US3782887A - Gaseous fuel burner - Google Patents

Gaseous fuel burner Download PDF

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Publication number
US3782887A
US3782887A US00293050A US3782887DA US3782887A US 3782887 A US3782887 A US 3782887A US 00293050 A US00293050 A US 00293050A US 3782887D A US3782887D A US 3782887DA US 3782887 A US3782887 A US 3782887A
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United States
Prior art keywords
burner
venturi
air
plate
head
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Expired - Lifetime
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US00293050A
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English (en)
Inventor
R Brown
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TRI MEN Manufacturing Inc
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TRI MEN Manufacturing Inc
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Publication date
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    • 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

  • Means are also provided for ad- [56] References Cited justing the primary air-gas ratio entering the venturi and further means are provided for distributing secon- UNITED STATES PATENTS dary air to the base of the flame approximately in the 2,72l.607 l0/l955 Damon et all 431/353 X plane f h downstream mouth f h i 3.709.473 l/l973 Ito et al. 43 l/353 X 9 Claims, 8 Drawing Figures GASEOUS FUEL BURNER BACKGROUND OF THE INVENTION
  • This invention relates to gaseous fuel burners, particularly to relatively small size burners for use in space heating, as for example, the interior of mobile homes, marine craft and land vehicles.
  • a principal object of the invention is to provide a burner that is extremely compact but one that can produce a high output.
  • a typical burner of this invention may have the approximate dimensions of a three-inch cube and be able to produce an output of approximately 20,000 BTU perhour atan efficiency of greater than 80 percent. Not only is the burner of this invention able to perform with the above ability, but it does so in a reliable, safe and quiet fashion.
  • the principle of supplying air and gaseousfuel at super-atmospheric pressure is used. Futhermore, the mixing of the primary combustion air and the gaseous fuel is effected by use of the venturi principle wherein the gaseous fuel is introduced into the throat of the venturi cross current to the flow of combustion air therethrough and the mixture rapidly expanded while still at super-atmospheric pressure and then burned off a deep-ported bumerplate over a relatively wide or large area.
  • primary air shall be rdfined as that part of the combustion air that is intimately mixed with the gaseous fuel within the venturi structure; secondary air shall designate that part of the combustion air that is delivered to the burner head, but which is not mixed with the fuel in advance of the burner :ports.
  • a further object of this invention is to provide a burner having an ignition means (preferably of the continuous spark variety) that is safe and dependable in operation andis designed to have along life.
  • the igniterforthe subjectburneris so situated as to be cooled by the incoming air and air-gas mixtures and is further arranged to have its parts, particularly the electrode tip, out of the intense zone of combustion, but proximate the zone or plane where combustion initiates.
  • FIG. 1 is a longitudinal view, partially in section, showing theburner applied to a combustion chamber.
  • FIG. 2 is a cross-sectional view looking upstream from the mouth of the burner, essentially along line 11-41 of FIG. 1.
  • FIG. 3 is afragmentary section across the throat of the venturi at the gaseous fuel admission orifices and on the plane of line III-III.
  • FIG. 4 is a'longitudinal schematic view of the venturi assembly, the supporting flange, combustion chamber, illustrating the air and 'gas flow and the combustion process.
  • FIG. 5 is an end view of the upstream end of the venturi showing the distribution of primary air intake openings at the fixed primary air plate.
  • FIG. 6 is a detail of the air shutter adjusting means.
  • FIG. 7 is a fragmentary detail of the igniter structure.
  • FIG.8 is a schematic representation of a heating system embodyingthe subject burner.
  • Thepreferred embodiment of this invention includes a burnerbody B enclosing a venturi assembly V, gas admission means G, combustion air admission means A and an igniter assembly I.
  • the burner body is cup-shaped with an open mouth and includes an end wall'2 and peripheralwall 3 having a flange 4 for attaching the burner to a combustion chamber designated generally as H.
  • the end wall is provided with a boss 6 bored and threaded to receive a gas supply fitting 7 and a primary air adjustment crank pin 8 and its lock nut 9.
  • a gas spud 12 is threaded into the end wall (in communication with the gas supply fitting 7) on the axis of the burner and has gas orifices 13 directed radially and in a plane lying about one-half the depth of the burner cup.
  • a flange member 15 having a cylindrical skirt l6 is clamped by screws 18 between the face of the burner flange 4 and the combustion chamber H.
  • venturi member designated generally by the reference character V.
  • the upstream mouth 20 of the venturi supports a primary air admission and adjustment means 40, described infra, in spaced relation to the end wall 4 and has its throat portion 22 located in the plane of the gas orifices 13; the abruptly flared downstream portion 26 of the venturi terminates just beyond the mouth of the burner body.
  • venturi V divides the interior of the burner body B into two zones, namely; (1) the volume within the venturi that comprises a mixing zone in which a portion of the combustion air is mixed with the gaseous fuel and (2) the space surrounding the venturi over which passes the remaining combustion air to feed a concentric series of small (secondary) air openings 17 in the face of the flange 15.
  • these openings 17 are placed near and just outboard the juncture of the skirt 16 and the flange 15.
  • these openings furnish air that cools the venturi structure and burner plate structure, as will be shown in greater detail infra.
  • a relatively thick burner plate 30 having a large number of deep ports 32, uniformly distributed over the face of the plate, forming discharge openings for the mixture of fuel, gas and primary air delivered from venturi V.
  • the ratio of port diameter to port depth is in the range of 1:4; for a burner plate having a 2-inch diameter, approximately 250 ports each having a l/l6 inch diameter may be provided.
  • the burner is designed to burn a wide variety of combustible gases, ranging in heating value from 500 to 2500 BTU or more; to accomplish this in a efficient manner, control of the primary combustion air is necessary.
  • this control is obtained by fixing a primary air plate 41 in the upstream end 20 of venturi V, FIG. 5.
  • This plate has a series of air admission openings 42 the effective size of which are controlled by a movable shutter plate 44 having a matching series of openings 45.
  • the shutter is positioned by and rides on a shoulder 2a (part of the burner end wall 2) and is actuated by crank pin 8 joumaled in end wall 2 and having a slotted flange 52 which receives a pin 46 carried by the shutter, FIG. 6. Rotational movement of the crank causes the shutter to rotationally shift with respect to the air plate and allows the desired adjustment of the primary air admission openings.
  • the crank is fixed in the desired position by lock nut 9.
  • the igniter I consists of an electrode 60 sheathed in an insulating sleeve 62 that is mounted in an opening through the top of the burner and held in place by lock nut 63.
  • the working end of the igniter is positioned near the axis of the burner just downstream of the burner plate 30 and is adapted to continuously are against said plate.
  • the igniter electrode tip 64 terminates at the downstream face of burner plate 30 proximate a pocket 38. Arcing occurs from the tip 64 to the pocket wall. Some of the burner ports intersect the wall of the pocket 38 and thereby introduce the combustible mixture to the confines of the pocket across which the arc 56 occurs.
  • the burner B is applied to a combustion chamber-heat exchanger H, served with an exhaust line H1, and enclosed in a shroud T to which ventilating air is suppleid by a fan F driven by motor M.
  • This same motor may drive a separate blower A which furnishes combustion air to the burner through air line Al.
  • Gaseous fuel is supplied through line G from a source at superatmospheric pressure (eg 8 to l3 inches of water column).
  • the burner igniter is shown at I, and has a convenient source of constant high tension voltage (not shown) during burner operation.
  • the entire system may be enclosed in a casing having appropriate heated air outlet openings S1 and air inlet openings S2.
  • the overall dimensions of such an installation may only be 14 inches long, 13 inches wide and 9 inches high, with the unit capable of delivering in excess of 15,000 BTU per hour at better than percent efficiency.
  • the novel burner of the invention being less than three inches in diameter and about two inches deep, is able to provide an efficient flame for a 7-inch long combustion chamber to effect the above output. Not only does the burner accomplish the above output, but in operation it is quiet, clean burning and safe.
  • the subject burner is designed for constant spark ignition and is generally operated under a control system (not shown) that provides for a start up, run and shutdown cycle, with thermostatic and safety control features.
  • the gaseous fuel supply at super-atmospheric pressure is introduced in a cross-current fashion to throat 22 of the venturi through orifices 13, preferably at a line pressure of 8 to 13 inches water column (see FIG. 3).
  • combustion air is brought tangentially into the head through opening 10 at a pressure of one to two inches of water column.
  • This air divides into two portions: the major part of it passes through the primary air openings 42 and 45 to enter the interior of the venturi bell section 20 and the remainder passes around the venturi and out through the secondary air holes 17.
  • the air that enters the venturi is funneled into the throat portion 22 and due to its increased flow velocity, tends to draw the fuel gas leaving orifices 13 into the stream and inter-mix it thoroughly with the combustion air.
  • This construction is an important feature of the design, since variation in the rate of air flow through the throat (which may be due to changes in the delivery rate of the blower because of external factors, such as line voltage variation, etc.) automatically adjusts the inspiration of gas to maintain a constant airgas ratio in the mixture discharged from the throat.
  • the gas-air mixture leaves the throat 22 it is expanded rapidly and further mixing takes place, so that a uniform, combustible mixture is presented to the burner plate 30.
  • the venturi may have an inlet cone that is inch deep with sides converging at an included angle of 120, a throat one inch in diameter and inch long and a downstream bell 26 diverging at an included angle of 90.
  • the volume of the downstream conical section or hell 26 is larger than the corresponding upstream structure to allow for the increased volume of gases (the added fuel gas) and the expansion thereof at higher temperature in proximity to the combustion zone. It is desirable to maintina the internal pressure uniform throughout the venturi, except at the throat where the pressure drop is designed to assist in the injection and mixing of the gaseous fuel. This is accomplished by proper sizing of the primary air openings 42 and balanced by the size and number of burner port openings 32.
  • the space within the burner head 1 and exterior of the venturi structure is maintained at essentially the same pressure (e.g. one and be inch water column) as that inside the venturi bell portions 22 and 26.
  • This air is given a spiral motion, sweeps the venturi structure tending to cool the same, and is discharged through the secondary air openings 17 in the flange 15.
  • the purpose of the secondary air is twofold: (1) it is supplied to the combustion chamber H to assure complete and properly controlled combustion and (2) it is used to ventilate or cool the burner parts including the burner wall 3, the venturi structure V, the burner plate 30 and the igniter I.
  • the gas-air mixture presented to and leaving the burner ports 32 is a readily combustible gaseous medium (thus assuring proper ignition and burning at the ports)
  • the introduction of secondary air permits a softer flame from the ports 32 and assures completion of combustion in a quiet manner within a short distance from the burner plate 30.
  • the primary air-gas mixture first burns in soft jets at and off the burner face; these jets combine into a uniform, rapidly burning, hydroxylating flame or inner mantle of a length approximately lrfi times the diameter of the burner plate and this flame is surrounded by a blue outer mantle, filling the combustion chamber H and assuring complete combustion within a distance of three times the diameter of the burner plate.
  • a gaseous fuel burner comprising a cup-shaped burner head including an end wall and a cylindrical wall enclosing an air cavity with an open mouth, means for introducing combustion air at super-atmospheric pressure tangentially to the interior of the head near the end wall, means for introducing gaseous fuel under pressure through ports oriented in a radial direction at a point along the longitudinal axis of the burner and spaced from the end wall, a restrictor flange attached to and partially closing the mouth of the head member and terminating in a cylindrical sleeve portion extending downstream, a sharply flaring venturi structure supported at its downstream end by said sleeve and having its throat portion in the vicinity of the gas ports and its upstream end spaced from the end wall, a perforated plate across the upstream end of the venturi to allow primary air to enter the venturi and a multi-ported burner plate supported across the downstream portion of the sleeve and spaced from the diverging wall of the venturi.
  • the burner of claim 1 including electrical ignition means carried by the head and operative at the downstream face of the burner plate.
  • the burner of claim 1 including an air shutter for regulating the flow of primary air entering the venturi.
  • the ignition means is a high tension spark electrode that is mounted on the head, extends through the cavity and terminates in the pocket at essentially the central axis of the burner.

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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)
  • Spray-Type Burners (AREA)
US00293050A 1972-09-28 1972-09-28 Gaseous fuel burner Expired - Lifetime US3782887A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US29305072A 1972-09-28 1972-09-28

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US3782887A true US3782887A (en) 1974-01-01

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US00293050A Expired - Lifetime US3782887A (en) 1972-09-28 1972-09-28 Gaseous fuel burner

Country Status (5)

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US (1) US3782887A (cs)
JP (1) JPS4993933A (cs)
CA (1) CA985157A (cs)
DE (1) DE2348953A1 (cs)
GB (1) GB1446952A (cs)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3853456A (en) * 1973-05-29 1974-12-10 American Air Filter Co Fuel burning apparatus
DE3113416A1 (de) * 1981-04-03 1982-10-21 Ruhrgas Ag, 4300 Essen Verfahren zum betrieb eines einem luftstrom ausgesetzten gasbrenners sowie brenner zur durchfuehrung des verfahrens
US5447427A (en) * 1991-09-24 1995-09-05 Kabushiki Kaisha Kobe Seiko Sho Burner and method for burning low calorific gas
US5681159A (en) * 1994-03-11 1997-10-28 Gas Research Institute Process and apparatus for low NOx staged-air combustion
US5996200A (en) * 1993-09-09 1999-12-07 Sms Schloemann-Siemag Aktiengesellschaft Descaling device and method
US6071115A (en) * 1994-03-11 2000-06-06 Gas Research Institute Apparatus for low NOx, rapid mix combustion
US20040253559A1 (en) * 2003-06-12 2004-12-16 Honeywell International Inc. Premix burner for warm air furnace
CN108006628A (zh) * 2017-12-30 2018-05-08 赵金岷 一种高温高压烟气发生器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5361750A (en) * 1993-06-14 1994-11-08 Roberts-Gordon, Inc. Burner assembly

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2721607A (en) * 1954-04-30 1955-10-25 Hunter Liquid fuel burner and ignition means therefor
US3709473A (en) * 1969-08-26 1973-01-09 Mitsubishi Electric Corp Heating apparatus

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2721607A (en) * 1954-04-30 1955-10-25 Hunter Liquid fuel burner and ignition means therefor
US3709473A (en) * 1969-08-26 1973-01-09 Mitsubishi Electric Corp Heating apparatus

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3853456A (en) * 1973-05-29 1974-12-10 American Air Filter Co Fuel burning apparatus
DE3113416A1 (de) * 1981-04-03 1982-10-21 Ruhrgas Ag, 4300 Essen Verfahren zum betrieb eines einem luftstrom ausgesetzten gasbrenners sowie brenner zur durchfuehrung des verfahrens
US5447427A (en) * 1991-09-24 1995-09-05 Kabushiki Kaisha Kobe Seiko Sho Burner and method for burning low calorific gas
US5996200A (en) * 1993-09-09 1999-12-07 Sms Schloemann-Siemag Aktiengesellschaft Descaling device and method
US5681159A (en) * 1994-03-11 1997-10-28 Gas Research Institute Process and apparatus for low NOx staged-air combustion
US6071115A (en) * 1994-03-11 2000-06-06 Gas Research Institute Apparatus for low NOx, rapid mix combustion
US20040253559A1 (en) * 2003-06-12 2004-12-16 Honeywell International Inc. Premix burner for warm air furnace
US6923643B2 (en) * 2003-06-12 2005-08-02 Honeywell International Inc. Premix burner for warm air furnace
CN108006628A (zh) * 2017-12-30 2018-05-08 赵金岷 一种高温高压烟气发生器

Also Published As

Publication number Publication date
CA985157A (en) 1976-03-09
DE2348953A1 (de) 1974-04-11
JPS4993933A (cs) 1974-09-06
GB1446952A (en) 1976-08-18

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