US20100167222A1 - Fuel nozzle for use in a burner - Google Patents

Fuel nozzle for use in a burner Download PDF

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Publication number
US20100167222A1
US20100167222A1 US12/564,369 US56436909A US2010167222A1 US 20100167222 A1 US20100167222 A1 US 20100167222A1 US 56436909 A US56436909 A US 56436909A US 2010167222 A1 US2010167222 A1 US 2010167222A1
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United States
Prior art keywords
air flow
flow channel
fuel
outlet
fuel nozzle
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Abandoned
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US12/564,369
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English (en)
Inventor
Darsell Karringten
William T. Kelly
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Individual
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Individual
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Priority to US12/564,369 priority Critical patent/US20100167222A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/008—Flow control devices
    • 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
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
    • 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
    • F23D14/70—Baffles or like flow-disturbing devices
    • 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
    • F23L1/00—Passages or apertures for delivering primary air for combustion 
    • 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
    • F23L2900/00—Special arrangements for supplying or treating air or oxidant for combustion; Injecting inert gas, water or steam into the combustion chamber
    • F23L2900/07006—Control of the oxygen supply
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery

Definitions

  • the present invention relates to fuel nozzles for use in burners, and more particularly to fuel nozzles for use in burners that mix air or oxygen with a gaseous or evaporated fuel.
  • Burners that use gaseous fuel or liquid fuel are used in many applications including boilers, line heaters, furnaces, other gas fired appliances, and in many others. Basically, these burners introduce a gaseous fuel or liquid fuel into a stream of air or oxygen. If liquid fuel is used, it must be vapourized or atomized first. The resulting flow of fuel and air or oxygen is ignited and exits the nozzle of the burner either as a visible flame or as a stream of an extremely hot gaseous mixture.
  • the most common design improvement used to overcome the environmental problem of emissions is to recirculate exhaust gases.
  • recirculation of the exhaust gases can be used to decrease the overall emissions of a burner system.
  • problems associated with such recirculation of the exhaust gases are, however, problems associated with such recirculation of the exhaust gases.
  • the most significant problem is that the recirculation of exhaust gases substantially increases the energy required for passing the mixture flow of combustion air and added exhaust gas through the system. For example, an increase of ten percent (10%) of exhaust gas recirculation from the exhaust back to the burner typically results in about a 40% to 45% increase in the required power of the fan that forces air into the burner system. Obviously, this is an attempt at a solution that is less than acceptable in terms of efficiency, and therefore cost. This is especially true considering most exhaust gases are passed through the burner system several times.
  • U.S. Pat. No. 7,484,956 issued Feb. 3, 2009, to Kobayashi et al. discloses Low NOx combustion using cogenerated oxygen and nitrogen streams.
  • the combustion of hydrocarbon fuel is achieved with less formation of NOx by feeding the fuel into a slightly oxygen-enriched atmosphere, and separating air into oxygen-rich and nitrogen-rich streams which are fed separately into the combustion device.
  • U.S. Pat. No. 7,429,173 issued Sep. 30, 2008, to Lanary et al. discloses a gas burner for use in a furnace and a method of burning gas in a furnace, especially but not exclusively a process furnace used in an oil cracking or refining process.
  • the gas burner comprises two passageways with adjacent outlets.
  • the first passageway is in fluid communication with a source of pressurised fuel gas and has an aperture through which recirculated flue gas can enter the first passageway and the second passageway is in fluid communication with a source of air.
  • fuel gas is injected into the first passageway and recirculated flue gas is thereby drawn into the first passageway so that it mixes with the fuel gas.
  • Fuel gas is partially combusted and a mixture of partially combusted fuel gas and recirculated flue gas flows up the first passageway and comes into contact with air from the second passageway and combusts.
  • the use of recirculated flue gas keeps down the level of NOx emissions and as the recirculated flue gas is sucked into the first passageway by the pressurised fuel gas flow, it is not necessary to provide complex pumping mechanisms.
  • U.S. Pat. No. 7,422,427 issued Sep. 9, 2008, to Lifshits discloses an Energy Efficient Low NOX Burner and Method of Operating Same.
  • the burner is for installation in a furnace having a mixing chamber defined by at least a furnace front wall, two side walls, a top wall and a bottom wall as well as heat transfer pipes through which a heat transfer medium flows and which are arranged on at least one of the top, bottom and side walls.
  • the burner assembly is mounted to the furnace front wall and has a tubular member with an open distal end that is located inside the mixing chamber. The other end of the tubular member is attached to the furnace front wall.
  • Several combustion air ports extend into the tubular member from the other proximal end thereof, and are coupled to a source of combustion air.
  • Several fuel gas discharge nozzles also extend into the tubular member from the other end thereof and are coupled to a fuel source.
  • Furnace gas openings formed in the tubular member are spaced apart from the distal end, are arranged about the tubular member's periphery, and are located relative to the mixing chamber so that furnace gases circulate past some of the heat transfer pipes before they reach the furnace gas openings to thereby form a mixture of combustion air, fuel gas and furnace gas.
  • a spinner at the distal end of the tubular member creates a recirculation zone for the mixture downstream of the spinner and the tubular member.
  • U.S. Pat. No. 6,485,289 issued Nov. 26, 2002, to Kelly, et al. discloses an Ultra Reduced NOx Burner System and Process.
  • Fuel Modification Fuel Rich Reactor (FMFRR) zone gases are brought together with products from a Fuel Lean Reactor (FMR) zone in a low temperature burnout and NOx reduction reactor zone.
  • the fuel modification fuel rich reactor stabilizes combustion through recirculation of hot gases to the reactants.
  • Nitrogenous species decay reactions in the fuel rich zone controls the production of NOx.
  • the nitrogenous species from the fuel rich zone and the NOx from the fuel lean zone then react in the burnout zone at an optimal temperature and nitrogenous species mix where
  • NOx is minimized. Temperature in all zones, and in particular the burnout zone, can be controlled by furnace gas entrainment, induced flue gas recirculation, forced flue gas recirculation and active cooling by radiative and/or convective heat transfer. NOx can be even further reduced by introducing ammonia, or a like amine species, into the low temperature burnout zone. By balancing combustion and emissions control reactions over several zones, low emissions can be achieved under good flame stability, turndown, heat transfer and noise characteristics.
  • a novel fuel nozzle for use in a burner.
  • the fuel nozzle comprises a main body having an inlet end and an outlet end and defining a longitudinal axis extending between the inlet end and the outlet end.
  • a fuel passageway has a fuel receiving inlet, and a fuel emitting outlet for delivering fuel to a mixing chamber of the burner.
  • a first air flow channel has an inlet, and an outlet disposed adjacent the fuel emitting outlet for delivering air to the mixing chamber. The portion of the first air flow channel adjacent the outlet is oriented obliquely to the longitudinal axis.
  • a novel fuel nozzle for use in a burner.
  • the fuel nozzle comprises a main body having an inlet end and an outlet end and defining a longitudinal axis extending between the inlet end and the outlet end.
  • a fuel passageway has a fuel receiving inlet, and a fuel emitting outlet for delivering fuel to a mixing chamber of the burner.
  • a first air flow channel is disposed on the exterior of the elongate main body, and has an inlet, and an outlet disposed adjacent the fuel emitting outlet for delivering air to the mixing chamber.
  • the fuel nozzle for use in a burner.
  • the fuel nozzle comprises a main body having an inlet end and an outlet end and defining a longitudinal axis extending between the inlet end and the outlet end.
  • a fuel passageway has a fuel receiving inlet, and a fuel emitting outlet for delivering fuel to a mixing chamber of the burner.
  • a first air flow channel has an inlet, and an outlet disposed adjacent the fuel emitting outlet for delivering air to the mixing chamber.
  • a second air flow channel has an inlet, and an outlet disposed adjacent the fuel emitting outlet for delivering air to the mixing chamber.
  • the first air flow channel and the second air flow channel generally surround the fuel passageway.
  • FIG. 1 is a sectional side elevational view of the first preferred embodiment of the fuel nozzle according to the present invention, installed in a burner;
  • FIG. 2 is a perspective view of the first preferred embodiment of the fuel nozzle installed in the burner as shown in FIG. 1 ;
  • FIG. 3 is a side elevational view of the fuel nozzle of FIG. 2 ;
  • FIG. 4 is a front elevational view of the fuel nozzle of FIG. 2 ;
  • FIG. 5 is a rear elevational view of the fuel nozzle of FIG. 2 ;
  • FIG. 6 is a sectional side elevational view of the fuel nozzle of FIG. 2 , taken along section line 6 - 6 of FIG. 5 ;
  • FIG. 7 is a side elevational view of a second preferred embodiment of the fuel nozzle according to the present invention.
  • FIG. 8 is a sectional side elevational view similar to FIG. 7 , but with the nozzle tip removed from the nozzle body.
  • FIGS. 1 through 8 of the drawings it will be noted that FIGS. 1 through 6 are directed to a first preferred embodiment of the fuel nozzle according to the present invention, and FIGS. 7 and 8 are directed to a second preferred embodiment of the fuel nozzle according to the present invention.
  • FIGS. 1 through 6 show a first preferred embodiment of the fuel nozzle according to the present invention, as indicated by general reference numeral 50 , for use in a burner 20 , such as the burner 20 shown in FIG. 1 .
  • air is used to describe air received from a pressurized or compressed source of air but that also oxygen from a pressurized or compressed source of oxygen could be used. If a source of air is used, the oxygen in the air is reacted with a fuel such as propane, natural gas, and so on. The nitrogen in the air is merely separated from the oxygen upon combustion. It is also contemplated that hydrogen could be used along with the oxygen.
  • the substantially straight fuel nozzle 50 comprises an elongate main body 55 having an inlet end 56 and an outlet end 57 , and is substantially circular in cross-section.
  • the main body 55 defines a longitudinal axis “L” extending between the inlet end 56 and the outlet end 57 .
  • the fuel nozzle 50 has a substantially straight fuel passageway 58 centrally disposed in the elongate main body 55 .
  • the substantially straight fuel passageway 58 has a fuel receiving inlet 53 and a fuel emitting outlet 54 for delivering fuel to a mixing chamber 80 of the burner 20 , by passing a flow of fuel from the fuel receiving inlet 53 to the fuel emitting outlet 54 .
  • the fuel emitting outlet 54 actually comprises a first fuel emitting outlet 54 a, a second fuel emitting outlet 54 b, a third fuel emitting outlet 54 c , a fourth fuel emitting outlet 54 d, a fifth fuel emitting outlet 54 e, and a sixth fuel emitting outlet 54 f.
  • the first fuel emitting outlet 54 a, the second fuel emitting outlet 54 b, the third fuel emitting outlet 54 c, the fourth fuel emitting outlet 54 d, the fifth fuel emitting outlet 54 e, and the sixth fuel emitting outlet 54 f are each oriented at an angle of about ten degrees with respect to the longitudinal axis “L”, which has been found to disperse the fuel fully for ready evaporation by the air. Any other suitable angle may alternatively be used.
  • the elongate main body 55 comprises a narrow back portion 55 a having a circular cross-section, a wider front portion 55 b having a circular cross-section, and a sloped portion 55 c interconnecting the narrow back portion 55 a and the wider front portion 55 b.
  • the fuel receiving inlet 53 is disposed at the inlet end 56 and the fuel emitting outlet 54 is disposed at the outlet end 57 .
  • the sloped portion 55 c of the fuel nozzle 50 engages in sealing contact with a co-operating receiving surface 21 on the main body of the burner 20 .
  • the fuel nozzle 50 also comprises an external rear portion 51 that projects rearwardly from the back end 26 of the main body 22 of the burner 20 .
  • the external rear portion 51 of the fuel nozzle 50 is threaded to accept a co-operating nut 52 thereon, to thereby retain the fuel nozzle 50 in place in the main body 32 .
  • first air flow channel 90 a In order to permit air flow from a source of compressed air (not specifically shown) to the mixing chamber 80 of the burner 20 , there is a first air flow channel 90 a, a second air flow channel 90 b, a third air flow channel 90 c, a fourth air flow channel 90 d, and a fifth air flow channel 90 e. It has been found that it is preferable to have this number of air flow channels for the purpose of even air flow and distribution there are two or more air flow channels 90 . Any suitable number of air flow channels 90 could be used depending on the specific application of the burner 20 , the size of the burner 20 and the fuel nozzle 50 , and so on. Various fuel nozzles according to the present invention have been tried, including from two air flow channels 90 on up. It has been found that each specific number of air flow channels might have its own advantages and disadvantages.
  • Each of the first, second, third, fourth and fifth air flow channels 90 a, 90 b, 90 c, 90 d, 90 e has an inlet 91 , and an outlet 92 disposed adjacent the fuel emitting outlet 54 for delivering air to the mixing chamber 80 of the burner 20 .
  • the portion 93 of each of the first air flow channel 90 a, the second air flow channel 90 b, the third air flow channel 90 c, the fourth air flow channel 90 d, and the fifth air flow channel 90 e adjacent the outlet that air flow channel is oriented obliquely to the longitudinal axis “L”.
  • substantially all of the first air flow channel 90 a , the second air flow channel 90 b, the third air flow channel 90 c , the fourth air flow channel 90 d, and the fifth air flow channel 90 e is oriented obliquely to the longitudinal axis “L”. Even more specifically, each of the first air flow channel 90 a, the second air flow channel 90 b, the third air flow channel 90 c, the fourth air flow channel 90 d, and the fifth air flow channel 90 e is helically shaped. Each of the plurality of helically shaped air flow channels 90 is substantially parallel to adjacent helically shaped air flow channels 90 . The helically shaped air flow channels 90 are preferably disposed on the exterior of the fuel nozzle 50 .
  • the inlet 91 of the first air flow channel 90 a has a cross-sectional area that is greater than the cross-sectional area of the outlet 92 of the same first air flow channel 90 a; the inlet 91 of the second air flow channel 90 b has a cross-sectional area that is greater than the cross-sectional area of the outlet 92 of the same second air flow channel 90 b; the inlet 91 of the third air flow channel 90 c has a cross-sectional area that is greater than the cross-sectional area of the outlet 92 of the same third air flow channel 90 c; the inlet 91 of the fourth air flow channel 90 d has a cross-sectional area that is greater than the cross-sectional area of the outlet 92 of the same fourth air flow channel 90 d; the inlet 91 of the fifth air flow channel 90 e has a cross-sectional area that is greater than the cross-sectional area of the outlet 92 of the same fifth air flow channel 90 e.
  • the ratio of the cross-sectional area of the inlet 91 of the first air flow channel 90 a to the cross-sectional area of the outlet 92 of the same first air flow channel 90 a is about 1.6 to 1; the ratio of the cross-sectional area of the inlet 91 of the second air flow channel 90 b to the cross-sectional area of the outlet 92 of the same second air flow channel 90 b is also about 1.6 to 1; the ratio of the cross-sectional area of the inlet 91 of the third air flow channel 90 c to the cross-sectional area of the outlet 92 of the same third air flow channel 90 c is also about 1.6 to 1; the ratio of the cross-sectional area of the inlet 91 of the fourth flow channel 90 d to the cross-sectional area of the outlet 92 of the same fourth air flow channel 90 d is also about 1.6 to 1; and the ratio of the cross-sectional area of the inlet 91 of the fifth air flow channel 90 e to the cross-sectional area of the outlet 92 of the
  • the ratio of about 1.6 to 1 can be more accurately expressed as the golden ratio, also known as the golden number, which is often denoted by the Greek letter PHI (q) and is determined by the mathematical expression (1+ ⁇ 5)/2, which is approximately equal to 1.618033987.
  • each of the five air flow channels 90 decreases from the inlet 91 to the outlet 92 . More specifically, it is also preferable that the width of each of the five air flow channels 90 decreases from the inlet 91 to the outlet 92 , for ease of manufacturing, while the depth remains constant. It is quite permissible for the depth of the five air flow channels 90 to also decrease from the inlet 91 to the outlet 92 , either additionally to the decrease in width of the channels 90 , or instead of the decrease in width of the channels 90 .
  • the wider front portion 55 b of the fuel nozzle 50 contacts the constant cross-section front portion 24 of the burner 20 in sealed relation. Accordingly, air must pass through the helically shaped air flow channels 90 in order to reach the mixing chamber 80 .
  • air within the burner 20 must pass through the first air flow channel 90 a, the second air flow channel 90 b, the third air flow channel 90 c, the fourth air flow channel 90 d, and the fifth air flow channel 90 e immediately before being emitted to the mixing chamber 80 of the burner 20 .
  • the fast flow of air then passes by the outlet end 57 of the elongate main body 55 of the substantially straight fuel nozzle 50 and past the fuel nozzle tip 60 , to then mix with the fuel emanating from the fuel nozzle tip 60 .
  • the air exiting the outlets 92 of each of these five air flow channels 90 travels in a fast-swirling helical pattern along the mixing chamber 80 towards the combustion chamber 82 , and then even in the combustion chamber 82 .
  • the swirling of the air in the combustion chamber 82 provides for a substantially lengthened path of travel for the air within the combustion chamber 82 , as compared to the actual length of the combustion chamber 82 . In this manner, there is a significantly longer dwell time for the air, and also the fuel that the air has “picked up”.
  • flame temperature of the burner 20 of the present invention can readily be in excess of 2000 degrees, and produce a stack temperature of about 400 degrees Fahrenheit, which is a drop of 1600 degrees Fahrenheit that has gone into elevating the temperature of the object to be heated.
  • flame temperature of about 1600 degrees Fahrenheit and a stack temperature of about 800 degrees Fahrenheit which transfer to only 800 degrees temperature difference that is used to heat an object.
  • FIGS. 7 and 8 show a second preferred embodiment of the fuel nozzle according to the present invention, as indicated by the general reference numeral 250 .
  • the second preferred embodiment of the fuel nozzle 250 is similar to the first preferred embodiment of the fuel nozzle 50 except that the fuel nozzle 250 further comprises a fuel nozzle tip 260 mounted in removable and replaceable relation in the outlet end 257 of the elongate main body 255 of the fuel nozzle 250 .
  • the fuel nozzle tip 260 is mounted in removable and replaceable relation as described, to permit ready replacement of the fuel nozzle tip 260 in the event of damage, and also to permit selection of an appropriate fuel nozzle tip 260 for an end application, such as placement in a boiler, line heater, or furnace.
  • the present invention provides a fuel nozzle that causes a burner to burn fuel very efficiently, that produces minimal unwanted emissions, that can be used with various types of gaseous and liquid fuel, and that is cost effective, all of which features are unknown in the prior art.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
  • Filtering Of Dispersed Particles In Gases (AREA)
US12/564,369 2008-09-22 2009-09-22 Fuel nozzle for use in a burner Abandoned US20100167222A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US12/564,369 US20100167222A1 (en) 2008-09-22 2009-09-22 Fuel nozzle for use in a burner

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Application Number Priority Date Filing Date Title
US9920008P 2008-09-22 2008-09-22
US12/564,369 US20100167222A1 (en) 2008-09-22 2009-09-22 Fuel nozzle for use in a burner

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US20100167222A1 true US20100167222A1 (en) 2010-07-01

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US12/564,369 Abandoned US20100167222A1 (en) 2008-09-22 2009-09-22 Fuel nozzle for use in a burner
US12/564,337 Abandoned US20100154771A1 (en) 2008-09-22 2009-09-22 Air-flow-controlling rear housing member

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US12/564,337 Abandoned US20100154771A1 (en) 2008-09-22 2009-09-22 Air-flow-controlling rear housing member

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US (2) US20100167222A1 (zh)
EP (2) EP2334985A4 (zh)
CN (3) CN104197331B (zh)
AU (2) AU2009295222A1 (zh)
RU (2) RU2507447C2 (zh)
WO (3) WO2010031175A1 (zh)

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EP2334985A4 (en) 2014-08-06
US20100154771A1 (en) 2010-06-24
RU2011115779A (ru) 2012-10-27
AU2009295222A1 (en) 2010-03-25
WO2010031174A3 (en) 2010-05-14
RU2507447C2 (ru) 2014-02-20
AU2009295221A1 (en) 2010-03-25
EP2338000A4 (en) 2014-08-06
CN102224378B (zh) 2014-07-23
RU2011115778A (ru) 2012-10-27
WO2010031176A1 (en) 2010-03-25
EP2334985A2 (en) 2011-06-22
CN102224379B (zh) 2014-09-24
CN104197331A (zh) 2014-12-10
RU2509955C2 (ru) 2014-03-20
WO2010031174A2 (en) 2010-03-25
CN102224379A (zh) 2011-10-19
EP2338000A1 (en) 2011-06-29
CN104197331B (zh) 2017-07-07
WO2010031175A1 (en) 2010-03-25

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