EP0021035B1 - Verfahren zum Betrieb von Vormischbrennern und Brenner zur Durchführung des Verfahrens - Google Patents

Verfahren zum Betrieb von Vormischbrennern und Brenner zur Durchführung des Verfahrens 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
Authority
EP
European Patent Office
Prior art keywords
burner
flame
combustion
air
guard
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP80102799A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0021035A1 (de
Inventor
Detlef Dr.-Ing. Altemark
Hans Dipl.-Ing. Sommers
Manfred Weid
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
EON Ruhrgas AG
Original Assignee
Ruhrgas AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6074483&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0021035(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Ruhrgas AG filed Critical Ruhrgas AG
Publication of EP0021035A1 publication Critical patent/EP0021035A1/de
Application granted granted Critical
Publication of EP0021035B1 publication Critical patent/EP0021035B1/de
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
EP80102799A 1979-06-29 1980-05-21 Verfahren zum Betrieb von Vormischbrennern und Brenner zur Durchführung des Verfahrens Expired EP0021035B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792926278 DE2926278A1 (de) 1979-06-29 1979-06-29 Verfahren zum betrieb von vormischbrennern und brenner zur durchfuehrung des verfahrens
DE2926278 1979-06-29

Publications (2)

Publication Number Publication Date
EP0021035A1 EP0021035A1 (de) 1981-01-07
EP0021035B1 true EP0021035B1 (de) 1983-08-10

Family

ID=6074483

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80102799A Expired EP0021035B1 (de) 1979-06-29 1980-05-21 Verfahren zum Betrieb von Vormischbrennern und Brenner zur Durchführung des Verfahrens

Country Status (7)

Country Link
US (3) US4439135A (el)
EP (1) EP0021035B1 (el)
JP (1) JPS5610615A (el)
BR (1) BR8003995A (el)
CA (1) CA1142421A (el)
DE (1) DE2926278A1 (el)
IN (1) IN153603B (el)

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DE2926278A1 (de) * 1979-06-29 1981-01-15 Ruhrgas Ag Verfahren zum betrieb von vormischbrennern und brenner zur durchfuehrung des verfahrens
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FR2595791B1 (fr) * 1986-03-14 1989-07-28 Centre Nat Rech Scient Bruleur a faible emission de gaz polluants
DE3630177A1 (de) * 1986-09-04 1988-03-10 Ruhrgas Ag Verfahren zum betreiben von vormischbrennern und vorrichtung zum durchfuehren dieses verfahrens
US4773702A (en) * 1987-06-18 1988-09-27 Combi Co., Ltd. Reversible seat pad for a baby carriage
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CA2035291C (en) * 1990-01-30 1996-02-27 Robert H. Nath Drum dryer for reprocessing recycled asphalt pavement
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
US5805973A (en) * 1991-03-25 1998-09-08 General Electric Company Coated articles and method for the prevention of fuel thermal degradation deposits
US5247792A (en) * 1992-07-27 1993-09-28 General Electric Company Reducing thermal deposits in propulsion systems
WO1997018417A1 (en) * 1995-11-13 1997-05-22 Gas Research Institute, Inc. 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
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US7096722B2 (en) * 2002-12-26 2006-08-29 Woodward Governor Company Method and apparatus for detecting combustion instability in continuous combustion systems
EP1445534A1 (de) * 2003-01-29 2004-08-11 Ruhrgas Aktiengesellschaft Anordnung zum Beheizen von Gebäuden, insbesondere von Gewächshäusern
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 (ja) * 2008-03-21 2009-10-08 Gastar Corp 風呂給湯装置
CN102944014A (zh) * 2012-10-22 2013-02-27 瑞焓能源科技有限公司 工业锅炉燃烧器及具有其的工业锅炉

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Also Published As

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

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