US3880571A - Burner assembly for providing reduced emission of air pollutant - Google Patents

Burner assembly for providing reduced emission of air pollutant Download PDF

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Publication number
US3880571A
US3880571A US383008A US38300873A US3880571A US 3880571 A US3880571 A US 3880571A US 383008 A US383008 A US 383008A US 38300873 A US38300873 A US 38300873A US 3880571 A US3880571 A US 3880571A
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United States
Prior art keywords
fuel
oxidizer
combustion
distribution tube
controlling
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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 - Lifetime
Application number
US383008A
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English (en)
Inventor
Richard R Koppang
Jr Harland L Burge
Wallace A Carter
Ellis W Sheffield
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Northrop Grumman Space and Mission Systems Corp
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TRW Inc
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Publication date
Application filed by TRW Inc filed Critical TRW Inc
Priority to US383008A priority Critical patent/US3880571A/en
Priority to BE136453A priority patent/BE805796R/xx
Priority to CA183,149A priority patent/CA991527A/en
Priority to IT83645/73A priority patent/IT1045989B/it
Priority to FR7344654A priority patent/FR2328372A5/fr
Priority to GB5235073A priority patent/GB1468364A/en
Priority to DE2431573A priority patent/DE2431573A1/de
Priority to SE7409632A priority patent/SE412637B/xx
Priority to AU71665/74A priority patent/AU482909B2/en
Priority to NL7410032A priority patent/NL7410032A/xx
Priority to JP49085928A priority patent/JPS5043532A/ja
Application granted granted Critical
Publication of US3880571A publication Critical patent/US3880571A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
    • F23D11/101—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet
    • F23D11/102—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet in an internal mixing chamber
    • F23D11/103—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet in an internal mixing chamber with means creating a swirl inside the mixing 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

Definitions

  • ABSTRACT A pair of conduits, coaxially arranged, provide flow paths for carrying combustible reactants to a combustion zone.
  • the central conduit otherwise known as a distribution tube, extends to within the combustion zone and includes a disc element at the combustion zone end thereof for deflecting an oxidizing reactant moving axially along the exterior of the distribution tube.
  • a fuel reactant introduced into the distribution tube is carried to the combustion zone end thereof where it issues through radially aligned orifices and impinges the oxidizing reactant to produce a hollow cone flame.
  • a mixing element may be included within the distribution tube to impart centrifugal motion to liquid fuels which are then subject to being atomized in the region of the radial ports.
  • NATURAL GAS L5 I07 BTU/HR INPUT UNCOOLED FURNACE 20% EXCESS AIR AI R BLOCKAGE RATIO :ii o 4.. 8 56518 62 PATENIEBAPMQIQYE, 3.880.571
  • the invention relates generally to burner assemblies used for the combustion of fossil and manufactured fuels. More particularly the invention relates to power burner assemblies which herein means burners of such a size as are normally used for industrial and commercial applications. e.g.. boilers. dryers. and process heat ers.
  • Typical burner assemblies provide two or more orifices through which a fuel or an oxidizer is ejected into an external mixing zone. Mixing takes place in the external mixing zone by impingement of one reactant stream which. in the case of liquid fuels provides additional atomization of the liquid fuel. Once the reactants have been ejected from the orifices. further treatment of the reactant stream generally is not attempted. However. simple impingement of one reactant stream with another does not result in optimum mixing.
  • Atomization of liquid fuel takes place in the external mixing zone by the impingement of the fuel stream with an oxidizer stream. Preconditioning of the fuel prior to its ejection from the orifice is seldom attempted.
  • Typical burner assemblies may be found in the 1933 patent to Zulver. US. Pat. No. l.934.837; the I966 patent to Schreter et al.. U.S. Pat. No. 3.254.846 and the 1965 patent to elverum. .lr. US. Pat. No. 3.205.656.
  • One method of reducing emissions of oxides of nitrogen is to minimize the residence time that hot nitrogen molecules are in contact with unreacted oxygen. and to conduct the combustion and post combustion process at minimum temperatures.
  • the residence time may be controlled by completing the combustion process rapidly and at near homogenous conditions. Flame temperature reduction may be accomplished by radiating and conducting heat away from the flame and by diluting the reactants with an inert gas. These conditions will also result in reduction of carbon monoxide. hydro carbon. and particulate emission also.
  • a burner assembly of the forced draft type includes a set of coaxial conduits defining an annular flow path therebetween which exits into a combustion zone.
  • a distribution tube. or inner conduit. includes an array of radially aligned orifices near the combustion zone end of the distribution tube.
  • the burner may further include means within the distribution tube for causing liquid fuels to be entrained upon the interior walls of the distribution tube. This fuel will then be subjected to shear forces at the radial ports that will assist in atomizing liquid fuels.
  • the flame By controlling the momentum of the reactant streams. properly sizing the deflector disc. and selectively sizing and positioning the array of orifices. the flame will take the shape of a hollow cone having a relatively thin wall.
  • FIG. 1 is a view in partial cross section and partly in block diagram form showing a burner assembly in com bination with an industrial type boiler unit;
  • FIG. 2 is a view in partial cross section showing the burner assembly of FIG. I and portion of the boiler combustion chamber;
  • FIG. 3 is a graph representing conditions of combustion.
  • FIGS. 3 I0 are graphical representations showing the effects of various dimensional and dynamic parameters on NO, emissions
  • FIG. II is a view in partial cross section showing a specific fuel distribution design
  • FIG. 12 is a graph representing the trend in NO, emissions as a function of burner rating.
  • FIG. 13 is an alternative embodiment of the burner assembly of FIG. 2.
  • the present invention is shown embodied in an industrial boiler 10 having a cylindrical inner wall 11, and an outer wall I2 defining a coolant jacket.
  • the boiler further has an inlet 14 for introducing a coolant such as water.
  • the inner wall I I serves as a combustion chamber wall and defines a combustion zone 16 wherein combustion products are introduced by a burner assembly I7.
  • An oxidizer from an oxidizer reservoir 18 is introduced into the assembly 17 by an oxidizer pump 19 and an oxidizer conduit 20. In many cases. the oxidizer is air taken directly from the atmosphere.
  • a fuel from a fuel reservoir 21 is introduced into the assembly 17 by a fuel pump 22 and fuel conduit 23.
  • a fuel atomizing gas which may be an oxidizer. such as air. or an inert gas, may be supplied to the assembly I7 by a mixing gas pump 24 and a mix ing gas conduit 25.
  • the burner assembly 17 is further detailed in FIG. 2 wherein the combustion zone 16. in addition to the chamber walls 11 is further defined by an end wall 26.
  • the oxidizer tube 27 enters the combustion chamber through the end wall 12.
  • a second conduit 28 hereinafter referred to as a distribution tube. is coaxially mounted within the oxidizer tube 27 and extends to within the combustion chamber.
  • the one end 30 of the distribution tube 28 carries a circular disc element 3!.
  • the distribution tube 28 is further characterized by an array of radially aligned orifices 32 which are circumferentially disposed around the distribution tube near the one end 30 thereof.
  • the oxidizer tube 27 together with the distribution tube 28 serve to define an annular flow path 33.
  • Oxidizer from oxidizer conduit (FIG. I) is introduced into the annular oxidizer flow path 33.
  • Atomizing gas from conduit may be introduced into distribution tube 28.
  • Fuel from fuel conduit 23 is introduced into the distribution tube 28.
  • an oxidizing gas such as air. is intro pokerd into the oxidizer supply tube 27 as indicated by the arrow at 54.
  • the oxidizer gas flows down the annular parh 33 to create a shroud of oxidizer gas around the distribution tube 28.
  • a fuel is introduced into the fuel supply tube 22 as indicated at arrow 35.
  • the fuel enters the distribution tube 28 through an inlet orifice 36.
  • the fuel may be joined by an atomizing gas introduced as indicated by the arrow 37.
  • the atomizing gas may simply be an oxidizer gas as indicated in FIG. 1, an inert gas such as steam. nitrogen. or combustion gas products recirculated from the combustion chamber.
  • the fuel and. if used. the atomizing gas pass down the distribution tube 28 toward the radial ports 32 and in the case of gaseous fuels such as methane become an admixture through turbulent mixing.
  • the fuel passes through the radial ports creating a plurality of jets around the distribution tube each of which impinges the shroud of oxidizing gas.
  • the inclusion of a mixing element 38 having helical surfaces 39 mounted or formed within the distribution tube 28 serves to impart centrifugal forces to the fuel and mixing gas.
  • liquid fuels. such as oil.
  • the liquid is centrifuged outwardly and entrained on the internal walls of the distribution tube 28.
  • atomizing gas exiting through the orifices subject the liquid to high shear forces which break up the liquid into a fine fog like mist.
  • the centrifuging of liquid fuels is enhanced by introducing the fuel tangentially into the distribution tube 28 thereby imparting to the fuel centrifugal motion prior to reaching the mixing element 38.
  • the impingement of the fuel exiting through the orifices 32 with the oxidizer stream results in a mixing of the fuel and the oxidizing gas in an external mixing zone generally designated by the numeral 40.
  • the gas flow is generally shown by the arrows at 41.
  • the external mixing is enhanced by any premixing which occurred within the distribution tube 28.
  • the external mixing is further enhanced by any oxidizing gas which passes between the fuel jets and is reflected into the external mixing zone 40 by the deflector disc 3
  • the deflected oxidizing gas. indicated at 42. impinges the main stream. where further mixing occurs.
  • there is provided a very thoroughly mixed set of reactants in both the radial and circumferential dimensions which aids in assuring a complete combustion process. local control of oxidizer and fuel mixture ratio. and therefore. as will be seen from later discussions. reduced emissions of air pollutants.
  • atomic oxygen combines with free nitrogen to form nitrous oxide and atomic nitrogen. i.e.. O N N0 N. This reaction may be followed by the atomic nitrogen combining with molecular oxygen. if available. to form more nitro gen oxide plus atomic oxygen, i.e.. N -l- 0 NO 0. Thermal generation of nitrogen oxide is dependent upon time. temperature. and the availability of molecular oxygen.
  • nitrogen oxide may be reduced by sufficiently reducing the time during which 0 is exposed to N or N. i.e.. reducing the resident time.
  • FIG. 3 shows that as a result of combustion. the temperature rises to some peak which is limited in part by the heat transfer characteristics of the system. After combustion. the temperature drops off gradually. Molecular oxygen of course decreases rapidly during combustion. but a certain residual quantity remains post combustion. It is known that thermal generation of NO requires temperatures in excess of some nominal temperature which is about 2.200 F.
  • the oxidizer will be air. the O to the extent that it exceeds the needs for combustion. is available to combine with the N from the air during the combustion step. Further. since this is a rate limiting step. rapid combustion contributes to reducing NO generation.
  • the presence of N is further compounded by chemically bound N, in the fuel.
  • the quantity of excess 0 at any particular time may vary greatly throughout the fuel-oxygen mixture.
  • stoichiomatric mixture ratios do not assure that local conditions throughout the combustion gases will also be at stoichometric conditions.
  • thermal generation of NO occurs only above about 2.200 F. Therefore. if the post combustion temperatures of the unburned fuel/air components are rapidly reduced to less than this critical temperature. there will be no further NO formation.
  • NO formation will occur downstream of the flame front due to the presence of oxygen and nitrogen at elevated temperatures. It is desirable to reduce the post combustion gas temperatures to less than such a critical temperature as rapidly as possible. This will of course depend in part upon the heat transfer characteristics of of the surrounding media. It is also known to induce cooler gases from an external source as by some recirculation scheme.
  • the substantially short conical flame 45 as produced by the invention herein results in higher gas velocities near the combustion chamber walls when the momentum ratio and the air blockage ratio are properly selected thereby providing heat transfer by convection in addition to radiation.
  • Heat transfer measurements have confirmed that a burner constructed and operated as disclosed herein displays better heat transfer characteristics than conventional burners of comparable rating.
  • the shape of the flame produced by the subject burner and the homogeneous mixing yield a flame shape substantially in the form of a hollow cone.
  • This shape is primarily dictated by the deflector 31 which serves as a flame holder and by the degree of combustion and swirl or momentum.
  • the degree to which the flame will be thrown radially outwardly toward the combustion chamber walls will be influenced by the air blockage ratio, discussed above.
  • a large blockage ratio indicates a relatively large disc which would tend to throw the flame more radially outward.
  • the primary combustion air velocity will also substantially affect the flame shape by throwing the flame more forward at higher velocities.
  • the resultant flame of the burner herein described has a relatively short combustion distance, i.e., the conical flame has a thin reaction zone. thereby indicating rapid combustion as desired.
  • the physical size and various dimensions are of course dependent upon the input rating of the burner and the heat content of the fuel. As in any burner. the total flow rates of the reactants are determined by the net heating value of the fuel selected. thus the oxidizer annual flow path 33, otherwise designated a venturi section. may be calculated for selected inlet pressures.
  • the sizing ofthe central pintle or distribution tube 28 has been developed from analytical and experimental investigations. These parameters are important in controlling the mixing characteristics.
  • the number and size of the fuel orifices 32. FIG. 2, may be determined from the fuel stream to air stream aspect ratio which herein means the ratio of the total fuel orifice area to the circumference of the distribution tube at the fuel orifice location.
  • the fuel orifice total area equation is as follows:
  • Q flow rate (cu. ft. per minute) A orifice area (sq. inches) C constant including the coefficient of discharge and a unit conversion factor AP pressure differential (psi) p specific weight of fluid (lbs/fr) substituting a nominal inlet pressure drop of 1 psi, an orifice coefficient of 0.65 and a specific weight for natural gas of 0.05 lb/ft" yields Q/A equal to 338.8.
  • the flow rate Q is determined from heat rating.
  • the total fuel injection area is then divided into a number of radial orifices distributed circumferentially around the central element in order to determine the fuel injection orifice diameter.
  • FIG. 4 show that with residual oil 6 increasing the number of orifices improves the circumferential distribution of fuel resulting in a reduction of the NO emis sions; however, manufacturing and economic consider ations places a practical limit on the number selected.
  • the radial momentum of the fuel stream should be held within a predetermined range to assure proper radial penetration of the fuel into the oxidizer stream. This constraint also limits the practical useful diameter and therefore the numbers of orifices. A sharp rise in NO, emissions as shown in FIG. 4 would occur when the orifice diameter becomes sufficiently small as to unduly limit fuel stream momentum.
  • the ratio of total number of fuel orifices times their diameters to the fuel distribution tube circumference is commonly called the fuel blockage, 8,. This ratio can be expressed as:
  • This ratio is defined as the ratio of the combustion air injection area (annular path 33) to the cross-sectional area of the deflector 31.
  • the combustion air requirements are based upon the desired fuel input rating and the design excess air.
  • the air required for combustion varies with the type of fuel; however. a representative value for natural gas is SCF air/SCF gas (standard cubic foot).
  • SCF air/SCF gas standard cubic foot.
  • the actual combustion requires some excess air, therefore. the burner should be sized for about it] 30 percent excess air.
  • the annular combustion air sheet must be suffi ciently thick to preclude penetration by the radial fuel jet prior to the final mixing by the deflector.
  • the penetration distance of the radial gas (natural gas) et into the air stream can be estimated from the following empirical equation I: vi 1),
  • the mixing gas serves as a means for atomizing the fuel by apparatus which provides for centrifugal action heretofore described and shown in FIG. I, or by the atomizing appa ratus of FIG. 11. or some other such device.
  • the atomizing gas may be steam in which case the hardware is simplified by eliminating the need for an air compressor in the atomizing system.
  • FIG. ll A alternate embodiment of the fuel distribution tube 28 utilized for testing in a YorlcShipply Scotch Marine boiler rated at 50 horsepower (2,100,000 BTU/hr) is shown in FIG. ll.
  • the distribution tube 28, in a configuration suitable for using fueLoil. includes a mating flange 52 for use with the York shippley boiler.
  • a pintle portion 53 projects into the boiler combustion chamber.
  • the pintle base portion 54 extends through the boiler air plennum which distributes air along the pintle toward the combustion chamber substantially as in FIG. 2 except that the deflector disc 31 is not shown.
  • Fuel oil is introduced into a fuel tube 55 while a mixing or atomizing gas is introduced through a gas inlet 56 and directed along the annular mixing gas tube 57 formed between the fuel tube 55 and the wall of the pintle portion 53.
  • Sets of fuel orifices 32 and 320 are matched-drilled through the walls of the pintle S3 and fuel tube 55.
  • This concentric type of fuel distribution tube pro vides an alternative liquid fuel atomizing means to that of the centrifugal type means of FIG. 2.
  • Fuel and atomizing gas. each under pressure. project fuel droplets mately stoichiometric proportion to achieve a pre determined heat input rating;
  • the Q flow rate 60- t per t burner emission characteristics will remain favorable A ri a (sq. ihChEiS) over a rather large range of heat output ratings as indi- C a t nclu ing the discharge Coefficient and cated by the trends depicted by FIG. 12.
  • a unit conversion factor Additional temperature dissipation may be provided P pre differential HCI'OSS Said l' (P by introducing cool gas to the interior of the conical p specific flighl 0f fluid (lbs/ft) and the number flame.
  • a cooling gas tube 44, FIG. 2, oforifices being determined in accordance with the is mounted coaxially within distribution tube 28.
  • Cooling gas tube 44 extends through deflector r "Du disc 31 so as to inject cooling gas into the interior of the whet flame 45.
  • Other features of the burner assembly are shown In d; fuel orifice diameter (inches) FIG. 13.
  • the distnbution tube 28 IS coupled through D fuel distribution tube diameter appropriate linkage to a translator device 47 whlch in "hides means [on l v men h providing a deflector disc affixed to the combustion mpa mg m0 6 o e zone end of the fuel distribution tube and having a tribution tube 28.
  • FIG. 13 is split along centerline 51 to Sh e districontrolling the fuel exiting the fuel orifices to provide bution tube 28 in two of its infinitely selectable posia penetration depth, whereby to minimize the protions.
  • Axial translation results in a change in the oxi- 55 duction of nitrogen oxides. dizer annulus area. this causing the flow rate to change 2.
  • the step of controlling the momentum of the hi m n rn n p r i n m y be pli h fuel and oxidizer reactants further includes the step of: y area throttling Wangel retaining the gn Point regulating the mass flow rates of the fuel and oxidizer ing characteristics. streams to provide an oxidizer to fuel momentum What is claimed is:
  • oxidizer regulating means operably coupled to said oxidizer tube for reguiating the oxidizer flow
  • a fuel distribution tube coaxially mounted within said oxidizer tube.
  • said tubes forming an annular oxidizer flow path, said fuel distribution tube having a plurality of radially aligned fuel orifices formed therein and distributed equidistant on a circumference of said fuel distribution tube proximate the combustion zone end thereof, the total orifice area being determined in accordance with the expression:

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Supply (AREA)
  • Spray-Type Burners (AREA)
US383008A 1973-07-26 1973-07-26 Burner assembly for providing reduced emission of air pollutant Expired - Lifetime US3880571A (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
US383008A US3880571A (en) 1973-07-26 1973-07-26 Burner assembly for providing reduced emission of air pollutant
BE136453A BE805796R (fr) 1973-07-26 1973-10-08 Bruleur a emission reduite de matieres polluantes dans l'air
CA183,149A CA991527A (en) 1973-07-26 1973-10-11 Burner assembly for providing reduced emission of air pollutant
IT83645/73A IT1045989B (it) 1973-07-26 1973-11-12 Bruciatore di conbustibili particolarmente liquidi che funzionando emette una quantita ridotta di in quinante atmosferici e metodo per regolarne il funzionamento e il dimensionamento
FR7344654A FR2328372A5 (fr) 1973-07-26 1973-12-13 Perfectionnements aux procedes et aux dispositifs pour reduire l'emission de polluants atmospheriques par une combustion
GB5235073A GB1468364A (en) 1973-07-26 1974-05-12 Burner assembly and method for controlling its operation to provide reduced emission of air pollutant
DE2431573A DE2431573A1 (de) 1973-07-26 1974-07-01 Brenneranordnung mit verminderter emission von die luft verunreinigenden stoffen
SE7409632A SE412637B (sv) 1973-07-26 1974-07-25 Forfaringssett for reglering av forbrenningen av reaktionskomponenter i en tryckmatad brennare samt tryckmatad brennare for utovande av forfaringssettet
AU71665/74A AU482909B2 (en) 1973-07-26 1974-07-25 A burner reduced emission of air pollutant
NL7410032A NL7410032A (nl) 1973-07-26 1974-07-25 Werkwijze en inrichting voor het regelen van de verbranding van reactiecomponenten in een bran- der met geforceerde trek.
JP49085928A JPS5043532A (de) 1973-07-26 1974-07-26

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US383008A US3880571A (en) 1973-07-26 1973-07-26 Burner assembly for providing reduced emission of air pollutant

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US (1) US3880571A (de)
JP (1) JPS5043532A (de)
BE (1) BE805796R (de)
CA (1) CA991527A (de)
DE (1) DE2431573A1 (de)
FR (1) FR2328372A5 (de)
GB (1) GB1468364A (de)
IT (1) IT1045989B (de)
NL (1) NL7410032A (de)
SE (1) SE412637B (de)

Cited By (24)

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US3989444A (en) * 1973-12-20 1976-11-02 Shell Oil Company Gas burner and process for the partial combustion of a gaseous fuel
US4018554A (en) * 1975-03-19 1977-04-19 Institutul Pentru Creatie Stintifica Si Tehnica-Increst Method of and apparatus for the combustion of liquid fuels
FR2370925A1 (fr) * 1976-11-11 1978-06-09 Lucas Industries Ltd Atomiseur de combustible liquide
EP0008187A1 (de) * 1978-08-04 1980-02-20 The British Petroleum Company p.l.c. Einspritzdüse und damit versehene Verteilerplatte
US4408982A (en) * 1982-01-05 1983-10-11 Union Carbide Corporation Process for firing a furnace
US4439135A (en) * 1979-06-29 1984-03-27 Ruhrgas Aktiengesellschaft Process for the operation of premixture burners and burner for carrying out the process
US4505665A (en) * 1980-02-19 1985-03-19 Southern California Edison Method and burner tip for suspressing emissions of nitrogen oxides
US4515553A (en) * 1980-04-10 1985-05-07 Kobe Steel, Ltd. Combustion method for reducing the emission of nitrogen oxides
US4541798A (en) * 1983-11-07 1985-09-17 Union Carbide Corporation Post-mixed spark-ignited burner
US4556386A (en) * 1982-01-04 1985-12-03 Mcelroy James G Combustion furnace and burner
US4618323A (en) * 1980-02-19 1986-10-21 Southers California Edison Method and burner tip for suppressing emissions of nitrogen oxides
US4764105A (en) * 1986-12-04 1988-08-16 Kirox, Inc. Waste combustion system
US4854853A (en) * 1986-12-04 1989-08-08 Kirox, Inc. Waste combustion system
USRE33464E (en) * 1984-08-17 1990-11-27 American Combustion, Inc. Method and apparatus for flame generation and utilization of the combustion products for heating, melting and refining
US5857339A (en) * 1995-05-23 1999-01-12 The United States Of America As Represented By The Secretary Of The Air Force Combustor flame stabilizing structure
US5984665A (en) * 1998-02-09 1999-11-16 Gas Research Institute Low emissions surface combustion pilot and flame holder
US20040020211A1 (en) * 2001-07-23 2004-02-05 Ramgen Power Systems, Inc. Trapped vortex combustor
US6694743B2 (en) 2001-07-23 2004-02-24 Ramgen Power Systems, Inc. Rotary ramjet engine with flameholder extending to running clearance at engine casing interior wall
US7402039B1 (en) 2003-03-17 2008-07-22 Mcelroy James G High velocity pressure combustion system
US20090113895A1 (en) * 2001-07-23 2009-05-07 Steele Robert C Vortex combustor for low NOx emissions when burning lean premixed high hydrogen content fuel
US20100285413A1 (en) * 2009-05-06 2010-11-11 General Vortex Energy, Inc. Apparatus and Methods For Providing Uniformly Volume Distributed Combustion of Fuel
US20100326137A1 (en) * 2008-02-08 2010-12-30 Saint-Gobain Glass France Low nox glass furnace with high heat transfer
US10281146B1 (en) * 2013-04-18 2019-05-07 Astec, Inc. Apparatus and method for a center fuel stabilization bluff body
GB2609240A (en) * 2021-07-26 2023-02-01 Adair Chris Boiler and combustion unit

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DE19542530C2 (de) * 1995-11-15 1998-08-27 Andreas Dipl Ing Patz Brennstoffzerstäuber

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US1934837A (en) * 1931-08-11 1933-11-14 Swinney Brothers Ltd Liquid fuel burner or atomizer
US2011283A (en) * 1930-04-28 1935-08-13 Lyman C Huff Apparatus for efficiently burning fluid fuels
US3182712A (en) * 1962-11-05 1965-05-11 Zink Co John Gaseous fuel burner for producing radiant heat
US3254846A (en) * 1965-01-21 1966-06-07 Hauck Mfg Co Oil atomizing burner using low pressure air
US3787168A (en) * 1972-08-23 1974-01-22 Trw Inc Burner assembly for providing reduced emission of air pollutant

Patent Citations (5)

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Publication number Priority date Publication date Assignee Title
US2011283A (en) * 1930-04-28 1935-08-13 Lyman C Huff Apparatus for efficiently burning fluid fuels
US1934837A (en) * 1931-08-11 1933-11-14 Swinney Brothers Ltd Liquid fuel burner or atomizer
US3182712A (en) * 1962-11-05 1965-05-11 Zink Co John Gaseous fuel burner for producing radiant heat
US3254846A (en) * 1965-01-21 1966-06-07 Hauck Mfg Co Oil atomizing burner using low pressure air
US3787168A (en) * 1972-08-23 1974-01-22 Trw Inc Burner assembly for providing reduced emission of air pollutant

Cited By (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3989444A (en) * 1973-12-20 1976-11-02 Shell Oil Company Gas burner and process for the partial combustion of a gaseous fuel
US4018554A (en) * 1975-03-19 1977-04-19 Institutul Pentru Creatie Stintifica Si Tehnica-Increst Method of and apparatus for the combustion of liquid fuels
FR2370925A1 (fr) * 1976-11-11 1978-06-09 Lucas Industries Ltd Atomiseur de combustible liquide
EP0008187A1 (de) * 1978-08-04 1980-02-20 The British Petroleum Company p.l.c. Einspritzdüse und damit versehene Verteilerplatte
US4439135A (en) * 1979-06-29 1984-03-27 Ruhrgas Aktiengesellschaft Process for the operation of premixture burners and burner for carrying out the process
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Also Published As

Publication number Publication date
SE412637B (sv) 1980-03-10
DE2431573A1 (de) 1975-02-20
JPS5043532A (de) 1975-04-19
NL7410032A (nl) 1975-01-28
SE7409632L (de) 1975-01-27
BE805796R (fr) 1974-02-01
FR2328372A5 (fr) 1977-05-13
AU7166574A (en) 1976-01-29
IT1045989B (it) 1980-06-10
GB1468364A (en) 1977-03-23
CA991527A (en) 1976-06-22

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