must be sufficiently high.
  • the recirculated exhaust gas 21 should the highest possible axial speed component are torn into the mixing section 5.
  • FIG. 3 shows an exemplary embodiment, the feed geometry of which enables a particularly high jet pump efficiency.
  • the constriction 3 of the outer shell should be of relatively small dimensions so that the counterpressure which the jet pump has to overcome can be kept as low as possible.
  • the recirculated exhaust gas 21 enters the mixing channel 5 without swirling, and the swirling of the gas mixture is generated either by the fresh air flow or by guide vanes (not shown) in the mixing channel.
  • the cross-sectional area of all air bores 17 should preferably be approximately 10% to 20% of the cross-sectional area of the mixing chamber 5. All burner parts, which are located on the right side of the boiler wall 22 and thus inside the boiler, are naturally exposed to a high thermal load.
  • FIG. 1 shows a further possibility in which part of the fresh air is led through a deflection duct into the part of the mixing duct lying downstream and thereby cools the inner contour .
  • the embodiment variant shown in FIG. 1 shows a further possibility in which part of the fresh air is led through a deflection duct into the part of the mixing duct lying downstream and thereby cools the inner contour .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)

Abstract

The recirculated exhaust gases are mixed with the fresh air (16) in a mixing channel (5) formed as a ring-shaped jet pump with a device for causing the gas mixture to twist round the burner axis as it moves in a main flow direction parallel to the burner axis. The mixing channel is defined by two conical shells with the inner shell ending in the main flow direction in front of a restriction (3) in the outer shell. The outer shell widens out after the restriction to a diffusor. Several openings are provided for the fresh air to enter the mixing channel in order to form several individual separate suction jet pumps to recirculate the exhaust gases.

Description

Technisches GebietTechnical field

Die Erfindung betrifft einen Brenner mit Abgasrückführung gemäss Oberbegriff des Anspruchs 1.The invention relates to a burner with exhaust gas recirculation according to the preamble of claim 1.

Stand der TechnikState of the art

Aus den Schriften EP-A-0 430 011 und EP-491 079 sind Brenner bekannt, in welchen mittels Luftdüsen Abgas in die primäre Verbrennungszone zurückgeführt wird. In diesen Fällen finden die Vermischung von Frischluft und Abgas und die Primärverbrennung im gleichen Bereich statt. Ausserdem ist aus EP-A-0 394 800 ein Brenner bekannt geworden, der aus Teilkegelkörpern mit tangentialen Verbrennungslufteintrittskanälen besteht, in welchen Luft und rückgeführtes Abgas vor dem eigentlichen Verbrennungsprozess vermischt werden. Nach der Vermischung von eintretender Luft mit rückgeführtem Abgas findet in einem kegeligen Hohlraum eine Vormischung von flüssigem oder gasförmigem Brennstoff mit dem zuvor erzeugten Abgas-Luftgemisch statt. Eine ausreichend hohe Temperatur des Abgas-Luftgemisches ermöglicht zudem eine Vorverdampfung des flüssigen Brennstoffes. Die letztgenannte Eigenschaft ist für die blaue Farbe der Flamme im Betrieb des Brenners mit flüssigem Brennstoff verantwortlich.Burners are known from documents EP-A-0 430 011 and EP-491 079, in which exhaust gas is returned to the primary combustion zone by means of air nozzles. In these cases, the mixing of fresh air and exhaust gas and the primary combustion take place in the same area. In addition, a burner has become known from EP-A-0 394 800, which consists of partial cone bodies with tangential combustion air inlet channels, in which air and recirculated exhaust gas are mixed before the actual combustion process. After the mixing of incoming air with recirculated exhaust gas, a premixing of liquid or gaseous fuel with the previously generated exhaust gas / air mixture takes place in a conical cavity. A sufficiently high temperature of the exhaust gas / air mixture also enables the liquid fuel to be pre-evaporated. The latter property is responsible for the blue color of the flame when the burner is operating with liquid fuel.

Die Vorzüge eines Brenners mit Abgasrückführung bestehen darin, dass die grösstmögliche Verbrennungstemperatur, bei guter Vermischung von Luft und Abgas vor der Verbrennung und bei ausreichender Kühlung des rückgeführten Abgases, stark abgesenkt wird. Als direkte Folge der Absenkung der maximalen Verbrennungstemperatur wird die Emission der Stickoxide (NOx) abgesenkt. Bei guter Vorverdampfung und Vormischung wird die Verbrennungstemperatur ausserdem sehr gleichförmig. Damit können gleichzeitig auch die Emissionen von Kohlenmonoxid (CO) und unverbrannten Kohlenwasserstoffen (UHC) gering gehalten werden. Schliesslich kann dank guter Vorverdampfung und Vormischung die Entstehung von Russ vermieden werden.The advantages of a burner with exhaust gas recirculation are that the highest possible combustion temperature, with good mixing of air and exhaust gas before combustion and with sufficient cooling of the recirculated exhaust gas, is greatly reduced. As a direct consequence of the lowering of the maximum combustion temperature, the emission of nitrogen oxides (NOx) is reduced. With good pre-evaporation and premixing, the combustion temperature also very uniform. At the same time, emissions of carbon monoxide (CO) and unburned hydrocarbons (UHC) can be kept low. Finally, soot can be avoided thanks to good pre-evaporation and premixing.

Der Erfindung liegt die Aufgabe zugrunde, einen Brenner der eingangs genannten Art konstruktiv zu vereinfachen und zu erweitern, um die Schadstoffemissionen und den Bedarf an Fremdenergie bei jedem Betrieb zu minimieren, dies sowohl bei einem Betrieb mit flüssigen als auch mit gasförmigen Brennstoffen. Erfindungsgemäss wird dies durch die im Anspruch 1 aufgezählten Merkmale erreicht.The object of the invention is to simplify and expand the design of a burner of the type mentioned at the outset in order to minimize the pollutant emissions and the need for external energy in each operation, both when operating with liquid and with gaseous fuels. According to the invention, this is achieved by the features listed in claim 1.

Gegenüber den eingangs erwähnten, vorbekannten Brennern ist ein wesentlicher Vorteil der Erfindung darin zu sehen, dass eine besonders innige Vermischung von Abgas und Luft schon vor der Brennstoffeindüsung stattfindet. Damit werden auch eine ausgezeichnete Vorverdampfung und Vormischung des Brennstoffs erreicht. Ausserdem ist die Konstruktion der vorliegenden Erfindung entscheidend einfacher als beispielsweise die aus EP-A-0 394 800 bekannte. Ein weiterer Vorteil der Erfindung liegt im guten Wirkungsgrad der ringförmigen Strahlpumpe, welche Abgase durch den Frischluftstrom mitreisst. Man kann diesen Wirkungsgrad noch verbessern, indem man den Frischlufteintritt in den Mischkanal in eine Anzahl getrennter Einlassöffnungen aufteilt. Dank seinem hohen Strahlpumpenwirkungsgrad und seinem niedrigen Gegendruck nach der Strahlpumpe kann der hier vorgeschlagene Brenner mit einem herkömmlichen einstufigen Gebläse betrieben werden. Ausserdem kann gegebenenfalls auf die sonst bei Abgasrückführbrennern üblichen Starthilfemassnahmen verzichtet werden.Compared to the previously known burners mentioned at the outset, an important advantage of the invention is that particularly intimate mixing of exhaust gas and air takes place before the fuel is injected. Excellent pre-evaporation and premixing of the fuel are also achieved in this way. In addition, the construction of the present invention is significantly simpler than, for example, that known from EP-A-0 394 800. Another advantage of the invention is the good efficiency of the annular jet pump, which entrains exhaust gases through the fresh air flow. This efficiency can be improved even further by dividing the fresh air inlet into the mixing duct into a number of separate inlet openings. Thanks to its high jet pump efficiency and its low back pressure after the jet pump, the burner proposed here can be operated with a conventional single-stage fan. In addition, it may be possible to dispense with the start-up measures that are otherwise customary in exhaust gas recirculation burners.

Wird der Brenner mit flüssigem Brennstoff betrieben, so sorgt die erhöhte Temperatur des Abgas-Luftgemisches in Kombination mit der Flammstabilisierung im Bereich des Brenneraustrittes dafür, dass ein Gemisch von Frischluft, Abgas und vorverdampftem Brennstoff der Verbrennung zugeführt wird. Die aufgrund der Abgasrückführung erreichte Optimierung des Gemisches beeinflusst auch die Flammentemperatur im Brennraum in der Weise, dass dort keine lokalen Temperaturspitzen auftreten können, welche zu erhöhter NOx-Bildung führen würden. Anderseits vermeidet die Vormischung des Brennstoffs das Auftreten von Flammzonen mit zu niedriger Temperatur, die zu erhöhter CO- und UHC-Emission führen würden. Obwohl beim Betrieb mit gasförmigem Brennstoff keine Vorverdampfung erforderlich ist, kommen dabei ansonsten die gleichen Vorteile zum Tragen wie beim Betrieb mit flüssigem Brennstoff.If the burner is operated with liquid fuel, the increased temperature of the exhaust gas / air mixture in combination with the flame stabilization in the area of the burner outlet ensures that a mixture of Fresh air, exhaust gas and pre-evaporated fuel is supplied to the combustion. The optimization of the mixture achieved due to the exhaust gas recirculation also influences the flame temperature in the combustion chamber in such a way that no local temperature peaks can occur there, which would lead to increased NOx formation. On the other hand, the premixing of the fuel avoids the occurrence of flame zones with too low a temperature, which would lead to increased CO and UHC emissions. Although no pre-evaporation is required when operating with gaseous fuel, the same advantages apply as when operating with liquid fuel.

Ein weiterer Vorteil der Erfindung liegt in der Möglichkeit einer besonderen Flammstabilisierung. Wenn sich nämlich die Aussenschale nach der Verengung zu einem passend dimensionierten Diffusor verbreitert, kann die Flammenfront in der von der Strahlpumpe erzeugten Wirbelströmung nicht bis zur Brennstoffeindüsung zurückwandern. Damit wird nicht nur die gewünschte Vormischung und Vorverdampfung erreicht, sondern es gelingt auch, die Brennstoffeindüsung vor Verrussung und Überhitzung zu schützen. Diese Eigenschaft trägt dazu bei, die Störanfälligkeit des Brenners zu vermindern.Another advantage of the invention lies in the possibility of special flame stabilization. If, after the narrowing, the outer shell widens to a suitably dimensioned diffuser, the flame front in the vortex flow generated by the jet pump cannot migrate back to the fuel injection. This not only achieves the desired premixing and pre-evaporation, it also succeeds in protecting the fuel injection from soot and overheating. This property helps to reduce the burner's susceptibility to failure.

Vorteilhafte und zweckmässige Weiterbildungen der erfindungsgemässen Aufgabenlösung sind in den weiteren abhängigen Ansprüchen gekennzeichnet. Im folgenden werden anhand der Zeichnungen drei Ausführungsbeispiele der Erfindung erläutert. Alle für das unmittelbare Verständnis der Erfindung nicht erforderlichen Elemente sind fortgelassen. Die Strömungsrichtung der verschiedenen Medien sind mit Pfeilen angegeben. In den verschiedenen Figuren sind jeweils gleiche Elemente mit den gleichen Bezugszeichen versehen.Advantageous and expedient developments of the task solution according to the invention are characterized in the further dependent claims. Three exemplary embodiments of the invention are explained below with reference to the drawings. All elements not necessary for the immediate understanding of the invention have been omitted. The direction of flow of the different media is indicated by arrows. In the different figures, the same elements are provided with the same reference symbols.

Es zeigt:

  • Fig. 1 eine schematische Darstellung einer ersten Ausführungsvariante des kompletten Brenners,
  • Fig. 2 ein Bild des zur Brennerachse senkrecht verlaufenden Schnittes der ersten Ausführungsvariante am Ende der Lufteintrittsbohrungen,
  • Fig. 3 eine schematische Darstellung einer zweiten Ausführungsvariante des kompletten Brenners, und
  • Fig. 4 eine schematische Darstellung einer dritten Ausführungsvariante des kompletten Brenners.
It shows:
  • 1 is a schematic representation of a first embodiment of the complete burner,
  • 2 shows an image of the section of the first embodiment variant running perpendicular to the burner axis at the end of the air inlet bores,
  • Fig. 3 is a schematic representation of a second embodiment of the complete burner, and
  • Fig. 4 is a schematic representation of a third embodiment of the complete burner.

Mögliche Ausführungsbeispiele sind in den Figuren 1, 2, 3 und 4 schematisch dargestellt. Wie die Figuren 1, 3 und 4 verdeutlichen, besteht der Brennerkörper aus einer im wesentlichen rotationssymmetrischen Aussenschale 1 und einer konzentrisch dazu angeordneten Innenschale 2. Die Aussenschale 1 weist eine markante Verengung 3 und ein Diffusorteil 4 auf. Ein Mischkanal 5 wird von einem Teil 6 der Aussenschale 1 und einem Teil 7 der Innenschale 2 begrenzt, wobei der Verlauf der Schalenteile 6 und 7 so gewählt ist, dass die Querschnittsfläche der Strahlpumpenmischstrecke 5 über eine in Hauptströmungsrichtung (d.h. parallel zur Brennerachse) gemessenen Länge von wenigstens zwei mal die radiale Spaltbreite der Mischstrecke weitgehend konstant bleibt. Dabei beginnt der Mischkanal 5 unmittelbar nach der Zusammenführung von Luft und Abgas. Wie in den Ausführungsbeispielen in Fig. 1, Fig. 3 und Fig. 4 gezeigt ist, wird der Mischkanal 5 vorzugsweise zylindrisch ausgeführt. Es ist jedoch denkbar in bestimmten Fällen aus Platzgründen eine z.B. kegelförmige Mischstrecke zu bevorzugen. Eine Brennstoffdüse 8 sorgt für die Zufuhr des flüssigen Brennstoffes 9, wobei ein Sprühkegel 11 durch eine zentrale Zerstäuberbohrung 10 erzeugt wird. Über eine Zuleitung 12 wird einem Verteilerring 13 gasförmiger Brennstoff 14 zugeführt. Aus dem Verteilerring 13 gelangt der gasförmige Brennstoff 14 durch eine regelmässige Anordnung von Gaseindüsungsbohrungen 15, die vorzugsweise radial nach aussen gerichtet sind, zum Eintritt der Strahlpumpenmischstrecke 5. Bei bestimmten Brennerkonfigurationen kann jedoch aus Platzgründen eine (nicht gezeigte) axiale Gaseindüsung bevorzugt werden. Die Frischluft 16 tritt durch eine ringförmige Anordnung von Luftbohrungen 17 in den Mischraum 5 ein, wobei die Achsen der Luftbohrungen 17 im Falle eines zylindrischen Mischraumes 5 vorzugsweise windschief zur Brennerachse A liegen sollten. Im Falle eines nicht-zylindrischen Mischraumes 5 würde die Ausrichtung der Luftbohrungen dergestalt gewählt, dass ihre Achsen mit einer leichten Anstellung in Umfangsrichtung und parallel zur Mittelfläche der Mischkammer verlaufen. Eine leichte Anstellung der Achsen der Luftbohrungen 17 in tangentialer Richtung trägt zur Erzeugung einer Wirbelströmung bei, welche die Umströmung der Innenschale 2 und Stabilisierung der Flamme 18 garantiert. Abgas wird im Falle des in Fig. 1 dargestellten Ausführungsbeispiels durch eine ringförmige und regelmässige Anordnung von Abgaseintrittsöffnungen 19 in den Mischraum 5 eingesaugt. Leitschaufeln 20 erteilen der eintretenden Abgasströmung 21 einen Drall, welcher zusammen mit der von den schräg orientierten Luftbohrungen 17 verursachten Luftverdrallung einen Drall des Abgas-Luftgemisches in und nach der Mischstrecke 5 erzeugt. Es kann jedoch fallweise entweder auf die Luftverdrallung oder auf die Abgasverdrallung verzichtet werden. Je nach Temperatur des angesaugten Abgases 21 beträgt die ideale Abgasrückführrate etwa 40% bis 70%, bezogen auf den Frischluftmassenstrom. Die Abgasrückführrate wird so gewählt, dass die adiabate Verbrennungstemperatur in der Flammenzone 18 bei etwa 1350 Grad Celsius liegt. Damit können sowohl die NOx-Emissionen als auch die CO- und UHC-Emissionen klein gehalten werden. Bei hohen Temperaturen des rückgeführten Abgases 21, und entsprechend hohen Abgasrückführraten, muss der Strahlpumpenwirkungsgrad ausreichend gross sein. Zu diesem Zweck sollte das rückgeführte Abgas 21 mit einer möglichst hohen axialen Geschwindigkeitskomponente in die Mischstrecke 5 gerissen werden.Possible exemplary embodiments are shown schematically in FIGS. 1, 2, 3 and 4. As illustrated in FIGS. 1, 3 and 4, the burner body consists of an essentially rotationally symmetrical outer shell 1 and an inner shell 2 arranged concentrically therewith. The outer shell 1 has a striking narrowing 3 and a diffuser part 4. A mixing channel 5 is delimited by a part 6 of the outer shell 1 and a part 7 of the inner shell 2, the course of the shell parts 6 and 7 being selected such that the cross-sectional area of the jet pump mixing path 5 is measured over a length measured in the main flow direction (ie parallel to the burner axis) of at least twice the radial gap width of the mixing section remains largely constant. The mixing duct 5 begins immediately after the air and exhaust gas have been brought together. As shown in the exemplary embodiments in FIGS. 1, 3 and 4, the mixing channel 5 is preferably of cylindrical design. In certain cases, however, it is conceivable to use a conical mixing section, for example, for reasons of space. A fuel nozzle 8 ensures the supply of the liquid fuel 9, a spray cone 11 being generated through a central atomizing bore 10. Gaseous fuel 14 is fed to a distributor ring 13 via a feed line 12. The gaseous fuel 14 passes from the distributor ring 13 through a regular arrangement of gas injection bores 15, which are preferably radially outward are directed to the inlet of the jet pump mixing section 5. In certain burner configurations, however, axial gas injection (not shown) may be preferred for reasons of space. The fresh air 16 enters the mixing chamber 5 through an annular arrangement of air bores 17, the axes of the air bores 17 in the case of a cylindrical mixing chamber 5 preferably being skewed to the burner axis A. In the case of a non-cylindrical mixing space 5, the alignment of the air bores would be chosen such that their axes run with a slight inclination in the circumferential direction and parallel to the central surface of the mixing chamber. A slight adjustment of the axes of the air bores 17 in the tangential direction contributes to the generation of a vortex flow, which guarantees the flow around the inner shell 2 and stabilization of the flame 18. In the case of the exemplary embodiment shown in FIG. 1, exhaust gas is sucked into the mixing chamber 5 through an annular and regular arrangement of exhaust gas inlet openings 19. Guide vanes 20 impart a swirl to the incoming exhaust gas flow 21, which together with the air swirl caused by the obliquely oriented air bores 17 generates a swirl of the exhaust gas / air mixture in and after the mixing section 5. However, either air swirl or exhaust gas swirl can be dispensed with in some cases. Depending on the temperature of the intake exhaust gas 21, the ideal exhaust gas recirculation rate is approximately 40% to 70%, based on the fresh air mass flow. The exhaust gas recirculation rate is selected such that the adiabatic combustion temperature in the flame zone 18 is approximately 1350 degrees Celsius. This allows the NOx emissions as well as the CO and UHC emissions to be kept low. At high temperatures of the recirculated exhaust gas 21 and correspondingly high exhaust gas recirculation rates, the jet pump efficiency must be sufficiently high. For this purpose, the recirculated exhaust gas 21 should the highest possible axial speed component are torn into the mixing section 5.

Zu diesem Zweck zeigt Figur 3 ein Ausführungsbeispiel, dessen Zuführungs-Geometrie einen besonders hohen Strahlpumpenwirkungsgrad ermöglicht. In diesem Fall sollte die Verengung 3 der Aussenschale relativ klein bemessen sein, damit der Gegendruck, den die Strahlpumpe überwinden muss, möglichst gering gehalten werden kann. In dieser Ausführung tritt das rückgeführte Abgas 21 unverdrallt in den Mischkanal 5 ein, und die Verdrallung des Gasgemisches wird entweder durch den Frischluftstrom oder durch (nicht gezeigte) Leitschaufeln im Mischkanal erzeugt. Die Querschnittsfläche aller Luftbohrungen 17 sollte vorzugsweise etwa 10% bis 20% der Querschnittsfläche des Mischraumes 5 betragen. Alle Brennerteile, die sich auf der rechten Seite der Kesselwand 22 und damit im Innern des Kessels befinden, sind naturgemäss einer hohen thermischen Belastung ausgesetzt. Im Falle der Flüssigbrennstoffdüse 8 können übermässig hohe Temperaturen, insbesonders nach der Abschaltung des Brenners, zu Brennstoffverkokungsproblemen führen. Zum thermischen Schutz der Brennstoffdüse 8 weisen die in der Figur 1 gezeigten Ausführungsbeispiele daher einen luftdurchströmten Abschirmring 23 auf. Der ebenfalls luftdurchströmte Spülring 24 erzeugt zusammen mit dem Abschirmring einen Luftschleier, der die Brennstoffdüse 8 gegen rückströmenden Brennstoff und heisse Gase abschirmt. Ausserdem sorgt dieser Luftschleier beim Start des Brenners für ideale Zündbedingungen in unmittelbarer Nähe der Zerstäuberbohrung 10. In Figur 3 ist eine weitere Möglichkeit aufgezeigt, in welcher durch einen Umlenkkanal ein Teil der Frischluft in den stromwärts liegenden Teil des Mischkanals geführt wird und dadurch die Innenkontur kühlt. Die in Fig. 4 dargestellte Ausführungsvariante zeigt eine weitere Möglichkeit der thermischen Abschirmung der Brennstoffdüse 8. Anstatt des Abschirmkanales 23 ist hier zur Kühlung die gesamte Innenschale 2 mit Effusions-Kühlbohrungen 25 versehen. Damit können sowohl die Innenschale 2 als auch die Brennstoffdüse 8 auf niedriger Temperatur gehalten werden.For this purpose, FIG. 3 shows an exemplary embodiment, the feed geometry of which enables a particularly high jet pump efficiency. In this case, the constriction 3 of the outer shell should be of relatively small dimensions so that the counterpressure which the jet pump has to overcome can be kept as low as possible. In this embodiment, the recirculated exhaust gas 21 enters the mixing channel 5 without swirling, and the swirling of the gas mixture is generated either by the fresh air flow or by guide vanes (not shown) in the mixing channel. The cross-sectional area of all air bores 17 should preferably be approximately 10% to 20% of the cross-sectional area of the mixing chamber 5. All burner parts, which are located on the right side of the boiler wall 22 and thus inside the boiler, are naturally exposed to a high thermal load. In the case of the liquid fuel nozzle 8, excessively high temperatures, especially after the burner has been switched off, can lead to fuel coking problems. For thermal protection of the fuel nozzle 8, the exemplary embodiments shown in FIG. 1 therefore have a shielding ring 23 through which air flows. The flushing ring 24, through which air flows, together with the shielding ring, creates an air curtain which shields the fuel nozzle 8 against backflowing fuel and hot gases. In addition, this air curtain ensures ideal ignition conditions in the immediate vicinity of the atomizer bore 10 when the burner is started. FIG. 3 shows a further possibility in which part of the fresh air is led through a deflection duct into the part of the mixing duct lying downstream and thereby cools the inner contour . The embodiment variant shown in FIG. 4 shows a further possibility of thermal shielding of the fuel nozzle 8. Instead of the shielding channel 23, the entire inner shell 2 is provided here for cooling Effusion cooling holes 25 are provided. This allows both the inner shell 2 and the fuel nozzle 8 to be kept at a low temperature.

Claims (10)

Abgasrückführbrenner für Heissgaserzeugung, mit Zuleitungen für flüssige und/oder gasförmige Brennstoffe, und mit einem durch zwei konzentrische und zur Brennerachse rotationssymmetrische Schalen begrenzten Mischkanal für das Vermischen von rückgeführten Abgasen mit Frischluft, dadurch gekennzeichnet, dass der Mischkanal als ringförmige Strahlpumpe ausgebildet ist und Mittel aufweist, um dem sich in einer zur Brennerachse parallelen Hauptströmungsrichtung bewegenden Gasgemisch einen Drall um die Brennerachse zu erteilen, und dass die Innenschale in Hauptströmungsrichtung vor einer Verengung der Aussenschale endet.Exhaust gas recirculation burner for hot gas generation, with feed lines for liquid and / or gaseous fuels, and with a mixing channel delimited by two concentric shells and rotationally symmetrical to the burner axis for mixing recirculated exhaust gases with fresh air, characterized in that the mixing channel is designed as an annular jet pump and has means to impart a swirl around the burner axis to the gas mixture moving in a main flow direction parallel to the burner axis, and for the inner shell to end in the main flow direction before the outer shell narrows. Abgasrückführbrenner nach Anspruch 1, dadurch gekennzeichnet, dass sich die Aussenschale nach der Verengung zu einem Diffusor verbreitert.Exhaust gas recirculation burner according to claim 1, characterized in that the outer shell widens to a diffuser after the narrowing. Abgasrückführbrenner nach Anspruch 1 oder 2, gekennzeichnet durch mehrere Oeffnungen für den Eintritt von Frischluft in den Mischkanal, die ausgebildet sind, um mehrere einzelne getrennte Saugstrahlpumpen für die Rückführung der Abgase zu bilden.Exhaust gas recirculation burner according to claim 1 or 2, characterized by a plurality of openings for the entry of fresh air into the mixing channel, which are designed to form a plurality of individual, separate suction jet pumps for the recirculation of the exhaust gases. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass der Mischkanal eine Länge von mindestens zwei mal seine mittlere Ringspaltbreite aufweist.Exhaust gas recirculation burner according to one of the preceding claims, characterized in that the mixing channel has a length of at least twice its average annular gap width. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass der Mischkanal einen im wesentlichen konstanten Strömungs-Querschnitt aufweist.Exhaust gas recirculation burner according to one of the preceding claims, characterized in that the mixing channel has a substantially constant flow cross section. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Eintrittsöffnungen für Frischluft in den Mischkanal Mittel aufweisen, um der Strömung im Mischkanal einen Drall zu erteilen.Exhaust gas recirculation burner according to one of the preceding claims, characterized in that the inlet openings for fresh air into the mixing channel have means for imparting a swirl to the flow in the mixing channel. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, dass die Eintrittsöffnungen für Abgase in den Mischkanal Mittel aufweisen, um der Strömung im Mischkanal einen Drall zu erteilen.Exhaust gas recirculation burner according to one of the preceding claims, characterized in that the inlet openings for exhaust gases into the mixing channel have means for imparting a swirl to the flow in the mixing channel. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, gekennzeichnet durch eine oder mehrere in Hauptströmungsrichtung nach dem Mischkanal angeordnete Zerstäuberdüsen für flüssigen Brennstoff.Exhaust gas recirculation burner according to one of the preceding claims, characterized by one or more atomizer nozzles for liquid fuel arranged downstream of the mixing channel in the main flow direction. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, gekennzeichnet durch eine Zuführleitung die vorgesehen ist, um durch eine Anzahl ringförmig angeordneter Bohrungen gasförmigen Brennstoff in den Mischkanal einzubringen.Exhaust gas recirculation burner according to one of the preceding claims, characterized by a feed line which is provided in order to introduce gaseous fuel into the mixing channel through a number of annularly arranged bores. Abgasrückführbrenner nach einem der vorangehenden Ansprüche, gekennzeichnet durch eine einstellbare Drossel, um den in den Mischkanal einfliessenden Abgasstrom in Abhängigkeit der Feuerraumgeometrie und/oder des Betriebszustandes des Brenners zu steuern.Exhaust gas recirculation burner according to one of the preceding claims, characterized by an adjustable throttle in order to control the exhaust gas flow flowing into the mixing channel depending on the combustion chamber geometry and / or the operating state of the burner.
EP96107956A 1996-05-19 1996-05-19 Burner with exhaust gas recirculation Expired - Lifetime EP0809070B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP96107956A EP0809070B1 (en) 1996-05-19 1996-05-19 Burner with exhaust gas recirculation
AT96107956T ATE204972T1 (en) 1996-05-19 1996-05-19 BURNER WITH EXHAUST GAS RECIRCULATION
DE59607583T DE59607583D1 (en) 1996-05-19 1996-05-19 Burner with exhaust gas recirculation

Applications Claiming Priority (1)

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EP96107956A EP0809070B1 (en) 1996-05-19 1996-05-19 Burner with exhaust gas recirculation

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EP0809070A1 true EP0809070A1 (en) 1997-11-26
EP0809070B1 EP0809070B1 (en) 2001-08-29

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AT (1) ATE204972T1 (en)
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Cited By (5)

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KR100478085B1 (en) * 1999-12-22 2005-03-24 주식회사 포스코 Gas burner with oxygen supply
WO2008049757A1 (en) * 2006-10-23 2008-05-02 Robert Bosch Gmbh Mixture formation device for mixing a first gas, a second gas and a fluid, especially a combustible fluid, preferably for generating a synthesis gas for a motor vehicle
DE102012110506A1 (en) * 2012-11-02 2014-05-08 Webasto SE High-pressure atomization burner assembly for mobile heater, has high-pressure atomizing nozzle for atomizing liquid fuel and guiding fuel to combustion chamber, where heat shield shields high-pressure atomizing nozzle
DE102016001893A1 (en) * 2016-02-17 2017-08-17 Eisenmann Se Burner unit and device for tempering objects
CN115127101A (en) * 2021-03-26 2022-09-30 北京航空航天大学 Burner for low calorific value waste gas fuel

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11187408B2 (en) 2019-04-25 2021-11-30 Fives North American Combustion, Inc. Apparatus and method for variable mode mixing of combustion reactants

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DE8909288U1 (en) * 1989-07-14 1989-11-30 Electro-Oil GmbH, 2057 Reinbek Combustion plant with a device for recirculating combustion products
EP0348646A2 (en) * 1988-06-30 1990-01-03 Deutsche Babcock Energie- Und Umwelttechnik Aktiengesellschaft Burner
EP0386732A2 (en) * 1989-03-10 1990-09-12 Oertli Wärmetechnik Ag Combustion apparatus for dual fuel burner
EP0483520A2 (en) * 1990-10-02 1992-05-06 VAW Aluminium AG Method and apparatus for the combustion of gaseous and liquid fuels generating a low emission of noxious products
DE9213737U1 (en) * 1992-10-12 1992-12-10 MEKU Metallverarbeitungs-GmbH, 7735 Dauchingen Device for mounting a burner on a boiler
DE4238529A1 (en) * 1992-11-14 1994-05-19 Deutsche Forsch Luft Raumfahrt Burner for hot gas prodn. - has burner tube with heat feed reducing component between flame and support tubes, component connecting fuel jet direction to diaphragm and having insulation ring

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EP0348646A2 (en) * 1988-06-30 1990-01-03 Deutsche Babcock Energie- Und Umwelttechnik Aktiengesellschaft Burner
EP0386732A2 (en) * 1989-03-10 1990-09-12 Oertli Wärmetechnik Ag Combustion apparatus for dual fuel burner
DE8909288U1 (en) * 1989-07-14 1989-11-30 Electro-Oil GmbH, 2057 Reinbek Combustion plant with a device for recirculating combustion products
EP0483520A2 (en) * 1990-10-02 1992-05-06 VAW Aluminium AG Method and apparatus for the combustion of gaseous and liquid fuels generating a low emission of noxious products
DE9213737U1 (en) * 1992-10-12 1992-12-10 MEKU Metallverarbeitungs-GmbH, 7735 Dauchingen Device for mounting a burner on a boiler
DE4238529A1 (en) * 1992-11-14 1994-05-19 Deutsche Forsch Luft Raumfahrt Burner for hot gas prodn. - has burner tube with heat feed reducing component between flame and support tubes, component connecting fuel jet direction to diaphragm and having insulation ring

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100478085B1 (en) * 1999-12-22 2005-03-24 주식회사 포스코 Gas burner with oxygen supply
WO2008049757A1 (en) * 2006-10-23 2008-05-02 Robert Bosch Gmbh Mixture formation device for mixing a first gas, a second gas and a fluid, especially a combustible fluid, preferably for generating a synthesis gas for a motor vehicle
DE102012110506A1 (en) * 2012-11-02 2014-05-08 Webasto SE High-pressure atomization burner assembly for mobile heater, has high-pressure atomizing nozzle for atomizing liquid fuel and guiding fuel to combustion chamber, where heat shield shields high-pressure atomizing nozzle
DE102012110506B4 (en) * 2012-11-02 2017-04-27 Webasto SE Hochdruckzerstäubungsbrenneranordnung
DE102016001893A1 (en) * 2016-02-17 2017-08-17 Eisenmann Se Burner unit and device for tempering objects
US10928134B2 (en) 2016-02-17 2021-02-23 Eisenmann Se Burner unit and device for the temperature control of objects
CN115127101A (en) * 2021-03-26 2022-09-30 北京航空航天大学 Burner for low calorific value waste gas fuel
CN115127101B (en) * 2021-03-26 2025-07-29 北京航空航天大学 Burner for low heating value exhaust gas fuel

Also Published As

Publication number Publication date
EP0809070B1 (en) 2001-08-29
DE59607583D1 (en) 2001-10-04
ATE204972T1 (en) 2001-09-15

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