US3720496A - Fuel burner - Google Patents

Fuel burner Download PDF

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Publication number
US3720496A
US3720496A US00128734A US3720496DA US3720496A US 3720496 A US3720496 A US 3720496A US 00128734 A US00128734 A US 00128734A US 3720496D A US3720496D A US 3720496DA US 3720496 A US3720496 A US 3720496A
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Prior art keywords
head
cylindrical member
air
conical portion
nozzle
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US00128734A
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English (en)
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E Briggs
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Desa International LLC
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Koehring Co
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Assigned to DESA INTERNATIONAL, INC., 2701 INDUSTRIAL DRIVE, BOWLING GREEN, KENTUCY, A CORP. OF DE. reassignment DESA INTERNATIONAL, INC., 2701 INDUSTRIAL DRIVE, BOWLING GREEN, KENTUCY, A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: KOEHRING COMPANY, 200 EXECUTIVE DRIVE, BROOKFIELD, WI., A CORP. OF DE.
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Assigned to GENERAL ELECTRIC CREDIT CORPORATION reassignment GENERAL ELECTRIC CREDIT CORPORATION ADDENDUM TO SECURITY AGREEMENT Assignors: DESA INTERNATIONAL INC.
Assigned to CONFEDERATION LIFE INSURANCE COMPANY reassignment CONFEDERATION LIFE INSURANCE COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DESA INTERNATIONAL, INC., A DE CORP
Assigned to CONFEDERATION LIFE INSURANCE COMPANY reassignment CONFEDERATION LIFE INSURANCE COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DESA INTERNATIONAL, INC.
Assigned to COPENHAGEN HANDELSBANK A/S (AKTIESELSKABET KJOEBENHAVNS HANDELSBANK) CAYMAN BRANCH reassignment COPENHAGEN HANDELSBANK A/S (AKTIESELSKABET KJOEBENHAVNS HANDELSBANK) CAYMAN BRANCH SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: DESA INTERNATIONAL, INC.
Anticipated expiration legal-status Critical
Assigned to DESA INTERNATIONAL, INC. reassignment DESA INTERNATIONAL, INC. TERMINATION AND RELEASE Assignors: COPENHAGEN HANDELSBANK A/S (NOW KNOW AS DEN DANSKE BANK)
Assigned to DESA INTERNATIONAL, INC. reassignment DESA INTERNATIONAL, INC. RELEASE AND TERMINATION Assignors: GENERAL ELECTRIC CAPITAL CORPORATION
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D17/00—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel

Definitions

  • ABSTRACT A burner nozzle projects a mixture of fuel oil and air into a burner tube fitted with an open ended flame retention head having the general configuration of a frustum of a cone the small end of which faces the nozzle and the large end of which abuts the interior wall of the burner tube.
  • the zone on the nozzle side and around the circumference of the conical flame retention head is supplied with air under pressure. Slots each having an outwardly inclined vane adjacent one of its margins extend longitudinally of the head and open at both the periphery and the small end of the head to direct air from the pressure zone into an axially swirling pattern of motion within the head.
  • Additional openings of circular configuration are disposed in a ring about the conical head in the vicinity of but spaced from its large end, and the slots terminate at individual ones of these circular openings.
  • the openings provide additional passages for directing air from the pressurized zone toward the axis of the head.
  • This invention relates to fuel burner apparatus ofthe type in which fuel in fluid form is projected from a nozzle and burned in a restricted combustion zone to provide heat for such applications as residential air conditioning and heating units or systems, water heaters, small steam generating systems, etc.
  • Nozzle type burners have heretofore been employed in various kinds of equipment and such burners have recognized advantages in the areas of structural simplicity, performance flexibility, etc. However, difficulties have been encountered in obtaining highly efficient air-fuel mixtures with such apparatus.
  • This invention has as its principal object the provision of a fuel burner capable of producing a small intense flame of high combustion efficiency.
  • a more particular object of the invention is the provision of an oil burner in which air is caused to flow in paths which assure an efficient air-oil mixture in a small combustion zone and which protect against the impingement of incompletely burned oil particles against surfaces of the apparatus.
  • a burner constructed in accordance with the invention includes a cylinder member or burner tube having an open outlet end, a nozzle coaxial with the burner tube for projecting fuel toward the open outlet end of the burner tube, a flame retention head within the burner tube and located in front of the nozzle, and means for establishing a zone of pressurized air on the nozzle side of the flame retention head.
  • the flame retention head is a thin walled member having the general configuration of a frustum of a cone. The large end of the cone has a diameter corresponding to that of the interior of the burner tube and it is mounted against 0 the wall of the tube. The smaller end of the coned head is disposed a short distance in front of the nozzle and is completely open and of a diameter such that the material issuing from the nozzle enters the interior of the flame retention head without contacting the walls thereof.
  • the interior of the flame retention head is constituted by a conical surface of revolution uninterrupted by inwardly protruding elements or portions.
  • longitudinal slots are located at regularly spaced intervals about the axis of the head, and each of these slots is open to the small end of the head.
  • the material of the head is bent outwardly at an angle along the margin of each of the slots to provide a series of vanes skewed relative to the axis of the head.
  • the flame retention head preferably includes addi tional air passages located near but spaced from its larger end.
  • These additional air passages may be simple holes the axes of which intersect the longitudinal axis of the flame retention head.
  • the holes preferably are spaced regularly about the circumference of the head and at least some of them may intersect the ends of the longitudinal slots remote from the small end of the head.
  • the additional air passing through the holes is driven directly into the flame area and minimizes flame expansion so that the flame is held in close proximity to the conical head.
  • This additional air also provides a shield for preventing impingement of raw or incompletely burned fuel against the walls of the downstream portions of the head and burner tube so as to minimize carbon deposits thereon.
  • the nozzle itself preferably is an aspirator nozzle of the type in which air under pressure is causedto swirl at high velocity through and out of a passage surrounding a centrally located fuel oil conduit. As the air issues from the nozzle end, it entrains oil particles and the oilair mixture is projected toward the outlet end of the burner tube.
  • the direction of swirl of the primary air issuing from the nozzle tip be opposite to the direction of swirl of the secondary air guided into the interior of the flame retention head by the outwardly inclined vanes at the margins of the longitudinal slots which extend to the small inlet end of the head.
  • This counterflow arrangement promotes oil droplet breakdown and efficient mixing of the air with the dispersed oil particles.
  • the spacing of the burner tip from the small end of the flame retention head and the sizes of the vanes of this portion of the head also are factors which are relevant in connection with obtaining maximum performance. It is preferred that the nozzle end be spaced from the small end of the flame retention head a distance such that the visible portion of the flame is located at or a short distance from the small end of the head.
  • the diameter of the small end of the head should be small, and the vane ends should be of substantial length and have substantial inclinations. The mass of swirling air flow achieved with such a construction is large and results in good performance.
  • the advantages of the novel burner of this invention are pronounced.
  • the flame produced is a small, bright yellow flame having the appearance of a vortex, and it has been found that an oil burner constructed in accordance with the invention requires a combustion zone volume of about one-third that required in installations where conventional oil burners are employed.
  • the invention reduces the amounts of incompletely burned fuel and prevents the formation of carbon deposits on the walls of the apparatus.
  • FIG. 1 is a perspective view of a water chiller for an air conditioning system, which water chiller includes a fuel burner constructed in accordance with the invention.
  • FIG. 2 is a horizontal cross sectional view, taken along the line 22 in FIG. 1 and illustrating a fuel burner unit according to the invention in relation to certain other components of the equipment of FIG. 1.
  • FIG. 3 is an elevational view, taken from the direction 3--3 in FIG. 2 with a vertical panel of the chiller housing being removed to reveal the components within the housing which cooperate to supply the burner with fuel and air.
  • FIG. 4 is a similar view taken along the line 44 in FIG. 3.
  • FIGIS is a vertical cross sectional view illustrating the relationship between the fuel burner assembly and the heat receiving chamber for the generator element of the chiller of FIG. 1.
  • FIG. 6 is an end elevational view of the burner assembly shown in FIGS. 2 and 5.
  • FIG. 7 is a plan view of this burner assembly.
  • FIG. 8 is a detailed cross sectional view, taken along the line 88 in FIG. 6 and illustrating an igniter component of the burner assembly.
  • FIG. 9 is a cross sectional view taken generally along the line 9-9 in FIG. 6, but illustrating a fuel supply to the nozzle head as being in this plane and illustrating in plan a flame retention head in the burner assembly.
  • FIG. 10 is a detailed cross sectional view, taken along the line 1010 in FIG. 9 and illustrating air flow and fuel passages in the nozzle component of the burner assembly.
  • FIG. 11 is a cross sectional view taken along the line 11-11 in FIG. 7 to show the inlet end of the flame retention head in elevation and to illustrate an auxiliary air supply fitting in cross section.
  • FIG. 12 is an end view of the auxiliary air supply fitting of FIG. 11 as it appears from the outer end thereof.
  • the water chiller 1 is a small unit operating on an absorption cycle to chill water piped to and from the unit as a part of a residential air conditioning system.
  • absorption cycles require the presence of a generator unit where relatively high pressures and temperatures are maintained and where an absorbed vapor such as ammonia is driven from a solution.
  • the vapor is then condensed to a liquid and passed through an expansion valve to an evaporator where it is disposed in heat receiving relationship to the water to be chilled.
  • the low pressure vapor then is again put into a liquid solution in an absorber, and the liquid is pumped back to the generator to complete the cycle.
  • the combustion apparatus for supplying heat to the generator of the chiller is made up of equipment components located near the bottom 3 of the chiller unit 1 and that these equipment components are arranged to be accessible at one side 4 of the housing 2 provided with a conventional access panel (not illustrated) which may be removed when it becomes desirable to inspect or service the equipment.
  • the heat receiver for the generator of the chiller is designated generally at 5. It includes metal housing components 6 lined with refractory material 7.
  • This heat receiver is in the form of a vertically oriented cylinder, and it will be understood that the main body of the generator 8 is disposed immediately above and coaxially with the heat receiver so that the heat supplied to the heat receiver is made available in an efficient way to the main heat transfer components of the generator.
  • These heat transfer components form no part of the present invention and are represented schematically at 9 in FIG. 5.
  • the vertical extent of heat receiver 5 may be on the order of 6 or 7 inches.
  • the combustion apparatus includes two basic assemblies, a burner assembly 10 supported by the heat receiver 5 and a supply assembly 11 spaced from the burner assembly and supported on the bottom 3 of the chiller housing 2. Fluid conduits and electrical cables connect the two assemblies together in a manner to be described more fully below.
  • the burner assembly 10 extends into an opening in the vertical wall of the heat receiver 5 as illustrated in FIGS. 2 and 5.
  • This burner assembly includes a nozzle body 12, provided with a fuel inlet fitting 14, a primary air inlet fitting 16, and also a fitting 18 through which supplementary or auxiliary air may be admitted.
  • the supply assembly for delivering the required fluids to the fittings l4, l6 and 18 includes a motor 20 held in place by a clamp system 22 and having driven output shaft means at both ends thereof.
  • the output at one end of the motor 20 serves to drive a primary air pump or compressor 24 of a vane type described more fully in US. Pat. No. 3,256,003 granted to Eugene C. Briggs on June 14, 1966.
  • the disclosure of such patent is incorporated herein by reference and the patent may be examined in order to gain a detailed understanding of the interior construction of the compressor 24. It will suffice here to point out that the compressor 24 receives air from the interior of the casing 2 of the chiller unit 1 and delivers the compressed air to the primary air inlet fitting 16 of the burner assembly through a line or conduit 26.
  • the compression achieved in the compressor 24 need not be high, it having been found that a pressure of about four pounds per square inch gauge ordinarily is sufficient.
  • the other output end of the motor 20 drives an aux iliary air blower unit indicated generally at 28 as a centrifugal pump.
  • This unit receives air through an axial opening (not illustrated) and delivers it at an increased pressure through a peripheral outlet to a hose 30 leading to the auxiliary air inlet fitting 18 of the burner assembly.
  • Fuel oil is supplied from a small piston-solenoid type fuel pump 32 on the supply assembly 11.
  • This pump includes an inlet fitting 34 to which a line from a suitable reservoir is attached. These latter elements are conventional and have not been illustrated in the drawings.
  • the output from the pump 32 is connected to a line 36 which leads to a regulator 38, and the regulator 38 is connected to the oil inlet fitting 14 of the fuel burner by way ofa line 40.
  • the fuel regulator 38 preferably is a demand regulator of the diaphragm valve type illustrated and described in US. Pat. No. 3,298,418, granted to Eugene C. Briggs on Jan. 17, 1967, the disclosure of which patent is incorporated herein by reference.
  • This regulator 38 supplies constant fuel flow to the nozzle regardless of head variations, so long as the air system is operating properly to impose a demand for the presence of a supply of fuel within the nozzle.
  • the regulator shuts off the flow when the primary air supply is interrupted, so that there is no danger of fuel being delivered to the nozzle after the conditions necessary for combustion have ceased to exist.
  • the electrical system for controlling the operation of the equipment may be located at 42 in FIGS. 2 and 3. These controls are conventional in nature and need not be described in detail here.
  • the burner assembly includes an igniter component 44 connected to a cable 46 which leads into the control system and that the burner assembly also includes a detector 48 (e.g. a cadmium cell unit) which also is attached to a cable 50 leading to the control.
  • the igniter component 44 operates to provide an ignition arc in the beginning of a burner operation cycle, and the detector 48 operates to shut down the fuel supply in the event that the flame should go out unexpectedly.
  • the controls further serve to correlate the operations of the motor 20 and the fuel pump 32 with the requirements of the burner and the system being served by the burner.
  • a cylindrical member or burner tube 52 extends through a cylindrical opening in the wall of the heat receiver 5 and is attached to a mounting member 54 detachably secured to the exterior of the heat receiver 5 by such conventional means 56 as screws or the like.
  • the inner or outlet end 58 of the burner tube 52 is in open communication with the interior of the heat receiver 5. However, the outer end of the burner tube is closed by a member 60 having a central opening for receiving the nozzle structure.
  • the nozzle head or body element 12 fits closely within the central opening in the closure 60 and may be permanently secured to the closure in an appropriate manner for sealing the opening as best shown in FIG. 9.
  • the nozzle body 12 is hollow and includes both a chamber 62 communicating with the oil inlet fitting l4 and a chamber 64 communicating with the primary air inlet fitting 16.
  • the front end of the nozzle body 12 is provided with an internally threaded central opening for cooperation with an externally threaded rear end portion of a nozzle tip 66.
  • a nozzle core element 68 is disposed centrally of the assembly and fits closely within an opening at the rear end of the nozzle tip and within a seal 70 separating the oil chamber 62 from the air chamber 64.
  • the axial position of the core 68 within the body 12 and the-attached tip 66 is established by a radial collar 72 on the core and a compression spring '74 arranged to press the core forwardly until a forwardly directed face of the collar 72 abuts against the rear end of the threaded portion of the nozzle tip 66.
  • the front end portion of the nozzle core element 68 has an external diameter less than the diameter of the opening in the corresponding portion of the tip 66 to provide therebetween another air chamber 76.
  • the core element 68 additionally includes at its front end a tip portion 82 which protrudes into the orifice 80, and an oil passage 84 leads through the center of the core element 68 from the chamber 62 to the orifice 80.
  • the swirling air flow from the chamber 76 out of the orifice 80 in the nozzle tip produces an aspiration effect which causes oil to flow through the passage 84.
  • a mixture of air and atomized oil is projected forwardly from the nozzle tip toward the outlet end 58 of the burner tube 52.
  • a flame retention head 86 is disposed a short distance in front of the outlet end of the nozzle tip as illustrated in FIGS. 5 and 9.
  • This head 86 is formed of heat resistant thin wall material such for example as thirty gauge stainless steel. Its shape is basically that of a frustum of a cone and it is preferred that the cone angle (i.e. inclination relative to axis) be on the order of about 45 degrees.
  • the small end of the coned flame retention head 86 faces toward the nozzle tip 66, while the larger end faces toward the outlet end 58 of the burner tube 52.
  • the diameter of the larger end of the head 86 corresponds to the internal diameter of the burner tube 52, and an attachment ring 88 of cylindrical configuration seals this end of the head against the wall of the tube.
  • the igniter component 44 is threaded into a tubular mount 90 carried by a rear portion of the burner tube 52.
  • This igniter component 44 includes electrodes 92 and 94 which project into the interior of the tube 52 to a location in the vicinity of the outlet end of the nozzle tip 66. Current may be supplied to the electrodes 92 and 94 at sufficient voltage to strike an are between these electrodes when it is desired to initiate a burning cycle.
  • auxiliary air inlet fitting 18 (FIGS. 5, 7, l1 and 12).
  • This fitting 18 is a large diameter tube 96 which mates with a correspondingly sized opening in the burner tube 52.
  • the axis of the tube 96 is transverse to the axis of the burner tube 52 and air flow control means 98 extend centrally through the tube 96.
  • the air flow control means 98 is in the form of a pair of sheet members 100 and 102.
  • the outer ends 104 and 106 of the sheet members 100 and 102 are generally planar and extend parallel to the axis of the burner tube 52. These outer end portions of the sheet members are disposed in abutting relationship to each other to minimize the obstruction offered thereby to the passage of auxiliary air into the burner tube 52.
  • the inner end portions 108 and 110 of the sheet members 100 and 102 have special configurations for effecting distribution of the auxiliary air through the burner tube zone 112 at the rear and about the exterior of the flame retention head 86.
  • Each of the sheet member inner end portions 108 and 110 is curved outwardly (FIG. 11) and each is provided with tapered front and rear edges 109 and with a multiplicity of holes 111 as illustrated in FIG. 12. With this construction, some air is deflected in a counterclockwise direction (as viewed in FIG.
  • auxiliary air openings 114 through the coned flame retention head 86 is located near the larger end of the head. These openings 114 are circular holes regularly spaced about the circumference of the head. Although there are fourteen of the holes 114 in the illustrated embodiment, it will be understood that the number of holes provided in any given instance will be determined on the basis of the air requirements for efficient combustion of fuel at the rate appropriate for the system in which the burner is used.
  • the head portion 86 also is provided with a second set of auxiliary air passages or slots by slitting the head longitudinally from alternate ones of the holes 114 to the small rear end of the head. Thus, there are seven of these slits 116 in the illustrated embodiment.
  • Viewing the coned head 86 from its rear end (FIG. 1 l it will be seen with respect to each of the slits that the edge 118 thereof which trails in a counterclockwise sense lies in a longitudinal plane containing the axis of the head and is not deflected from the coned shape. However, the material adjacent the opposite marginal edge 120 is bent outwardly along a bend line 122 to provide an inclined vane 124.
  • the opposite edges 118 and 120 of the slits 116 cooperate to define forwardly converging longitudinal slots or air passage mounts for receiving the pressurized air from the zone surrounding the flame retention head 86, and the inclined inner faces of the vanes 124 impart to the air flowing thereover a swirling pattern of motion about and along the axis of the burner tube 52. Since the slits extend all the way to the completely open small end of the coned flame retention head 86, air may move to the inner flow-controlling surfaces of the vanes 124 not only from the zone at the circumference of the coned head but also from the zone immediately behind the head.
  • the swirling action is imparted to substantial masses of flowing air without any abrupt flow direction changes and in the absence of any obstructions to flow into the zones of action of the vanes.
  • the interior of the coned head 86 is unobstructed by inward protrusions which would obstruct the spiral flow established by the vanes 124.
  • the larger diameter of this coned head 86 is 2 ,4 inches, the angle of inclination or cone angle is 45, and the axial extent of the cone (distance between large and small ends of cone as projected onto a plane parallel to axis) is twenty-six thirty seconds inch.
  • the holes 114 have diameters of about nine thirty-seconds inch and have axes located about twenty-nine thirty-seconds inch forwardly of the rear end of the head 86 as measured along the sloping cone wall.
  • the angular extent of those rear edge portions 126 of the coned head 86 which are not bent outwardly to form the vanes 124 is slightly greater than
  • the rear end edges 128 of the vanes 124 extend outwardly at such angles that the juncture points of these edges 128 with the slit edges 120 define a circle having a diameter of about 1 15/32 inches, and both the widths and the angles of inclination of the vanes relative to the coned surface of revolution decrease as one proceeds forwardly from the rear end of the head.
  • the igniter M is energized to strike an arc between the igniter electrodes 92 and 94 located in the vicinity of the nozzle tip 66, air is supplied to both the primary air fitting l6 and the secondary air fitting l8, and oil is made available to the fuel fitting 14 on the nozzle body 12.
  • the igniter 44 is deenergized and remains idle until it is desired to start a new burning cycle.
  • the primary air is driven through the inclined passages 78 in the collar portion 72 of the nozzle core 68 and swirled forwardly and clockwise about the axis of the nozzle to issue from the orifice 80 in the nozzle tip 66. This produces an aspirating effect and tiny oil particles drawn from the passage 84 of the nozzle core are mixed with the stream of air issuing from the nozzle tip.
  • the supplementary air distributed through the zone 112 behind the flame retention head 86 follows several paths relative to the stream issuing from the nozzle tip 66. Some of the supplementary air will of course pass directly through the open rear end of the flame retention head along with the stream issuing from the nozzle. Additional increments of supplemental air are acted upon by the vanes to produce a swirling flow having a counter clockwise direction as viewed from the rear of the retention head. This flow exerts a confining effect upon the flame in a radial sense, scours the interior surface portions of the flame retention head 86, and further improves the air-fuel mixture in the flame area. In this latter connection, it is noted that the direction of swirl imparted by the vanes 124 is opposite to the direction of swirl provided by the passages 78 in the air channel of the nozzle, thereby promoting more efficient mixing.
  • Substantial additional increments of supplementary air are driven through the holes 114 toward and along the central axis to further confine the flame and carry the combustion of the fuel to completion.
  • This air flow through the holes 114 also provides a shield for the cooler metal surfaces located downstream so that these surfaces are protected against carbon deposits.
  • the illustrated embodiment of the invention is particularly adapted for the burning of oil or other liquid fuel, it will be appreciated that the invention also is suitable for use in the burning of gaseous fuels.
  • the vastly improved air-fuel mixtures achieved by the structures of the invention contribute to the efficiency of, combustion of gaseous fuel in the same manner they do for liquid fuel.
  • a fuel burner comprising:
  • a fuel nozzle adjacent the member inlet and generally coaxial with said cylindrical member and having an outlet opening spaced from the outlet end of said cylindrical member;
  • a flame retention head having a maximum diameter generally corresponding to the diameter of the in terior of said cylindrical member and including a hollow, open ended, generally conical portion having a concave interior surface uninterrupted by radial protrusions therefrom, said flame retention head being mounted within said cylindrical member with the smaller end of said conical portion facing said nozzle and being disposed in generally coaxial relationship with respect thereto;
  • said flame retention head further including means defining a first set of auxiliary air passages therethrough regularly spaced about the axis of said conical portion for admitting air from said zone to the interior of said conical portion and for guiding air flowing through said passages into a swirling pattern of motion about and along the axis of said head, each of the auxiliary air passages of said first set being formed by a slot communicating with and extending forwardly from the small open end of said conical portion, one marginal edge of the slot being located in a plane containing the axis of the flame retention head, and the opposite marginal edge of the slot being bent outwardly at an angle with respect to the first-mentioned marginal edge.
  • a fuel burner according to claim 1 wherein said conical portion of said flame retention head is additionally provided with a second set of airinlet passages formed by generally round holes therethrough, one of said holes being disposed in intersecting relation to the forward end of each of said slots.
  • a fuel burner according to claim 2 wherein the number of holes forming said second set of air passages is a multiple of the number of said slots forming said first set of air passages and wherein said holes are regularly spaced about the circumference of said conical portion.
  • An oil burner comprising:
  • an aspirator nozzle generally coaxial with said cylindrical member and having an outlet opening spaced from the outlet end of said cylindrical member, said nozzle including means for directing primary air in a spiral path to said opening and an axial oil passage leading to said opening so that oil is drawn through said passage and projected forwardly from the nozzle as an atomized spray;
  • said material being formed into a generally conical section coaxial with said cylindrical member, said conical section having a large end the diameter of which corresponds to the inner diameter of said cylindrical member and a small end defining an unobstructed opening facing the outlet end of said nozzle, said head having a ring of regularly spaced holes therethrough at a location close to but spaced from the large end of said conical section and the material of said conical section being slit longitudinally from at least some of said holes to the small end of the conical section, portions of the material of said conical section each bound by an edge of one of said slits and by an inclined bend line converging toward such edge from the small end of the conical section being bent outwardly along said bend lines to form vanes, all of said vanes having inner surfaces inclined in the same direction about the axis of the head for imparting a swirling motion to auxiliary air passing along said surfaces and into the interior of the head.
  • a fuel burner comprising:
  • a generally cylindrical member within which comflame retention head of thin material disposed bustion may occur, said member having an inlet and open outlet end;
  • a fuel nozzle adjacent said inlet and generally coaxial with said cylindrical member and having an outlet opening spaced from the outlet end of said cylindrical member;
  • a flame retention head having a maximum diameter generally corresponding to the diameter of the interior of said cylindrical member and including a hollow, open ended, generally conical portion having a concave interior surface uninterrupted by radial protrusions therefrom, said flame retention head being mounted within, said cylindrical member with the smaller end of'said conical portion defining an unobstructed opening facing said nozzle and being disposed in generally coaxial relationship with respect thereto;
  • means for supplying air under pressure to a zone surrounding the exterior of said conical portion of said flame retention head and in open communication with said unobstructed opening at the smaller end of said conical portion of said flame retention sai il fl ame retention head being further provided with a set of auxiliary air slots therethrough regularly spaced about the axis of said conical portion for admitting air from said zone to the interior of said conical portion, each of said slots being in open communication with and extending forwardly from the small open end of said conical portion, and vane means adjacent said slots for guiding air flowing toward the interior of said conical portion into a swirling pattern of motion about and along the axis of said head.
  • said conical portion of said flame retention head additionally includes means defining a second set of auxiliary air passages regularly spaced about the axis of said conical portion and being located near but spaced from the large end of said conical portion, said passages of said second set having axes intersecting the longitudinal axis of said head for directing air from said zone toward and along the axis of said head.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)
  • Spray-Type Burners (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
US00128734A 1971-03-29 1971-03-29 Fuel burner Expired - Lifetime US3720496A (en)

Applications Claiming Priority (1)

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US12873471A 1971-03-29 1971-03-29

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US00128734A Expired - Lifetime US3720496A (en) 1971-03-29 1971-03-29 Fuel burner

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US (1) US3720496A (fr)
CA (1) CA940818A (fr)
DE (1) DE2212321A1 (fr)
FR (1) FR2131697A5 (fr)
GB (1) GB1378307A (fr)

Cited By (12)

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WO1994027090A1 (fr) * 1993-05-14 1994-11-24 Cleveland Range, Inc. Systeme de bruleurs a gaz combustible
US5433601A (en) * 1992-03-21 1995-07-18 Deutsche Forschungsanstalt Fuer Luft- Und Raumfahrt E.V. Deposit-free burner
US5848585A (en) * 1996-02-02 1998-12-15 The Coleman Company, Inc. Portable space heater
US6142141A (en) * 1997-05-05 2000-11-07 The Coleman Company, Inc. Airflow diffuser for use with a forced-air space heater and a forced-air space heater using the same
US6651912B2 (en) * 2000-02-03 2003-11-25 Corning Incorporated Refractory burner nozzle with stress relief slits
US20050079458A1 (en) * 2003-10-13 2005-04-14 Webasto Ag Heater with an atomizer nozzle
US20070107642A1 (en) * 2005-11-14 2007-05-17 Johnson J E Fuel ignition systems
US20070264602A1 (en) * 2006-01-26 2007-11-15 Frenette Henry E Vapor fuel combustion system
US20070266591A1 (en) * 2006-05-18 2007-11-22 R.P. Scherer Technologies, Inc. Nozzle structure
US20100282238A1 (en) * 2008-08-18 2010-11-11 Meishun He Jet type gas cooker
US9657938B2 (en) 2014-02-07 2017-05-23 Eugene R. Frenette Fuel combustion system
US9874349B2 (en) 2015-04-03 2018-01-23 Eugene R. Frenette Fuel combustion system

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US2796118A (en) * 1954-07-21 1957-06-18 Hanck Mfg Co Burner for tube firing
US3245457A (en) * 1962-11-07 1966-04-12 Hunter Method of igniting liquid fuel

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Publication number Priority date Publication date Assignee Title
US1959521A (en) * 1931-03-21 1934-05-22 Bolt Frederic Leslie Air director for liquid fuel or powdered fuel furnaces
US2665748A (en) * 1949-05-27 1954-01-12 Frank H Cornelius Fuel burner
US2796118A (en) * 1954-07-21 1957-06-18 Hanck Mfg Co Burner for tube firing
US3245457A (en) * 1962-11-07 1966-04-12 Hunter Method of igniting liquid fuel

Cited By (17)

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Publication number Priority date Publication date Assignee Title
US5433601A (en) * 1992-03-21 1995-07-18 Deutsche Forschungsanstalt Fuer Luft- Und Raumfahrt E.V. Deposit-free burner
US5441405A (en) * 1993-05-14 1995-08-15 Cleveland Range, Inc. Power gas burner system
WO1994027090A1 (fr) * 1993-05-14 1994-11-24 Cleveland Range, Inc. Systeme de bruleurs a gaz combustible
US5848585A (en) * 1996-02-02 1998-12-15 The Coleman Company, Inc. Portable space heater
US6142141A (en) * 1997-05-05 2000-11-07 The Coleman Company, Inc. Airflow diffuser for use with a forced-air space heater and a forced-air space heater using the same
US6651912B2 (en) * 2000-02-03 2003-11-25 Corning Incorporated Refractory burner nozzle with stress relief slits
US20050079458A1 (en) * 2003-10-13 2005-04-14 Webasto Ag Heater with an atomizer nozzle
US20090233250A1 (en) * 2005-11-14 2009-09-17 Thermetic Products, Inc. Fuel ignition systems
US20070107642A1 (en) * 2005-11-14 2007-05-17 Johnson J E Fuel ignition systems
US7886675B2 (en) 2005-11-14 2011-02-15 Thermetic Products, Inc. Fuel ignition systems
US20070264602A1 (en) * 2006-01-26 2007-11-15 Frenette Henry E Vapor fuel combustion system
US7575182B2 (en) * 2006-05-18 2009-08-18 R.P. Scherer Technologies, Inc. Nozzle structure
US20070266591A1 (en) * 2006-05-18 2007-11-22 R.P. Scherer Technologies, Inc. Nozzle structure
US20100282238A1 (en) * 2008-08-18 2010-11-11 Meishun He Jet type gas cooker
US8857423B2 (en) * 2008-08-18 2014-10-14 Meishun He Jet type gas cooker
US9657938B2 (en) 2014-02-07 2017-05-23 Eugene R. Frenette Fuel combustion system
US9874349B2 (en) 2015-04-03 2018-01-23 Eugene R. Frenette Fuel combustion system

Also Published As

Publication number Publication date
FR2131697A5 (fr) 1972-11-10
GB1378307A (en) 1974-12-27
DE2212321A1 (de) 1972-10-12
CA940818A (en) 1974-01-29

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