EP0021035B1 - Operating process for premix burners and burner for carrying out the process - Google Patents

Operating process for premix burners and burner for carrying out the process Download PDF

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Publication number
EP0021035B1
EP0021035B1 EP80102799A EP80102799A EP0021035B1 EP 0021035 B1 EP0021035 B1 EP 0021035B1 EP 80102799 A EP80102799 A EP 80102799A EP 80102799 A EP80102799 A EP 80102799A EP 0021035 B1 EP0021035 B1 EP 0021035B1
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EP
European Patent Office
Prior art keywords
burner
flame
combustion
air
guard
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EP80102799A
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German (de)
French (fr)
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EP0021035A1 (en
Inventor
Detlef Dr.-Ing. Altemark
Hans Dipl.-Ing. Sommers
Manfred Weid
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EON Ruhrgas AG
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Ruhrgas AG
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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 
    • F23C3/00—Combustion apparatus characterised by the shape of the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/26—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid with provision for a retention flame
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • F23D14/64—Mixing devices; Mixing tubes with injectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L7/00—Supplying non-combustible liquids or gases, other than air, to the fire, e.g. oxygen, steam
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
    • F23M9/06—Baffles or deflectors for air or combustion products; Flame shields in fire-boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M2900/00—Special features of, or arrangements for combustion chambers
    • F23M2900/09062—Tube-shaped baffles confining the flame

Definitions

  • the invention relates to a method for operating premix burners under normal or increased pressure with gaseous fuels, or with fuels which are liquid at normal temperature and completely vaporized before combustion, at low combustion temperatures with formation of low-emission gases, and a burner for carrying out the method.
  • the nitrogen oxides NO and NO z ' are formed as pollutants in the exhaust gas. These pollutants contaminate the air and can have a negative effect on the material in the furnace or in contact with the burner exhaust gases in some furnaces. Therefore, efforts are made to keep the NO x content in the exhaust gas as low as possible.
  • the causes of the NO x formation are known, and several measures for reducing the NO x content in the exhaust gas are also known, for example
  • the object of the invention is to provide a method for operating premix burners with which gaseous and / or vaporous fuels can be burned at normal or elevated pressure so that on the one hand complete combustion at low combustion temperatures with the formation of exhaust gases with extremely low NO x - Held takes place, but on the other hand a high burner output is achieved and reliable combustion burning over a large output range is achieved, as well as creating a burner specially designed and suitable for carrying out this method.
  • this object is achieved by the measures mentioned in claims 1 to 9.
  • a large amount of cooling gas is therefore used to reduce the NO x formation, in particular at high specific burner outputs, at which the NO x formation and tendency towards NO x emission usually increases with the exhaust gases .
  • the reduction in flame speed caused by the use of the cooling gas nevertheless permits stable combustion, because of the simultaneous application of the special flame design during the combustion of the mixture and because of the shielding of the flame until it is completely burned out.
  • the mixture in front of the burner plate is accelerated by the narrowing mixing chamber, which is also too short for homogeneous mixing, and if the air ratio were also increased and the air ratios previously allowed for conventional premixing burners were increased, the mixture speeds would become too large to allow the flame to be held when the flame speed decreases at the same time as the air ratio increases, in particular since the known burner does not have a correspondingly adapted flame design for the possibility of preventing the flame from tearing off the burner plate when the air ratio is increased and has no means of effectively shielding the flame.
  • the lack of effective flame shielding in the known burner also helps to make the combustion taking place incomplete, which leads to the combustion products in the furnace chamber following the burner plate reacting and producing uncontrolled temperature peaks which favor the formation of NO x .
  • NO x is formed on the one hand from the nitrogen bound in the fuel and on the other hand thermally from free nitrogen, which is present in particular in the air and possibly also in the fuel, for example in natural gas.
  • the thermal NO x formation is preferably carried out at high combustion temperatures, for example natural gas from approximately 1600 ° C.
  • a low combustion temperature and thus a low NO x content in the exhaust gas can be achieved according to the inventive method for fuels with a low proportion of bound nitrogen by homogeneously mixing the combustion air / fuel mixture before the combustion with a cooling gas.
  • This cooling gas can contain air, exhaust gas, Steam or a mixture of two or all of these components.
  • the mass flow ratio e is defined as the ratio of a first mass flow, which is composed of a fuel quantity, a combustion air quantity and a cooling gas quantity, to a second mass flow, which is composed of the same fuel quantity and the combustion air quantity required for the stoichiometric combustion.
  • the theoretical combustion temperature results from the heat calorific value and the enthalpies of the materials fed to the burner without heat exchange with the environment, with complete combustion of the fuel to C0 2 and H 2 0.
  • the enthalpies are determined by quantities, temperatures and specific heat capacities of the substances.
  • the solid curves of a first family of curves show which combustion temperatures are reached as a function of the mass flow ratio e if the fuel natural gas is mixed homogeneously with air at the temperature T, indicated on the solid curves before combustion, if so in that
  • the mass flow ratio defined above, the first mass flow does not contain any recirculated exhaust gas as cooling gas and air quantities of different sizes are used as cooling gas.
  • the dashed curves of a second family of curves show in FIG. 1 the combustion temperatures that occur as a function of the mass flow ratio e, if the first mass flow of the mass flow ratio defined above contains an air quantity that is equal to the air quantity required for stoichiometric combustion in the second mass flow, and if the first mass flow contains recirculated exhaust gas as cooling gas. It applies to the dashed curves that the supplied combustion air has a temperature of 20 ° C and that the exhaust gas serving as cooling gas has the temperature T 2 indicated in each case on the dashed curves.
  • the dashed curves represent only an example for the determination of the theoretical combustion temperature or the mass flow ratio. For the sake of clarity, the corresponding curves have not been shown for cases in which differently tempered water vapor is used as cooling gas or that a differently tempered cooling gas with combustion air is mixed at a temperature other than 20 ° C. Such curves can be calculated using the specific data published in relevant manuals and the like.
  • the burner according to the invention is suitable for all fuels which are in gaseous or vapor form before combustion and which can be mixed homogeneously with the combustion air and the cooling gas.
  • the burner can be operated under normal pressure as well as under increased pressure.
  • the mixing tube 1 must be supplied with fuel 2, combustion air 3 and cooling gas 4.
  • the combustion air is fed to the mixing tube, for example, by a blower, not shown in FIG. 2.
  • air is used as the cooling gas, this air is supplied in the same way. If exhaust gas or water vapor serve as cooling gas, these can be conveyed together with the combustion air by a fan if their temperature or the temperature of the air-cooling mixture is permissible for the fan. Otherwise, the cooling gas as well as the fuel can reach the mixing tube directly, e.g. by injector action. To shorten the mixing tube, the fuel can also be fed upstream of the blower.
  • the burner head 5 is connected to the mixing tube 1, and its cross section 6 at the connection to the mixing tube 1 is, for example, twice the cross section of the mixing tube. This abrupt transition to a larger flow cross-section creates a tear-off edge for the flow.
  • the burner head 5 then expands ko nisch to, for example, 4.5 times the cross section of the mixing tube.
  • curved jacket shapes are also possible.
  • a burner plate 7 which has a large main flame bore 8 and a plurality of small bores 9 which are arranged in a plurality of concentric rings around the main flame bore 8 and serve to form the holding flames.
  • the small bores 9 can be replaced by corresponding slot-shaped openings.
  • the burner plate can consist of both metal and ceramic material.
  • the distances between the holding flame bores 9, which together have a slightly smaller free cross-section than the main flame bore 8, are selected so that they ensure a perfect ignition from the outermost holding flames to the main flame and a mutual stabilization of the holding flames.
  • the main flame bore 8 runs parallel to the burner axis, at least the holding flame bores 9, which are located in the outermost ring, are inclined at an angle of, for example, approximately 40 ° to the burner axis.
  • the outermost holding flame ring is stabilized in this way by backflows on the cylindrical wall of the burner mouth 10, which adjoins the burner plate 7.
  • the burner mouth 10 is only a short piece cylindrical and then tapers conically, for example to 2.9 times the cross section of the mixing tube.
  • the lateral surface of the burner mouth can be either conical, as shown in FIG. 2, or curved.
  • the burner plate 7 can also be made conical or curved instead of the flat shape shown.
  • the burner mouth 10 is connected to a flame protection cover 11.
  • a flame protection cover 11 In Figure 2 it is shown as a cylindrical tube, the inside diameter of which corresponds to the largest outside diameter of the free-burning flame.
  • Another advantageous embodiment, not shown, of the flame protection cover consists of a conically expanded and subsequently cylindrical tube, which is therefore adapted to the shape of the flame.
  • the flame protection cover is designed in such a way that it does not hinder or restrict the flame.
  • the flame protection cover 11 prevents the flame from being cooled further by contact with air and / or exhaust gas from the environment and would thereby be prevented from completely burning out.
  • a flame protection cover 11 It has proven to be advantageous to provide the inside of the burner mouth 10 and the flame protection cover 11 with a catalytically ineffective material or at low ambient temperatures with thermal insulation, e.g. Ceramics to line.
  • the task of a flame protection cover can also be fulfilled by a combustion chamber that does not dissipate useful heat and in which the flame can burn out completely.
  • the method according to the invention it is possible for the first time to burn homogeneous mixtures of the type mentioned with very high mass flow ratios in a manner that is reliable and low in pollutants.
  • a desired combustion temperature can be set in the manner described above. Because the mixing of the burner gases with foreign gases, such as air or exhaust gas, which are present in the vicinity of the burner, is largely avoided, the flame temperature remains so homogeneous that the thermal NO x formation largely corresponds to the NO x formation in the theoretical Combustion temperature corresponds.
  • the burner according to the invention is characterized, among other things, by a quiet, stable, low-pollutant combustion over a large output range.
  • the possible uses for the subject matter of the invention are extremely versatile. These include, for example, the generation of exhaust gas-air mixtures for heating and drying food, the heating of boilers and industrial ovens of all kinds and the generation of drive gas for gas turbines. In all of these cases, because of the unusually low NO x content in the exhaust gas, the subject of the invention can make a valuable contribution to air pollution control.

Description

Die Erfindung betrifft ein Verfahren zum Betrieb von Vormischbrennern unter normalem oder erhöhtem Druck mit gasförmigen Brennstoffen, oder mit bei Normaltemperatur flüssigen und vor der Verbrennung vollständig verdampften Brennstoffen, bei niedrigen Verbrennungstemperaturen unter Bildung schadstoffarmer Abgase, sowie einen Brenner zur Durchführung des Verfahrens.The invention relates to a method for operating premix burners under normal or increased pressure with gaseous fuels, or with fuels which are liquid at normal temperature and completely vaporized before combustion, at low combustion temperatures with formation of low-emission gases, and a burner for carrying out the method.

Bei der Verbrennung gasförmiger und flüssiger Brennstoffe entstehen als Schadstoffe im Abgas unter anderem die Stickstoffoxide NO und NOz' zusammengefasst als NOX bezeichnet. Diese Schadstoffe verunreinigen die Luft und können sich bei manchen Feuerungen negativ auf das im Ofen befindliche bzw. mit den Brennerabgasen in Berührung kommende Gut auswirken. Daher ist man bestrebt, den NOx-Gehalt im Abgas möglichst gering zu halten. Die Ursachen der NOx-Bildung sind bekannt, und es sind auch mehrere Massnahmen zur Verminderung des NOx-Gehalts im Abgas bekannt, wie z.B.During the combustion of gaseous and liquid fuels, the nitrogen oxides NO and NO z ', collectively referred to as NO x , are formed as pollutants in the exhaust gas. These pollutants contaminate the air and can have a negative effect on the material in the furnace or in contact with the burner exhaust gases in some furnaces. Therefore, efforts are made to keep the NO x content in the exhaust gas as low as possible. The causes of the NO x formation are known, and several measures for reducing the NO x content in the exhaust gas are also known, for example

Absenkung der Verbrennungstemperatur durch direkte Flammenkühlung, z.B. Wassereinspritzung oder gekühlte Brennflächen,

  • zwei oder mehrstufige Verbrennung,
  • Abgasrezirkulation durch Vorbeiführen der Abgase an der Flamme mittels Rückführungskanälen oder speziellen Brennerkonstruktionen,
  • überstöchiometrische Verbrennung.
Lowering the combustion temperature through direct flame cooling, e.g. water injection or cooled burning surfaces,
  • two or multi-stage combustion,
  • Exhaust gas recirculation by passing the exhaust gases past the flame using recirculation channels or special burner designs,
  • superstoichiometric combustion.

Trotzdem ist bisher kein Brenner für Industrie oder Gewerbe bekannt, der bei hoher Leistung (spezifische Leistung bezogen auf die Durchtrittsfläche oder das Durchtrittsvolumen des Brenners) einen extrem niedrigen NOx-Gehalt im Abgas aufweist. Dies gilt auch für einen bekannten Vormischbrenner (DE-B-1 526 031), bei dem das Gas und Luft durch getrennte, zur Leistungsverstellung des Brenners gemeinsam im Durchlassquerschnitt veränderbare Sektoren einer Lochplatte in eine Mischkammer geleitet werden und in dieser in einem bestimmten, über den gesamten Leistungsbereich des Brenners konstant bleibendem Mengenverhältnis gemischt werden, wonach das Gemisch durch eine Brennerplatte hindurchtritt, die eine gewöhnliche Perforation aus im wesentlichen gleich grossen und gleiche Gemischmengen hindurchlassenden Flammenbohrungen aufweist.In spite of this, no burner for industry or trade is known to date, which has an extremely low NO x content in the exhaust gas at high output (specific output based on the passage area or the passage volume of the burner). This also applies to a known premix burner (DE-B-1 526 031), in which the gas and air are passed into a mixing chamber through separate sectors of a perforated plate that can be changed in the passage cross-section to adjust the output of the burner, and in this in a certain chamber the entire output range of the burner is mixed in a constant quantitative ratio, after which the mixture passes through a burner plate which has an ordinary perforation of flame holes which allow the same mixture quantities to pass through.

Aufgabe der Erfindung ist es, ein Verfahren zum Betrieb von Vormischbrennern anzugeben, mit dem gas- und/oder dampfförmige Brennstoffe bei normalem oder erhöhtem Druck so verbrannt werden können, dass einerseits eine vollständige Verbrennung bei niedrigen Verbrennungstemperaturen unter Bildung von Abgasen mit extrsm niedrigen NOx-Gehalten stattfindet, andererseitsaber auch eine hohe Brennerleistung erzielt wird und eine über einen grossen Leistungsbereich mit stabiler Flamme brennende betriebssichere Verbrennung erzielt wird, sowie einen für die Durchführung dieses Verfahrens besonders gestalteten und geeigneten Brenner zu schaffen.The object of the invention is to provide a method for operating premix burners with which gaseous and / or vaporous fuels can be burned at normal or elevated pressure so that on the one hand complete combustion at low combustion temperatures with the formation of exhaust gases with extremely low NO x - Held takes place, but on the other hand a high burner output is achieved and reliable combustion burning over a large output range is achieved, as well as creating a burner specially designed and suitable for carrying out this method.

Diese Aufgabe wird erfindungsgemäss durch die in den Ansprüchen 1 bis 9 genannten Massnahmen gelöst. Nach dem erfindungsgemässen Verfahren wird also zur Verringerung der NOx-Bildung mit einer grossen Menge an Kühlgas gearbeitet, und zwar insbesondere bei hohen spezifischen Leistungen des Brenners, bei denen gewöhnlich die NOx-Bildung und Tendenz zur NOx-Emission mit den Abgasen zunimmt. Die durch die Anwendung des Kühlgases eintretende Verminderung der Flammengeschwindigkeit lässt dennoch eine stabile Verbrennung zu, und zwar wegen der gleichzeitigen Anwendung der besonderen Flammengestaltung bei der Verbrennung des Gemisches und wegen der Abschirmung der Flamme bis zu ihrem vollständigen Ausbrand.According to the invention, this object is achieved by the measures mentioned in claims 1 to 9. According to the method according to the invention, a large amount of cooling gas is therefore used to reduce the NO x formation, in particular at high specific burner outputs, at which the NO x formation and tendency towards NO x emission usually increases with the exhaust gases . The reduction in flame speed caused by the use of the cooling gas nevertheless permits stable combustion, because of the simultaneous application of the special flame design during the combustion of the mixture and because of the shielding of the flame until it is completely burned out.

Ein entsprechender Betrieb wäre mit dem vorstehend erwähnten bekannten Vormischbrenner (DE-B-1 526 031) nicht möglich. Bei diesem Brenner würden, wenn die Luftmenge gegenüber der Gasmenge, d.h. die Luftzahl vergrössert würde, mit zunehmender Luftzahl die Druckverluste im Brenner überproportional ansteigen, so dass sich bei vorgegebenen Gebläsedrücken die Leistung des Brenners vermindern müsste. Ferner wird das Gemisch vor der Brennerplatte durch die sich verengende Mischkammer, die im übrigen auch für eine homogene Durchmischung zu kurz ist, beschleunigt, und wenn ausserdem noch die Luftzahl erhöht würde und über die bisher bei üblichen Vormischbrennern erlaubter Luftzahlen gesteigert würde, würden die Gemischgeschwindigkeiten zu gross werden, um bei der gleichzeitig mit einer Luftzahlerhöhung eintretenden Verminderung der Flammengeschwindigkeit ein Halten der Flamme zu ermöglichen, insbesondere da der bekannte Brenner für die Möglichkeit, bei erhöhter Luftzahl ein Abreissen der Flamme von der Brennerplatte verhindern zu können, keine entsprechend angepasste Flammengestaltung aufweist und keine Mittel zur wirksamen Abschirmung der Flamme besitzt. Das Fehlen einer wirksamen Flammenabschirmung bei dem bekannten Brenner trägt auch dazu bei, die stattfindende Verbrennung unvollkommen zu machen, was dazu führt, dass die Verbrennungsprodukte in dem der Brennerplatte nachfolgenden Ofenraum ausreagieren und unkontrollierte Temperaturspitzen erzeugen, die die NOx-Bildung begünstigen.A corresponding operation would not be possible with the known premix burner (DE-B-1 526 031) mentioned above. With this burner, if the amount of air compared to the amount of gas, ie the air ratio, were increased, the pressure losses in the burner would increase disproportionately with the increase in the air ratio, so that the burner output would have to decrease at the specified fan pressures. Furthermore, the mixture in front of the burner plate is accelerated by the narrowing mixing chamber, which is also too short for homogeneous mixing, and if the air ratio were also increased and the air ratios previously allowed for conventional premixing burners were increased, the mixture speeds would become too large to allow the flame to be held when the flame speed decreases at the same time as the air ratio increases, in particular since the known burner does not have a correspondingly adapted flame design for the possibility of preventing the flame from tearing off the burner plate when the air ratio is increased and has no means of effectively shielding the flame. The lack of effective flame shielding in the known burner also helps to make the combustion taking place incomplete, which leads to the combustion products in the furnace chamber following the burner plate reacting and producing uncontrolled temperature peaks which favor the formation of NO x .

Nachstehend werden anhand der Figuren 1 und 2 das erfindungsgemässe Verfahren sowie der Aufbau und die Wirkungsweise des erfindungsgemässen Brenners erläutert.The method according to the invention and the structure and mode of operation of the burner according to the invention are explained below with reference to FIGS. 1 and 2.

NOx bildet sich einerseits aus dem im Brennstoff gebundenen Stickstoff sowie andererseits thermisch aus freiem Stickstoff, der insbesondere in der Luft und gegebenenfalls ausserdem im Brennstoff, z.B. in Erdgas, vorhanden ist. Die thermische NOx-Bildung erfolgt bevorzugt bei hohen Verbrennungstemperaturen, z.B. bei Erdgas ab ca. 1600°C. Eine niedrige Verbrennungstemperatur und damit einen geringen NOx-Gehalt im Abgas erreicht man nach dem erfindungsgemässen Verfahren bei Brennstoffen mit geringem Anteil an gebundenem Stickstoff durch homogenes Mischen des Verbrennungsluft-Brennstoffgemisches vor der Verbrennung mit einem Kühlgas. Dieses Kühlgas kann Luft, Abgas, Wasserdampf oder ein Gemisch zweier oder aller dieser Komponenten sein. Um z.B. theoretisch 1 ppm NOx im Abgas (parts per million bezogen auf luftfreies und trockenes Abgas) zu erreichen, ist bei einem Druck von 1 bar und bei der Verwendung von Luft von 20°C als Kühlgas eine Einstellung der theoretischen Verbrennungstemperatur von 1330°C erforderlich.NO x is formed on the one hand from the nitrogen bound in the fuel and on the other hand thermally from free nitrogen, which is present in particular in the air and possibly also in the fuel, for example in natural gas. The thermal NO x formation is preferably carried out at high combustion temperatures, for example natural gas from approximately 1600 ° C. A low combustion temperature and thus a low NO x content in the exhaust gas can be achieved according to the inventive method for fuels with a low proportion of bound nitrogen by homogeneously mixing the combustion air / fuel mixture before the combustion with a cooling gas. This cooling gas can contain air, exhaust gas, Steam or a mixture of two or all of these components. In order to theoretically achieve 1 ppm NO x in the exhaust gas (parts per million based on air-free and dry exhaust gas), a setting of the theoretical combustion temperature of 1330 ° is required at a pressure of 1 bar and when using air at 20 ° C as the cooling gas C required.

In Figur 1 ist am Beispiel der Verbrennung von Erdgas die Abhängigkeit der theoretischen Verbrennungstemperatur von dem Massenstromverhältnis e bei verschiedenen Lufttemperaturen Ti und Abgastemperaturen T2 dargestellt.In FIG. 1, the dependence of the theoretical combustion temperature on the mass flow ratio e at different air temperatures T i and exhaust gas temperatures T 2 is shown using the example of the combustion of natural gas.

Das Massenstromverhältnis e ist definiert als Verhältnis eines ersten Massenstromes, der sich aus einer Brennstoffmenge, einer Verbrennungsluftmenge und einer Kühlgasmenge zusammensetzt, zu einem zweiten Massenstrom, der sich aus der gleichen Brennstoffmenge und der für die stöchiometrische Verbrennung erforderlichen Verbrennungsluftmenge zusammensetzt. Die theoretische Verbrennungstemperatur ergibt sich ohne Wärmeaustausch mit der Umgebung, bei vollständiger Verbrennung des Brennstoffes zu C02 und H20, aus dem Brennstoffheizwert und den Enthalpien der dem Brenner zugeführten Stoffe. Die Enthalpien werden bestimmt durch Mengen, Temperaturen und spezifische Wärmekapazitäten der Stoffe.The mass flow ratio e is defined as the ratio of a first mass flow, which is composed of a fuel quantity, a combustion air quantity and a cooling gas quantity, to a second mass flow, which is composed of the same fuel quantity and the combustion air quantity required for the stoichiometric combustion. The theoretical combustion temperature results from the heat calorific value and the enthalpies of the materials fed to the burner without heat exchange with the environment, with complete combustion of the fuel to C0 2 and H 2 0. The enthalpies are determined by quantities, temperatures and specific heat capacities of the substances.

In Figur 1 zeigen die durchgezogenen Kurven einer ersten Kurvenschar, welche Verbrennungstemperaturen in Abhängigkeit vom Massenstromverhältnis e erreicht werden, wenn der Brennstoff Erdgas vor der Verbrennung allein mit Luft mit der jeweils an den durchgezogenen Kurven angegebenen Temperatur T, homogen gemischt wird, wenn also in dem oben definierten Massenstromverhältnis der erste Massenstrom kein rückgeführtes Abgas als Kühlgas enthält und allein unterschiedlich grosse Luftmengen als Kühlgas verwendet werden.In Figure 1, the solid curves of a first family of curves show which combustion temperatures are reached as a function of the mass flow ratio e if the fuel natural gas is mixed homogeneously with air at the temperature T, indicated on the solid curves before combustion, if so in that The mass flow ratio defined above, the first mass flow does not contain any recirculated exhaust gas as cooling gas and air quantities of different sizes are used as cooling gas.

Die gestrichelten Kurven einer zweiten Kurvenschar zeigen in Figur 1 die in Abhängigkeit vom Massenstromverhältnis e eintretenden Verbrennungstemperaturen, wenn der erste Massenstrom des oben definierten Massenstromverhältnisses eine Luftmenge enthält, die gleich der für die stöchiometrische Verbrennung benötigten Luftmenge im zweiten Massenstrom ist, und wenn der erste Massenstrom rückgeführtes Abgas als Kühlgas enthält. Hierbei gilt für die gestrichelten Kurven, dass die zugeführte Verbrennungsluft eine Temperatur von 20°C hat und dass das als Kühlgas dienende Abgas die jeweils an den gestrichelten Kurven angegebene Temperatur T2 hat.The dashed curves of a second family of curves show in FIG. 1 the combustion temperatures that occur as a function of the mass flow ratio e, if the first mass flow of the mass flow ratio defined above contains an air quantity that is equal to the air quantity required for stoichiometric combustion in the second mass flow, and if the first mass flow contains recirculated exhaust gas as cooling gas. It applies to the dashed curves that the supplied combustion air has a temperature of 20 ° C and that the exhaust gas serving as cooling gas has the temperature T 2 indicated in each case on the dashed curves.

Die gestrichelten Kurven stellen lediglich ein Beispiel für die Bestimmung der theoretischen Verbrennungstemperatur bzw. des Massenstromverhältnisses dar. Der Übersichtlichkeit halber wurde darauf verzichtet, die entsprechenden Kurven für diejenigen Fälle darzustellen, dass unterschiedlich temperierter Wasserdampf als Kühlgas verwendet wird oder dass ein unterschiedlich temperiertes Kühlgas mit Verbrennungsluft von anderer Temperatur als 20°C vermischt wird. Solche Kurven können unter Verwendung der in einschlägigen Handbüchern und dergleichen veröffentlichten spezifischen Daten errechnet bzw. dargestellt werden.The dashed curves represent only an example for the determination of the theoretical combustion temperature or the mass flow ratio. For the sake of clarity, the corresponding curves have not been shown for cases in which differently tempered water vapor is used as cooling gas or that a differently tempered cooling gas with combustion air is mixed at a temperature other than 20 ° C. Such curves can be calculated using the specific data published in relevant manuals and the like.

Aus Figur 1 ist zu entnehmen, dass zum Erreichen einer theoretischen Verbrennungstemperatur von z.B. 1300°C bei Verwendung nur von Verbrennungsluft von 20°C zugleich als Kühlgas (unterste durchgezogene Kurve) das Massenstromverhältnis e = 1,74 beträgt, während bei Verwendung von Verbrennungsluft von 20°C vermischt mit Abgas von 100°C als Kühlgas (unterste gestrichelte Kurve) das Massenstromverhältnis e = 1,70 ist.It can be seen from Figure 1 that in order to reach a theoretical combustion temperature of e.g. 1300 ° C when using only combustion air of 20 ° C at the same time as cooling gas (bottom solid curve) the mass flow ratio is e = 1.74, while when using combustion air of 20 ° C mixed with exhaust gas of 100 ° C as cooling gas (bottom dashed line Curve) the mass flow ratio e = 1.70.

Bei Versuchen, die sowohl im Labor als auch im betriebsmässigen Einsatz durchgeführt wurden, wurden NOX -Werte von 1,5 ppm (luftfrei, trocken) bei Verwendung von Erdgas als Brennstoff und Luft als Verbrennungs- und Kühlgas erzielt, wobei eine theoretische Verbrennungstemperatur von 1300°C eingestellt wurde. Das zeigt, dass die weiteroben genannten theoretischen Werte in der Praxis weitgehend erreicht werden. Bei den bisher üblichen Brennern beträgt der NOx-Gehalt im Abgas durchschnittlich 50 - 500 ppm (luftfrei, trocken).Experiments carried out both in the laboratory and in operational use have shown NO x values of 1.5 ppm (air-free, dry) when using natural gas as fuel and air as combustion and cooling gas, with a theoretical combustion temperature of 1300 ° C was set. This shows that the theoretical values mentioned above are largely achieved in practice. With the burners that have been customary to date, the NO x content in the exhaust gas averages 50-500 ppm (air-free, dry).

Bei niedrigen Verbrennungstemperaturen (bei Erdgas z.B. unter ca. 1600°C) wird die Verbrennungsgeschwindigkeit jedoch schon so gering, dass die Verbrennung instabil verlaufen kann und dass eine weitere Abkühlung der Flamme leicht zur Stabilisierung von Verbrennungszwischenprodukten wie CO und Formaldehyd führen kann. Diese Schwierigkeiten werden vermieden, wenn der Brenner erfindungsgemäss ausgebildet ist.At low combustion temperatures (e.g. natural gas below approx. 1600 ° C) the combustion rate becomes so low that the combustion can be unstable and that further cooling of the flame can easily stabilize combustion intermediates such as CO and formaldehyde. These difficulties are avoided if the burner is designed according to the invention.

Der erfindungsgemässe Brenner ist geeignet für alle Brennstoffe, die vor der Verbrennung gas- oder dampfförmig vorliegen und die homogen mit der Verbrennungsluft und dem Kühlgas vermischt werden können. Der Brenner kann sowohl unter Normaldruck als auch unter erhöhtem Druck betrieben werden.The burner according to the invention is suitable for all fuels which are in gaseous or vapor form before combustion and which can be mixed homogeneously with the combustion air and the cooling gas. The burner can be operated under normal pressure as well as under increased pressure.

Ein Ausführungsbeispiel des erfindungsgemässen Brenners ist in Figur 2 dargestellt. Nachstehend werden das erfindungsgemässe Verfahren sowie der Brenner beschrieben.An embodiment of the burner according to the invention is shown in Figure 2. The method according to the invention and the burner are described below.

Dem Mischrohr 1 müssen Brennstoff 2, Verbrennungsluft 3 und Kühlgas 4 zugeführt werden. Die Verbrennungsluft wird dem Mischrohr beispielsweise durch ein in Figur 2 nicht näher dargestelltes Gebläse zugeführt.The mixing tube 1 must be supplied with fuel 2, combustion air 3 and cooling gas 4. The combustion air is fed to the mixing tube, for example, by a blower, not shown in FIG. 2.

Wenn Luft als Kühlgas verwendet wird, wird diese Luft auf gleiche Weise zugeführt. Wenn Abgas oder Wasserdampf als Kühlgas dienen, können diese gemeinsam mit der Verbrennungsluft durch ein Gebläse gefördert werden, wenn ihre Temperatur bzw. die Temperatur des Luft-Kühl-Gemisches für das Gebläse zulässig ist. Anderenfalls kann das Kühlgas ebenso wie der Brennstoff dem Mischrohr direkt, .z.B. durch Injektorwirkung, zugeführt werden. Zur Verkürzung des Mischrohres kann auch der Brennstoff vor dem Gebläse zugeführt werden.If air is used as the cooling gas, this air is supplied in the same way. If exhaust gas or water vapor serve as cooling gas, these can be conveyed together with the combustion air by a fan if their temperature or the temperature of the air-cooling mixture is permissible for the fan. Otherwise, the cooling gas as well as the fuel can reach the mixing tube directly, e.g. by injector action. To shorten the mixing tube, the fuel can also be fed upstream of the blower.

An das Mischrohr 1 schliesst sich der Brennerkopf 5 an, dessen Querschnitt 6 am Anschluss an das Mischrohr 1 beispielsweise das 2fache des Mischrohrquerschnittes beträgt. Durch diesen sprunghaften Übergang auf einen grösseren Strömungsquerschnitt wird eine Abrisskante für die Strömung gebildet. Der Brennerkopf 5 erweitert sich danach konisch auf beispielsweise das 4,5fache des Mischrohrquerschnittes. Statt der dargestellten Kegelform des Brennerkopfmantels sind auch gekrümmte Mantelformen möglich. Am Ende des Brennerkopfes ist eine Brennerplatte 7 angeordnet, die eine grosse Hauptflammen-Bohrung 8 und mehrere kleine Bohrungen 9 aufweist, die in mehreren konzentrischen Ringen um die Hauptflammen-Bohrung 8 angeordnet sind und zur Bildung der Halteflammen dienen. Je nach Grösse des Brennerkopfes können mehrere Hauptflammen-Bohrungen in der Brennerplatte vorhanden sein. Ausserdem können die kleinen Bohrungen 9 durch entsprechende schlitzförmige Öffnungen ersetzt werden. Die Brennerplatte kann sowohl aus Metall als auch aus keramischem Material bestehen. Die Abstände der Halteflammen-Bohrungen 9, die zusammen einen etwas geringeren freien Querschnitt als die Hauptflammen-Bohrung 8 haben, werden so gewählt, dass sie eine einwandfreie Überzündung von den äussersten Halteflammen zur Hauptflamme und eine gegenseitige Stabilisierung der Halteflammen gewährleisten. Während die Hauptflammen-Bohrung 8 parallel zur Brennerachse verläuft, sind mindestens die Halteflammen-Bohrungen 9, die sich im äussersten Ring befinden, in einem Winkel von beispielsweise etwa 40° zur Brennerachse geneigt. Der äusserste Halteflammen-Ring wird auf diese Weise durch Rückströmungen an der zylindrischen Wand des Brennermundes 10, der sich an die Brennerplatte 7 anschliesst, stabilisiert.The burner head 5 is connected to the mixing tube 1, and its cross section 6 at the connection to the mixing tube 1 is, for example, twice the cross section of the mixing tube. This abrupt transition to a larger flow cross-section creates a tear-off edge for the flow. The burner head 5 then expands ko nisch to, for example, 4.5 times the cross section of the mixing tube. Instead of the conical shape of the burner head jacket shown, curved jacket shapes are also possible. At the end of the burner head there is a burner plate 7 which has a large main flame bore 8 and a plurality of small bores 9 which are arranged in a plurality of concentric rings around the main flame bore 8 and serve to form the holding flames. Depending on the size of the burner head, there may be several main flame holes in the burner plate. In addition, the small bores 9 can be replaced by corresponding slot-shaped openings. The burner plate can consist of both metal and ceramic material. The distances between the holding flame bores 9, which together have a slightly smaller free cross-section than the main flame bore 8, are selected so that they ensure a perfect ignition from the outermost holding flames to the main flame and a mutual stabilization of the holding flames. While the main flame bore 8 runs parallel to the burner axis, at least the holding flame bores 9, which are located in the outermost ring, are inclined at an angle of, for example, approximately 40 ° to the burner axis. The outermost holding flame ring is stabilized in this way by backflows on the cylindrical wall of the burner mouth 10, which adjoins the burner plate 7.

Der Brennermund 10 ist nur ein kurzes Stück zylindrisch ausgeführt und verjüngt sich dann konisch, beispielsweise auf das 2,9fache des Mischrohrquerschnittes. Die Mantelfläche des Brennermundes kann analog dem Brennerkopf entweder kegelförmig, wie in Figur 2 dargestellt, oder gewölbt ausgeführt sein. Auch die Brennerplatte 7 kann statt der dargestellten ebenen Form kegelförmig oder gewölbt ausgeführt sein.The burner mouth 10 is only a short piece cylindrical and then tapers conically, for example to 2.9 times the cross section of the mixing tube. Analogously to the burner head, the lateral surface of the burner mouth can be either conical, as shown in FIG. 2, or curved. The burner plate 7 can also be made conical or curved instead of the flat shape shown.

Um die entstehende Flamme vor einer Abkühlung von aussen zu schützen und um ein unerwünschtes Eindringen von Fremdgasen in den Flammen- bzw. Verbrennungsbereich zu verhindern, was die eingangs beschriebeen negativen Wirkungen zur Folge hätte, ist der Brennermund 10 mit einer Flammenschutzhülle 11 verbunden. In Figur 2 ist sie als zylindrisches Rohr dargestellt, dessen Innendurchmesser dem grössten Aussendurchmesser der freibrennenden Flamme entspricht. Eine andere, nicht dargestellte vorteilhafte Ausführungsform der Flammenschutzhülle besteht aus einem konisch erweiterten und anschliessend zylindrischen Rohr, welches also der Flammenform angepasst ist. Die Flammenschutzhülle wird derart ausgebildet, dass sie die Flamme nicht behindert bzw. einengt. Die Flammenschutzhülle 11 verhindert, dass die Flamme durch Berührung mit Luft und/oder Abgas aus der Umgebung weiter abgekühlt wird und dadurch am vollständigen Ausbrand gehindert würde. Es hat sich als vorteilhaft erwiesen, den Brennermund 10 und die Flammenschutzhülle 11 innen mit einem katalytisch unwirksamen Material oder bei niedrigen Umgebungstemperaturen mit einer Wärmeisolierung, z.B. Keramik, auszukleiden. Die Aufgabe einer Flammenschutzhülle kann auch eine Brennkammer erfüllen, die keine Nutzwärme abführt und in der die Flamme vollständig ausbrennen kann.In order to protect the resulting flame from cooling from the outside and to prevent undesired penetration of foreign gases into the flame or combustion area, which would have the negative effects described above, the burner mouth 10 is connected to a flame protection cover 11. In Figure 2 it is shown as a cylindrical tube, the inside diameter of which corresponds to the largest outside diameter of the free-burning flame. Another advantageous embodiment, not shown, of the flame protection cover consists of a conically expanded and subsequently cylindrical tube, which is therefore adapted to the shape of the flame. The flame protection cover is designed in such a way that it does not hinder or restrict the flame. The flame protection cover 11 prevents the flame from being cooled further by contact with air and / or exhaust gas from the environment and would thereby be prevented from completely burning out. It has proven to be advantageous to provide the inside of the burner mouth 10 and the flame protection cover 11 with a catalytically ineffective material or at low ambient temperatures with thermal insulation, e.g. Ceramics to line. The task of a flame protection cover can also be fulfilled by a combustion chamber that does not dissipate useful heat and in which the flame can burn out completely.

Mit dem erfindungsgemässen Verfahren ist es erstmals möglich, homogene Gemische der genannten Art mit sehr hohen Massenstromverhältnissen betriebssicher und schadstoffarm zu verbrennen. Durch Einstellung des Massenstromverhältnisses kann in der zuvor beschriebenen Weise eine gewünschte Verbrennungstemperatur eingestellt werden. Dadurch, dass die Vermischung der Brennergase mit Fremdgasen, z.B. Luft oder Abgas, die in der Umgebung des Brenners vorhanden sind, weitestgehend vermieden wird, bleibt die Flammentemperatur so homogen, dass die thermische NOX-Bildung weitgehend der NOx-Bildung bei der theoretischen Verbrennungstemperatur entspricht.With the method according to the invention, it is possible for the first time to burn homogeneous mixtures of the type mentioned with very high mass flow ratios in a manner that is reliable and low in pollutants. By setting the mass flow ratio, a desired combustion temperature can be set in the manner described above. Because the mixing of the burner gases with foreign gases, such as air or exhaust gas, which are present in the vicinity of the burner, is largely avoided, the flame temperature remains so homogeneous that the thermal NO x formation largely corresponds to the NO x formation in the theoretical Combustion temperature corresponds.

Der erfindungsgemässe Brenner zeichnet sich trotz einfachster Konstruktion unter anderem durch eine leise, stabile, schadstoffarme Verbrennung über einen grossen Leistungsbereich aus.Despite the simplest construction, the burner according to the invention is characterized, among other things, by a quiet, stable, low-pollutant combustion over a large output range.

Die Anwendungsmöglichkeiten für den Erfindungsgegenstand sind ausserordentlich vielseitig. Dazu gehören beispielsweise die Erzeugung von Abgas-Luft-Gemischen zur Erwärmung und Trocknung von Lebensmitteln, die Beheizung von Kesseln und Industrieöfen der verschiedensten Art sowie die Erzeugung von Antriebsgas für Gasturbinen. In allen diesen Fällen kann wegen des ungewöhnlich geringen NOx-Gehalts im Abgas der Erfindungsgegenstand einen wertvollen Beitrag zur Luftreinhaltung leisten.The possible uses for the subject matter of the invention are extremely versatile. These include, for example, the generation of exhaust gas-air mixtures for heating and drying food, the heating of boilers and industrial ovens of all kinds and the generation of drive gas for gas turbines. In all of these cases, because of the unusually low NO x content in the exhaust gas, the subject of the invention can make a valuable contribution to air pollution control.

Claims (9)

1. Process for the operation of pre-mixture burners under normal or elevated pressure with gaseous fuels, or with fuels which are liquid at normal temperature and completely vaporised before combustion, at low combustion temperatures, forming waste gases having a low content of harmful substances, characterised in that a homogeneous mixture which is composed of the fuel in gas or vapour form, a combustion air quantity required for the complete combustion of the fuel and a cooling gas quantity serving for the setting of the combustion temperature of 1100to 1700°C, preferably 1200to 1300°C, is fed to the burner, in that the combustion of the homogeneous mixture takes place in a manner known per se in at least one central main flame which is surrounded by several support flame rings, and in that the occurring flame is protected over its length against access of ambient air and/or waste gas and against cooling to the exterior or heating from the exterior until the completion of burning.
2. Process according to Claim 1, characterised in that air and/or waste gas and/or water vapour is used as cooling gas in the unburned mixture fed to the burner.
3. Process according to Claim 1 or 2, characterised in that the quantity of the cooling gas amounts to 20 to 600% of the quantity of air required for the complete combustion of the fuel.
4. Apparatus for carrying out the process according to one of Claims 1 to 3, characterised by a mixer pipe (1) with supply conduits for the fuel (2), for the combustion air (3) and for the cooling gas (4), a burner head (5) adjoining the mixer pipe (1), which has at its entry end connected to the mixer pipe a cross-section of 1.1 to 3.8 times, preferably 1.8 to 2.7 times, the mixer pipe cross-section and widens to its exit end to a cross-section of 2.0 to 6.8 times, preferably 3.2 to 4.8 times, the mixer pipe cross-section, a burner plate (7) arranged at the widened exit end of the burner head (5), which in a manner known per se contains at least one large main flame bore (8) parallel to the burner axis and several small support flame openings (9) surrounding the main flame bore in several concentric rings, where at least the support flame openings in the outermost ring extend at an angle of 10 to 70°, preferably 25 to 45°, to the burner axis, a burner mouth (10) adjoining the burner plate (7) which with a cross-section corresponding to the widened exit end of the burner head is made initially cylindrical and then narrows to 1.4 to 4.9 times, preferably 2.3 to 3.5 times, the mixer pipe cross-section, and by a flame guard (11) adjoining the narrowed end of the burner mouth (10), which guard surrounds the flame over its length as far as the position of completion of flame combustion and the internal diameter of which corresponds to the maximum external diameter of the free-burning flame.
5. Apparatus according to Claim 4, characterised in that the flame guard (11) consists of a cylindrical tube extending from the narrowed end of the burner mouth (10) to the completely burned-out flame end.
6. Apparatus according to Claim 4, characterised in that the flame guard (11) consists of a tube which, beginning at the narrowed end of the burner mouth (10), firstly widens conically and then extends cylindrically as far as the completely burned-out flame end.
7. Apparatus according to one of Claims 4 to 6, characterised in that the burner mouth (10) and the flame guard (11) are formed by a combustion chamber connected to the burner head (5) with burner plate (7), which chamber conducts away practically no useful heat.
8. Apparatus according to one of Claims 4 to 7, characterised in that the burner mouth (10) and the flame guard (11) are internally lined with a catalytically ineffective material.
9. Apparatus according to Claim 8, characterised in that the burner plate (7), the burner mouth (10) and the flame guard (11) are produced from and/or lined with a thermally insulating ceramic material.
EP80102799A 1979-06-29 1980-05-21 Operating process for premix burners and burner for carrying out the process Expired EP0021035B1 (en)

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Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2926278A1 (en) * 1979-06-29 1981-01-15 Ruhrgas Ag METHOD FOR OPERATING PRE-MIXING BURNERS AND BURNERS FOR CARRYING OUT THE METHOD
NL8200272A (en) * 1982-01-26 1983-08-16 Veg Gasinstituut Nv BURNER.
FR2595791B1 (en) * 1986-03-14 1989-07-28 Centre Nat Rech Scient LOW EMISSION OF POLLUTANT GAS BURNER
DE3630177A1 (en) * 1986-09-04 1988-03-10 Ruhrgas Ag METHOD FOR OPERATING PRE-MIXING BURNERS AND DEVICE FOR CARRYING OUT THIS METHOD
US4773702A (en) * 1987-06-18 1988-09-27 Combi Co., Ltd. Reversible seat pad for a baby carriage
AU1862688A (en) * 1987-07-17 1989-01-19 Manville Corporation Method and apparatus for attenuating glass fibers
EP0440423B1 (en) * 1990-01-30 1994-12-07 Cyclean, Inc Drum dryer for reprocessing recycled asphalt pavement
US5805973A (en) * 1991-03-25 1998-09-08 General Electric Company Coated articles and method for the prevention of fuel thermal degradation deposits
US5891584A (en) * 1991-03-25 1999-04-06 General Electric Company Coated article for hot hydrocarbon fluid and method of preventing fuel thermal degradation deposits
US5247792A (en) * 1992-07-27 1993-09-28 General Electric Company Reducing thermal deposits in propulsion systems
EP0861402A1 (en) * 1995-11-13 1998-09-02 Gas Research Institute Flame ionization control apparatus and method
AUPP895999A0 (en) * 1999-03-01 1999-03-25 Bowin Technology Pty Limited Gas fired burner apparatus
US6383461B1 (en) 1999-10-26 2002-05-07 John Zink Company, Llc Fuel dilution methods and apparatus for NOx reduction
US6299433B1 (en) 1999-11-05 2001-10-09 Gas Research Institute Burner control
US7096722B2 (en) * 2002-12-26 2006-08-29 Woodward Governor Company Method and apparatus for detecting combustion instability in continuous combustion systems
EP1445534A1 (en) * 2003-01-29 2004-08-11 Ruhrgas Aktiengesellschaft Heating system for buildings, in particular for green houses
US20040236313A1 (en) * 2003-05-21 2004-11-25 Klein Jeffrey A. Infiltration cannula
US7241135B2 (en) 2004-11-18 2007-07-10 Honeywell International Inc. Feedback control for modulating gas burner
US8171716B2 (en) * 2007-08-28 2012-05-08 General Electric Company System and method for fuel and air mixing in a gas turbine
JP2009228961A (en) * 2008-03-21 2009-10-08 Gastar Corp Bath hot water supply device
CN102944014A (en) * 2012-10-22 2013-02-27 瑞焓能源科技有限公司 Industrial boiler burner and industrial boiler with same

Family Cites Families (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1512579A (en) * 1923-04-19 1924-10-21 Neville C Davison Gas burner
US2462704A (en) * 1945-02-07 1949-02-22 John S Zink Burner and burner nozzle
DE909760C (en) * 1950-11-24 1954-04-26 Philips Nv Procedure and burner for commissioning for gasifying heavier fuel
US2767784A (en) * 1951-03-22 1956-10-23 Ind Systems Inc Fuel burner
US2753925A (en) * 1951-07-05 1956-07-10 Sinclair Refining Co Carbon monoxide burner
US3352347A (en) * 1963-10-30 1967-11-14 Ferro Corp Ceramic refractory flame retention nozzle
US3320999A (en) * 1965-03-15 1967-05-23 Owens Corning Fiberglass Corp Internal combustion burner
FR1449818A (en) * 1965-07-05 1966-05-06 Soc Metallurgique Imphy Gas burner
US3485566A (en) * 1966-04-15 1969-12-23 Fritz Schoppe Burner for firing a combustion chamber
DE1977410U (en) * 1967-11-02 1968-01-25 Stroehlein & Co LABORATORY BURNER FOR NATURAL GAS.
FR1603101A (en) * 1968-04-03 1971-03-22 Oxy-acetylene cutting head
US3574506A (en) * 1968-07-29 1971-04-13 Bernzomatic Corp Blow torch burner
NL7113989A (en) * 1970-10-16 1972-04-18
CA954789A (en) * 1970-11-20 1974-09-17 Trw Inc. Burner assembly for providing reduced emission of air pollutant
JPS48100226U (en) * 1972-02-26 1973-11-26
GB1453440A (en) * 1973-01-18 1976-10-20 Flaregas Eng Ltd Apparatus for use in the disposal of waste gas
JPS49111235A (en) * 1973-02-24 1974-10-23
GB1465785A (en) * 1973-03-12 1977-03-02 Tokyo Gas Co Ltd Burner and method of combustion-
FR2236394A5 (en) * 1973-07-06 1975-01-31 Gaz De France
US3880571A (en) * 1973-07-26 1975-04-29 Trw Inc Burner assembly for providing reduced emission of air pollutant
JPS5043326U (en) * 1973-08-15 1975-05-01
JPS5128842U (en) * 1974-08-27 1976-03-02
US4113417A (en) * 1974-11-06 1978-09-12 Stein Industrie Combustion of hot gases of low calorific power
DE2525303C3 (en) * 1975-06-06 1979-05-10 Penzenskij Kompressornyj Zavod, Penza (Sowjetunion) Gas burner
DE2527073A1 (en) * 1975-06-18 1977-01-13 Pensenskij Kompressornyj Sawod High performance burner for gaseous fuels - has radial outlet nozzles for preheated gas and preheated air supply
JPS5759823Y2 (en) * 1975-08-16 1982-12-21
JPS5228732A (en) * 1975-08-29 1977-03-03 Matsushita Electric Ind Co Ltd Fully primary air-type gas burner
US4152108A (en) * 1977-07-15 1979-05-01 John Zink Company Steam injection to zone of onset of combustion in fuel burner
JPS5455214A (en) * 1977-10-12 1979-05-02 Hitachi Ltd Gas turbine combustor
DE2926278A1 (en) * 1979-06-29 1981-01-15 Ruhrgas Ag METHOD FOR OPERATING PRE-MIXING BURNERS AND BURNERS FOR CARRYING OUT THE METHOD

Also Published As

Publication number Publication date
US4439135A (en) 1984-03-27
JPS5610615A (en) 1981-02-03
BR8003995A (en) 1981-01-21
EP0021035A1 (en) 1981-01-07
CA1142421A (en) 1983-03-08
JPH0150804B2 (en) 1989-10-31
US4582476A (en) 1986-04-15
DE2926278A1 (en) 1981-01-15
US4530656A (en) 1985-07-23
DE2926278C2 (en) 1987-04-23
IN153603B (en) 1984-07-28

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