US3511589A - Gas burner - Google Patents

Gas burner Download PDF

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Publication number
US3511589A
US3511589A US690299A US3511589DA US3511589A US 3511589 A US3511589 A US 3511589A US 690299 A US690299 A US 690299A US 3511589D A US3511589D A US 3511589DA US 3511589 A US3511589 A US 3511589A
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United States
Prior art keywords
burner
ports
faces
face
manifold
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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
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US690299A
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English (en)
Inventor
Charles W Rothhaar
Guy Richard Harter
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Maxon Premix Burner Co Inc
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Maxon Premix Burner Co Inc
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Publication date
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Publication of US3511589A publication Critical patent/US3511589A/en
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Classifications

    • 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
    • F23D14/34—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2209/00—Safety arrangements
    • F23D2209/20—Flame lift-off / stability

Definitions

  • a manifold which denes an interior fuel conduit, is provided with burner face means having ports communicating with the conduit.
  • the ports and the face means are cooperatively oriented to establish an interlaced flame pattern.
  • a pair of aerodynamic projections on the manifold upstream of the burner face means serve to pre- ⁇ vent the formation of a fluid barrier about the face means when the burner is operated in a moving air stream.
  • This invention concerns gas burner systems and, more particularly, an improved burner unit adapted to burn airgas fuel mixtures. It is a primary purpose of the invention to provide a burner unit capable of uniformly high performance under a wide range of operating conditions and in a variety of Iapplications, either in a moving air stream or in a static environment.
  • Gas burners are used in a variety of applications including, for example, the heating of make-up air in industrial and commercial structures, supplying heated air for ovens and other recirculating industrial facilities, supplying heated air for non-recirculating drying systems, and ordinary direct heating applications. These typical applications ideally require a burner characterized by, among other things, a wide range of heat output (high turndown), good llame retention and ignition control, high maximum heat output with short flame length, system flexibility (i.e. the ability to satisfy many different industrial, commercial and institutional heating needs), and operating flexibility (i.e. the ability to provide satisfactory performance under adverse environmental or operational conditions).
  • the principal objective of the invention lies in the provision of a gas burner having -means for establishing a self-sustaining interlaced flame pattern, and aerodynamic means for improving operating performance.
  • a basic burner unit comprising a manifold which defines a conduit for the gas-air mixture.
  • burner face means having essentially opposed surface areas which are convergently inclined toward the center of the conduit.
  • Each of the surface areas includes one or more rows of ports communicating with the conduit, with the ports in one area being longitudinally staggered from those in the other area-to provide an interlaced flame pattern.
  • the ports in adacent rows may lbe of different dimensions to assist in reducing burner noise level.
  • Certain ports may have concentric counterbore depressions to assist in llame retention and sustain ignition.
  • the invention also contemplates the use of aerodynamic means to prevent formation of a uid barrier or seal about the combustion area, in moving air stream environments.
  • the basic burner unit may be fabricated in a variety of shapes and sizes to promote system flexibility.
  • FIG. 1 is a somewhat diagrammatic sectional view of an air heating installation employing an exemplary burner 'assembly constructed in accordance with the invention
  • FIG. 2 is an enlarged view of a portion of the installation depicted in FIG. 1;
  • FIG. 3 is a view taken on the line 3 3 of FIG. 2, lsjlliowing a front elevation of the exemplary burner assemy;
  • FIG. 4 is a somewhat diagrammatic view of an exemplary burner assembly in a direct heating application
  • FIG. 5 is a sectional View taken on the line 5 5 of FIG. 3;
  • FIG. 6 is a Vview similar to that of FIG. 2, showing a modified burner assembly
  • FIG. 7 is a sectional View taken on the line 7 7 of FIG. 6;
  • FIG. 8 is a sectional view similar to that of FIG. 5, taken on the line 8 8 of FIG. 7;
  • FIG. 9 is a perspective View of a perforated baffle member designed for use in accordance with the invention.
  • FIG. 10 is a top plan view of a portion of the burner assembly taken on the line 10-10 of FIG. 8, showing a straight burner unit and yassociated components;
  • FIG. 11 is an enlarged view of a portion of the burner unit depicted in FIG. 10;
  • FIG. 12 shows a transverse section of the burner unit taken on the line 12 12 of FIG. 11;
  • FIG. 13 is an enlarged fragmentary sectional View of a portion of a burner unit constructed in accordance with the invention.
  • the air heating installation depicted in FIG. 1 is illustrative of arrangements wherein a burner assembly 10 ⁇ is used to heat an air stream flowing in a duct 12.
  • the air stream may be a fresh air stream, in which case the duct might be connected to a fresh air inlet grille; or the duct 12 may be part of the recirculating duct-work of an industrial oven 14 or the like, as shown in FIG. 1.
  • the air stream is propelled through the duct 12 by a blower 16 which may, depending upon the nature of the installation, be located downstream of the burner assembly 10, or upstream as shown in FIG. 1.
  • FIG. l Included in diagrammatic form in the air heating installation of FIG. l is one of several types of air-gas mixers, e.g. a mixer 18, which may be employed to supply air-gas mixtures to the burner assembly 10.
  • the air may be ordinary fresh air, or any other gas containing oxygen in suilicient amounts to sustain combustion when mixed with the fuel gas.
  • a thermostat 20 is provided downstream of the burner assembly to regulate its firing rate in accordance with the sensed temperature.
  • the illustrated mixer 18 includes a fuel gas supply line 22 and an air inlet shutter 24.
  • a controller 26 is responsive to signals from t-he thermostat to actuate a valve in the mixer 18, thus regulating the volume rate of flow of mixed fuel from the mixer to the burner assembly 10 through a suitably supply line 28.
  • the moving air stream is assumed to be flowing through the duct 12 in the general direction shown by the arrows, thus passing the burner assembly 10 from left to right.
  • FIG. 4 depicts a typical burner assembly I0 as it might be used in a direct heating application, as for example, the heating of a vessel.
  • mixing apparatus 19 comprising a gas inlet line 23, an air inlet line 25, a chamber 27 and a proportional mixing tube 29, the latter being connected to the supply line 28.
  • the burner assembly 10 constitutes an interconnected array of individual burner units, including a centrally located straight burner unit 30 having a back inlet portion 32 for connection with the supply line 28. Also included in the array are a pai-r of T-shaped burner units 34 and four L-shaped burner units 36. Each of the L-shaped -unts 36 has its free end closed with a generally hemispherical end cap 38.
  • each of the burner units 30, 34 and 36 is provided at each of its open ends with an attachment flange 40, so that it can be attached to neighboring burner units or closed by the end cap 38 by means of suitable fasteners 42.
  • the air-gas mixture enters the back inlet portion 32 of the straight burner unit 30 and is dispersed by a generally rectangular baille plate 44 and smoothly and uniformly distributed throughout the remaining burner units 34 and 36 in the burner assembly 10.
  • FIG. 5 likewise shows the somewhat Y,
  • FIGS. 6 and 7 are similar to FIGS. 2 and 3, and depict several alternatively-shaped burner units arrayed to form a modified burner assembly 50.
  • the assembly S0 is shown mounted for operation in a moving air stream flowing in a circular duct 12, with an air-gas mixture entering through the supply line 28.
  • the modified burner assembly is made up of an X-shaped back inlet burner unit 52, a pair of X-shaped burner units 54 and a pair of straight burner units S6.
  • the burner units 52, 54 and 56 in the burner assembly 50 are bolted together at the attachment flanges 40, and the end caps 38 are employed to close the free, ends of the burner units 54 and S6.
  • FIG. 8 shows in more detail the manner in which the air-gas mixture enters the array of burner units comprising the burner assembly 5t).
  • the mixture from the supply line 28 enters an inlet portion 58 which is integrally formed on the back of the burner unit 52.
  • a modified form of perforated baflle member (shown in perspective in FIG. 9) is mounted in the burner unit 52 in front of the inlet portion S8.
  • the baille member 44 mounted in the straight inlet burner unit 3d FIG.
  • the baille member 60 serves to disperse the entering stream of fuel mixture and distribute it smoothly through le array of burner units comprising the burner assem-
  • burner units constructed in accordance with the present invention can be made in any number of shapes and sizes, thus permitting them to be easily and flexibly arrayed to produce a burner assembly of any desired size and configuration.
  • FIGS. I0 through l2 illustrate in greater detail an exemplary burner -unit embodying the features of the present invention.
  • the burn-er unit shown is the straight unit 56 illustrated in FIGS. 7 and 8, but it should be understood that all of the units 30, 34, 36, 50, 54 and 56 are constructed in accordance with the inventive features, and are merely differently shaped, some having inlet sections.
  • the burner unit 56 includes a manifold 70 which defines an interior fuel conduit 72. Associated with the front of the manifold are face means having suitable surface areas for accommodating burner ports. In this instance, the face means comprise a pair of bumer faces 74 which are convergently inclined toward the center of the fuel conduit 72.
  • the manifold 70, the burner faces 74 and the attachment ilanges 40 may be advantageously fabricated in a single casting of iron or other suitable material.
  • Each of the burner faces 74 includes two rows of ports 76 and 78 with the ports 76 being arranged in the rows adjacent the line of convergence between the burner faces 74 (the inner rows), and the ports 78 being arranged in the outer rows.
  • the ports 76 and 78 are preferably of circular cross section and are disposed with their longitudinal axes substantially normal to the burner faces 74, extending therethrough to communicate with the fuel conduit 72. Associated with each of the ports 78 in the outer rows are concentric counterbore depressions 80 in the burner faces 74.
  • the burner face means may assume other coniigurations.
  • the face means might be curved, or might comprise a series of planar surface elements,
  • the face means include at least a pair of essentially opposed surface areas (eg, the faces 74), and that the face means and ports be cooperatively oriented to establish an interlaced llame pattern.
  • the manifold 70 also includes a pair of integrally formed longitudinally extending aerodynamic projections 82 which function to prevent the formation of a fluid barrier or seal about the burner face means when the burner unit 56 is operated in a moving air stream, as will be described in greater detail hereinatfer.
  • the air-gas mixture enters the burner assembly 50 through the back inlet portion S8 of the X-shaped burner unit 52, and strikes the perforated baille member 60 (FIGS. 7 and 8), thus being distributed through the remaining units including the straight burner unit 56.
  • the mixture then passes from the conduit 72 of the burner unit 56 through the ports 76 and 78 in standing jets, where it is ignited and burned in the space adjacent the burner faces 74.
  • the hemispherical end caps 38 serve to absorb turbulence beyond the ported portion of the conduit 72, thereby inhibiting flash-back, i.e., ignition of the mixture within the conduit.
  • the ports in one of the burner faces 74 are longitudinally staggered with respect to the ports in the other burner face. As best shown in FIG. ll, this staggered relationship results in a llame pattern which is interlaced.
  • the flame pattern shown (in somewhat idealized form) is that which might be produced with the burner unit 56 being operated at a low to medium tiring rate.
  • the llames issuing from the ports 76 and 78 on one of the burner faces 74 make slight Contact ⁇ with the llames issuing from the other burner face. This aids in establishing cross ignition, and in maintaining ignition and flame retention.
  • the counterbore depressions 80 also serve to maintain ignition, as best illustrated in FIG. 13.
  • the increased -volume of the counterbore depression 80 surrounding the port 78 permits the formation of a negative-pressure pocket in the form of an annular space 84 disposed concentrically about the main jet of mixture 86 issuing from the port 78.
  • Flow in this volume 84 is turbulent and relatively slow, thus permitting easy ignition of the gas therein. In this manner a ring of ame is maintained about the main jet of mixture 86, and the ring in turn sustains ignition of the main jet.
  • the depth and diameter of the depression 80 may vary with respect to the diameter of the port 78, in practice it has been found that ignition is maintained most satisfactorily when the diameter of the depression 80 is from about two to about three times the diameter of the port 78, and when the depth of the depression is from about 75 to about 200% of the port diameter.
  • each of the burner faces 74 might include a longitudinal slot or depression running the length of the row of ports 78'. In this arrangement the width of the slot is about one and one-half to about three times the diameter of the ports 78, and the depth f the slot is again preferably in the range of 75% to 200% of the port diameter.
  • the ports 76 are preferably of a different diameter than the ports 78, so as to substantially diminish a condition of resonance, and the attendant increase in burner noise level or tone, which might result from identically sized ports.
  • the ports 76 in the inner rows are preferably larger than the ports 78 in the outer rows, so as to assist the aerodynamic projections 82 in preventing the formation of a fluid barrier or seal about the burner faces 74. In practice it has been found that these objectives will be achieved most successfully by maintaining the total area of the ports 76 in the range of from about one and one-half to two times the total area of the ports 78 (exclusive of the counterbore depressions 80).
  • each of the burner faces 74 might include, for example, an inner row of 24 ports 76 each having a diameter of about 0.154 inch and an outer row of 24 ports 78 each having a diameter of about 0.125 inch.
  • the counterbore depressions 80 associated with the ports 78 in the outer rows might have a diameter of about 6 inch and a depth of about 1/s inch, with the thickness of walls of the manifold 70 and the burner faces 74 bein-g about 1A inch and 'M6 inch, respectively.
  • the number and spacing of the rows, the number, size and spacing of the ports 76 and 78, the diameter and depth of the counterbore depressions 80, and the thickness of the manifold 70 and burnerV faces 74 can vary over wide limits, and will depend upon such factors as the desired heat release per linear foot of burner, the mixture supply pressure, the velocity of ignition, the amount of space available in each face for drilling and counterboring, etc.
  • a single port 78a at one end of the outer row in each of the burner faces 74 does not have a counterbore depression associated therewith, due to the fact that, in the construction illus- 6 trated in FIG. 10, the staggering of the ports does not permit sufficient space.
  • the projections 82 which in such case are upstream from the burner face means, operate aerodynamically to prevent the moving air stream from for-ming a fluid barrier or seal about the burner faces. It has been found that elimination of this barrier reduces the burner noise or tone and enhances heat release from the space between the burner face means.
  • the included angle of convergence between the burner faces 74 may also be significant in this regard. It has been found that, for most satisfactory operation this angle should be in the range of from about to about 100, and preferably about Larger angles result in increased suction in the flame area between the faces 74, and also render the burner faces more vulnerable to adverse elements in the moving air stream, thus impairing flame retention. On the other hand, smaller angles substantially reduce the potential heat release per foot of burner and likewise impair flame retention. Where other face means configurations are employed, the angular relationships may be adjusted accordingly.
  • the open configuration of the face means exposes the ports 76 and 78 and the depressions 80 for easy inspection and cleaning and, moreover, provides more space for drilling and counterboring than would a single fiat face.
  • the interlaced flame pattern produces a benecial scrubbing action on the face surfaces.
  • the aerodynamic projections 82 could be omitted if it were desired to construct a burner unit for use only in a static environment. Conversely, similar aerodynamic means could be advantageously employed to enhance the performance of ordinary prior burner units operating in moving air streams. In this connection, it should be understood that the precise shape and size of the projections 82 are not critical, so long as they serve to break the streamline ow of air past the sides of the manifold 70 and prevent the formation of a fluid barrier downstream of the burner face means.
  • a burner comprising: a manifold defining a fuel conduit; burner face means associated with said manifold including a pair of essentially opposed surface areas; and two rows of ports defined in each of said surface areas, the axes of the ports in one of said surface areas being essentially parallel to one another and to the other of said surface areas, the ports in one of said surface areas being spaced in longitudinally staggered relationship to those in the other of said areas, said spaced relationship being such that a full flame issuing fro-m a port in one of said areas makes no more than slight contact with adjacent flames issuing from ports in the other of said areas, the ports in the innermost row in each face being larger than those in the outermost row.
  • a burner comprising: a manifold defining a fuel conduit; a pair of burner faces on the exterior of said manifold convergently inclined to include an angle of about 90; and two rows of ports defined in each of said faces essentially normal thereto, the ports in one of said faces being staggered with respect to the ports in the other of said faces to form an interlaced but only slightly contacting ame pattern, the ports in one row in each face being of different diameter than the ports in the other row, the ports in the outer row in each face having associated therewith a depression formed in said face.
  • a system for obtaining heat from premixed gaseous fuel including mixing means for mixing said fuel, an array of connected burner units, inlet means for passing said fuel from said mixing means to said array of burner units, and end cap means for closing unconnected ends of said burner units, wherein each of said burner units cornprises: a manifold defining a fuel conduit; attachment means at each end of said manifold permitting attachment thereof to similar burner units or said end cap means; a pair of burner faces on the exterior of said manifold 'convergently inclined to include an angle of about 90; and two rows of ports defined in each of said faces essentially normal thereto, the ports in one of said faces being staggered with respect to the ports in the other of said faces to form an interlaced but only slightly contacting iiame pattern, the ports in one row in each face being of different diameter lthan the ports in the other row, the ports in the outer row in each face having associated therewith a depression formed in said face.
  • end cap means consists of substantially hemispherical hollow members having a cross section essentially congruent with the cross section of said manifolds.

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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)
US690299A 1967-12-13 1967-12-13 Gas burner Expired - Lifetime US3511589A (en)

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US69029967A 1967-12-13 1967-12-13

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US690299A Expired - Lifetime US3511589A (en) 1967-12-13 1967-12-13 Gas burner

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US (1) US3511589A (en:Method)
BE (1) BE713431A (en:Method)
DE (1) DE1751483C3 (en:Method)
GB (1) GB1196338A (en:Method)
NL (1) NL6806789A (en:Method)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4492563A (en) * 1982-04-22 1985-01-08 Windmoller & Holscher Burner for heating air and disposed in a passage through which air flows
US5662467A (en) * 1995-10-05 1997-09-02 Maxon Corporation Nozzle mixing line burner
US6059566A (en) * 1997-07-25 2000-05-09 Maxon Corporation Burner apparatus
US6537064B1 (en) 2000-05-04 2003-03-25 Megtec Systems, Inc. Flow director for line burner
US20090291402A1 (en) * 2006-07-07 2009-11-26 Eun Seong Cho Flame structure of gas burner

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US366780A (en) * 1887-07-19 Fuel-gas burner
US697235A (en) * 1900-12-01 1902-04-08 Colin William Claybourne Gas-heater.
US702873A (en) * 1901-01-24 1902-06-17 Blanche I Holland Gas-burner.
US817750A (en) * 1905-06-22 1906-04-17 John B Carroll Acetylene-gas burner.
US1695587A (en) * 1927-03-21 1928-12-18 James R Rose Gaseous-fuel burner
US1859961A (en) * 1929-12-31 1932-05-24 Dodd Gas burner
US1907734A (en) * 1931-04-27 1933-05-09 Denver Fire Clay Company Gas burner
US2061561A (en) * 1930-03-20 1936-11-24 William G Cartter Burner for hydrocarbon gases
US2150819A (en) * 1936-07-21 1939-03-14 American Stove Co Gas burner
GB521772A (en) * 1938-11-25 1940-05-30 Isaac Vernon Brumbaugh Gas burner
US3051464A (en) * 1958-10-20 1962-08-28 Maxon Premix Burner Company Air-heating gas burner
US3202203A (en) * 1962-11-16 1965-08-24 Zink Co John Burner for gaseous fuels
GB1026899A (en) * 1964-03-26 1966-04-20 American Radiator & Standard Improvements in or relating to gas burners

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US366780A (en) * 1887-07-19 Fuel-gas burner
US697235A (en) * 1900-12-01 1902-04-08 Colin William Claybourne Gas-heater.
US702873A (en) * 1901-01-24 1902-06-17 Blanche I Holland Gas-burner.
US817750A (en) * 1905-06-22 1906-04-17 John B Carroll Acetylene-gas burner.
US1695587A (en) * 1927-03-21 1928-12-18 James R Rose Gaseous-fuel burner
US1859961A (en) * 1929-12-31 1932-05-24 Dodd Gas burner
US2061561A (en) * 1930-03-20 1936-11-24 William G Cartter Burner for hydrocarbon gases
US1907734A (en) * 1931-04-27 1933-05-09 Denver Fire Clay Company Gas burner
US2150819A (en) * 1936-07-21 1939-03-14 American Stove Co Gas burner
GB521772A (en) * 1938-11-25 1940-05-30 Isaac Vernon Brumbaugh Gas burner
US3051464A (en) * 1958-10-20 1962-08-28 Maxon Premix Burner Company Air-heating gas burner
US3202203A (en) * 1962-11-16 1965-08-24 Zink Co John Burner for gaseous fuels
GB1026899A (en) * 1964-03-26 1966-04-20 American Radiator & Standard Improvements in or relating to gas burners

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4492563A (en) * 1982-04-22 1985-01-08 Windmoller & Holscher Burner for heating air and disposed in a passage through which air flows
US5662467A (en) * 1995-10-05 1997-09-02 Maxon Corporation Nozzle mixing line burner
US6059566A (en) * 1997-07-25 2000-05-09 Maxon Corporation Burner apparatus
US6537064B1 (en) 2000-05-04 2003-03-25 Megtec Systems, Inc. Flow director for line burner
US20090291402A1 (en) * 2006-07-07 2009-11-26 Eun Seong Cho Flame structure of gas burner

Also Published As

Publication number Publication date
DE1751483A1 (de) 1970-10-22
NL6806789A (en:Method) 1969-06-17
DE1751483C3 (de) 1979-06-21
GB1196338A (en) 1970-06-24
BE713431A (en:Method) 1968-08-16
DE1751483B2 (de) 1973-02-08

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