US3670713A - Gas-fired heater means - Google Patents

Gas-fired heater means Download PDF

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US3670713A
US3670713A US47433A US3670713DA US3670713A US 3670713 A US3670713 A US 3670713A US 47433 A US47433 A US 47433A US 3670713D A US3670713D A US 3670713DA US 3670713 A US3670713 A US 3670713A
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gas
air
heat exchanger
apertures
heat
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US47433A
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Roy W Abbott
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Trane US Inc
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General Electric Co
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Assigned to TRANE CAC, INC., A CORP. OF DE reassignment TRANE CAC, INC., A CORP. OF DE ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: GENERAL ELECTRIC COMPANY A NY CORP.
Assigned to TRANE COMPANY, THE, A WI CORP reassignment TRANE COMPANY, THE, A WI CORP MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE: 12/29/83. STATE OF INCORP. WISCONSIN Assignors: TRANE CAC, INC.
Assigned to TRANE COMPANY, THE reassignment TRANE COMPANY, THE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE DATE 12/29/83 SURINAME Assignors: TRANE CAC, INC.
Assigned to TRANE COMPANY, THE reassignment TRANE COMPANY, THE MERGER (SEE DOCUMENT FOR DETAILS). DELAWARE, EFFECTIVE FEB. 24, 1984 Assignors: A-S CAPITAL INC. A CORP OF DE
Assigned to TRANE COMPANY THE reassignment TRANE COMPANY THE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/1/83 WISCONSIN Assignors: A-S CAPITAL INC., A CORP OF DE (CHANGED TO), TRANE COMPANY THE, A CORP OF WI (INTO)
Assigned to AMERICAN STANDARD INC., A CORP OF DE reassignment AMERICAN STANDARD INC., A CORP OF DE MERGER (SEE DOCUMENT FOR DETAILS). EFFECTIVE 12/28/84 DELAWARE Assignors: A-S SALEM INC., A CORP. OF DE (MERGED INTO), TRANE COMPANY, THE
Assigned to BANKERS TRUST COMPANY reassignment BANKERS TRUST COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TRANE AIR CONDITIONING COMPANY, A DE CORP.
Assigned to BANKERS TRUST COMPANY reassignment BANKERS TRUST COMPANY SECURITY INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AMERICAN STANDARD INC., A DE. CORP.,
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Assigned to CHEMICAL BANK, AS COLLATERAL AGENT reassignment CHEMICAL BANK, AS COLLATERAL AGENT ASSIGNMENT OF SECURITY INTEREST Assignors: BANKERS TRUST COMPANY, AS COLLATERAL TRUSTEE
Assigned to AMERICAN STANDARD, INC. reassignment AMERICAN STANDARD, INC. RELEASE OF SECURITY INTEREST (RE-RECORD TO CORRECT DUPLICATES SUBMITTED BY CUSTOMER. THE NEW SCHEDULE CHANGES THE TOTAL NUMBER OF PROPERTY NUMBERS INVOLVED FROM 1133 TO 794. THIS RELEASE OF SECURITY INTEREST WAS PREVIOUSLY RECORDED AT REEL 8869, FRAME 0001.) Assignors: CHASE MANHATTAN BANK, THE (FORMERLY KNOWN AS CHEMICAL BANK)
Assigned to AMERICAN STANDARD, INC. reassignment AMERICAN STANDARD, INC. RELEASE OF SECURITY INTEREST Assignors: CHASE MANHATTAN BANK, THE (FORMERLY KNOWN AS CHEMICAL BANK)
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H3/00—Air heaters
    • F24H3/02—Air heaters with forced circulation
    • F24H3/06—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators
    • F24H3/08—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes
    • F24H3/087—Air heaters with forced circulation the air being kept separate from the heating medium, e.g. using forced circulation of air over radiators by tubes using fluid fuel

Definitions

  • ABSTRACT Improved gas-fired heater means are provided for supplying heat to a space, such as a room, house, building, or the like.
  • the improved heater means comprises a combination of highly efiicient heat exhanger means for transferring heat generated by the combustion of a combustible gas-air mixture to air circulated between the heat exchanger means and the space to be heated at a rate of at least 3,500 BTU of heat per hour per pound of heat exchanger means material and high intensity combustor means for mixing fuel-gas with pressurized air to produce the combustible gas-air mixture and to burn that mixture to provide a source of heat of sufficient intensity to meet the heat transferring ability of the highly efficient heat exchanger means.
  • the improved heater means provided by the present invention permits considerable weight and volume reduction and consequent cost savings in heat exchanger means material over conventional gas-fired heaters of comparable heating capacity.
  • This invention relates to means for supplying heat to a space, such as a room, house, building, or the like and, more particularly, to improved gas-fired heater means for supplying such heat.
  • conventional gas-fired heater or furnace means of the aforedescribed type have most frequently employed rather crude cast iron or steel heat exchangers having the general shape of a hollow box or clam shell to transfer heat generated by the combustion of a combustible gas-air mixture to air circulated between the heat exchanger and the space to be heated.
  • these conventional heat exchangers have usually been combined with similarly unsophisticated combustor or burner means which have been very much like those used in gas cooking ranges and wherein the air that is mixed with the fuel-gas is supplied to the burner at atmospheric conditions.
  • the present invention provides improved gas-fired heater means which permit considerable weight and volume reduction, and consequent cost savings, in heat exchanger means material over the aforedescribed conventional gas-fired heaters of comparable heating capacity.
  • the improved heater means of the present invention comprises a combination of highly efficient heat exchanger means for transferring heat generated by the combustion of a combustible gas-air mixture to air circulated between the heat exchanger means and the space to be heated at a rate of at least 3,000 BTU per hour per pound of heat exchanger means material and high intensity combustor means for mixing fuelgas with pressurized air to produce the combustible gas-air mixture and to burn that mixture to provide a source of heat of sufficient intensity to meet the heat transferring ability of the highly efiicient heat exchanger means.
  • the total volume of the combination of the highly efiicient heat exchanger means and the high intensity combustor means, which comprises the improved heater means of the present invention is such that this combination has a heat release rate to the space air stream of at least 45 BTU of heat released per hour per cubic inch of material forming the combination, or around five times greater than the similar heat release rate previously achieved with the conventional heater means.
  • this combination of far less bulky and lighter weight heat exchanger means and high intensity combustor means, which comprises the improved gas-fired space heater means of the present invention provides geometry that is much smaller and, hence, far more compatible in size with the compact conventional air-cooling equipment than has heretofore been the case with the aforenoted prior-art heater means.
  • FIG. 1 is a somewhat schematic, partly-sectioned, front elevational view of a space air-conditioning unit incorporating a presently preferred form of the improved gas-fired heater means of the present invention
  • FIG. 2 is a greatly enlarged sectional view taken along line 2-2 of FIG. 1;
  • FIG. 3 is a sectional view taken along line 3-3 of FIG. 2;
  • FIG. 4 is a view generally similar to FIG. 2 but illustrating an alternative form of the improved gas-fired heating means of the present invention
  • FIG. 5 is a sectional view taken along line 5-5 of FIG. 4;
  • FIG. 6 is a greatly enlarged sectional view taken along line 6-6 of FIG. 5;
  • FIG. 7 is a greatly enlarged sectional view taken along line 7-7 of FIG. 5.
  • FIG. 1 there is illustrated, somewhat schematically, an air-conditioning unit, generally designated 10.
  • the air-conditioning unit 10 is fluid-connected by right and left hollow conduit means 1 l and 12 to a space 13 (shown in block), such as a room, house, building, or the like, so as to condition the air contained within the space 13, as by supplying heat to or removing heat from air that is circulated between the space 13 and the air-conditioning unit 10 through the conduit means 1 l and 12. And, as shown in FIGS.
  • the air-conditioning unit 10 employs a presently preferred form of the improved gasfired heater means, generally designated 14, that are provided in accordance with the present invention to supply heat to the air stream, indicated by arrows 15, that is circulated between the air-conditioning unit 10 and the space I3.
  • the improved gasfired heater means generally designated 14 that are provided in accordance with the present invention to supply heat to the air stream, indicated by arrows 15, that is circulated between the air-conditioning unit 10 and the space I3.
  • the air-conditioning unit 10 includes a generally rectangular hollow box-like cabinet 16 that is subdivided by a vertically arranged partition 17 into a left compartment 18 and a right compartment 19.
  • the cabinet left compartment 18 has an air inlet opening 20 in its upper wall that is fluid-connected to the space 13 by the left conduit means 12, while the upper wall of the cabinet right compartment 19 has an air outlet opening 21 that is fluid-connected to the space 13 by the right conduit means 11.
  • the cabinet right compartment 19 houses presently preferred forms of highly efficient heat exchanger means 22 and high intensity combustor means 23 that are provided in accordance with the present invention, while the cabinet left compartment I8 houses space air blower means 24.
  • the presently preferred form of the high intensity combustor means 23 includes a generally horizontally arranged elongate trough 25 of U-shaped cross section having generally vertically arranged interconnected side walls 26 and 27 that are provided with a plurality of apertures along their lower and upper edges to respectively define primary combustion air inlet apertures 28 and secondary combustion air inlet apertures 29.
  • Combustion air is introduced into the trough 25 through the primary and secondary combustion air inlet apertures 28 and 29 under pressure that is provided by combustion air-blower means 30.
  • the combustion air blower means 30 is housed in the lower right hand comer of the cabinet right compartment I9 and has its inlet connected to combustion air intake conduit means 3] which extend outwardly from the cabinet 16 through an opening 32 provided in the right side wall thereof.
  • the combustion air blower means 30 has its outlet connected via combustion airblower discharge conduit means 33 to box-like combustion air supply plenum 34 that is located around the trough 25.
  • a generally horizontally disposed gas supply conduit 35 extends longitudinally through the trough 25 and is provided with plural gas inlet apertures 36 located below the primary combustion-air inlet apertures 28.
  • the inlet of the gas supply conduit 35 is connected via an electric control valve 37 of a wellknown type to a source (not shown) of pressurized fuel-gas, such as natural gas, propane, or the like.
  • the firel gas inlet apertures 36 are arranged such that gas enters the trough 25 generally parallel to the generally vertically arranged trough side walls 26 and 27 and is turbulently mixed as indicated by arrows 38 with the pressurized air that is admitted ⁇ ia the generally horizontally disposed primary combustion air inlet apertures 28.
  • the rich combustible gas fuel-air mixture which results from the turbulent mixing of the pressurized gas-fuel that is discharged from the gas inlet apertures 36 with the pressurized air that enters the trough through the primary combustion air inlet apertures 28 moves upwardly through the trough 25 and is ignited by means of a high voltage spark produced in a well-known manner by an electric spark plug 39 or similar igniter device that is generally horizontally arranged at the left end of the trough 25 at a point vertically spaced between the primary combustion air inlet apertures 28 and the secondary combustion air inlet apertures 29.
  • This ignited mixture of gas fuel and primary combustion air is then further turbulently mixed as indicated by arrows 40 with the pressurized air that enters the trough 25 via the generally horizontal secondary combustion air inlet apertures 29 along the upper edges of the trough side walls 26 and 27 and produces an extremely high intensity heat source or flame 41.
  • the highly intense heat from this heat source or flame 41 is now transmitted to the lower end of the presently preferred form of the high intensity heat exchanger means 22 via hollow box-like interconnecting conduit means 42.
  • the intensity of the heat source or flame 41 that is produced by the high intensity combustor means 23 is at least 300,000 BTU of heat per hour per cubic foot of the interconnecting conduit means 42, an intensity level far exceeding any previously achieved with the prior-art atmospheric combustion air burners which have heretofore been commonly employed in gas-fired space heaters.
  • the presently preferred form of highly efi'rcient heat exchanger means 22 that are provided in accordance with the present invention comprises a plurality of generally vertically arranged hollow tubes 43 having their lower ends fluid-connected in parallel to the upper end of the interconnecting conduit means 42 provided between the top or open side of the trough 25 and the bottom of the heat exchanger means 22, while their upper ends are fluid-connected in parallel to an exhaust plenum or header 44 which directs the waste products of combustion to an atmospheric vent 45 that extends outwardly from the air-conditioning unit cabinet 16 through an opening 46 provided in the upper end of the cabinet right sidewall.
  • the outer surfaces of the hollow tubes 43 of the heat exchanger means 22 are provided with fin means 47 of the so called spine-fin type" that are generally similar to those described in detail in commonly-assigned prior-art US. Pat. No. 2,983,300, except that the tubes 43 and fins 47 for the heat exchanger 22 are preferably formed of a ferrous metal, such as steel, rather than of non-ferrous aluminum or copper as in the air-cooling exchanger described in the aforenoted priorart patent.
  • twisted ribbon-like turbulence promoters 48 are provided in the upper or exit ends of each of the heat exchanger tubes 43 in order to provide a balance of heat transfer between the finned outer surfaces and the bare inner surfaces of the tubes 43.
  • the space-air blower means 24 has its inlet 49 arranged beneath the air inlet opening 20 for the cabinet left compartment 18 and has its discharge 50 fluidconnected to the cabinet right compartment 19 via an opening 51 that is provided in the partition 17 and is arranged such that rotation of the space air-blower impeller 52 by its electric motor 53 will cause the air stream 15 to be circulated between the space 13 and the finned exterior of the heat exchanger tubes 43.
  • the right space-air conduit means 1 I serve as means for directing heated air from the air-conditioning unit 10 to the space 13 or as the so called warm air conduit means
  • the left conduit means 12 serve as the means for returning air from the space 13 to the air-conditioning unit 10 for reception of heat or as the so-called return air conduit means
  • the space-air blower means 24 serves as the means for circulating air between the space 13 and the improved gas-fired heater means 14 that are provided in accordance with the present invention.
  • the rate of transfer of this heat to the air stream 15 that can be accomplished with the presently preferred form of the heat exchanger means 22 (FIGS.
  • 1-3 is at least 3,500 BTU of heat per hour per pound of material that is used in the tubes 43 and fins 47, a rate far exceeding any previously achieved with the rather crude prior-art box-like or clam shellshaped heat exchangers which have hereto-fore been commonly employed in gas-fired space heaters.
  • FIGS. 4-7 illustrate alternative forms of the highly efficient heat exchanger means 22a and high intensity combustor means 230 that are provided in accordance with the present invention, and it should be understood that the relative locations of these alternative forms of highly emcient heat exchanger means 22a and high intensity combustor means 230 within the air-conditioning unit [0 are intended to be generally similar to the locations shown for the presently preferred forms of the highly efficient heat exchanger means 22 and high intensity combustor means 23 in FIG. 1.
  • the alternative form of high intensity combustor means 230 provided in accordance with the present invention substitutes a plurality of generally vertically arranged flame tubes 25a for the unitary trough 25 that is utilized in the previously described presently preferred form of combustor means 23 (FIGS. 1-3). As illustrated in FIGS. 4-7, these flame tubes 25a correspond in number to the total number of the alternate form of heat exchanger tubes 43a that are employed in the alternative form of heat exchanger means 22a.
  • Each of these flame tubes 250 comprises a generally vertically arranged hollow cylindrical tube having an open upper end that is joined by welding or other suitable fastening means to the lower end of its associated one of the alternative fonn of heat exchanger tubes 43a and a bottom end which is provided with a fuel-gas inlet aperture 36c that is connected by conduit means 36b to one of a plurality of gas-fuel apertures 36a provided in the top of a generally horizontally disposed alternate form of gas-fuel supply conduit means 35a which, of course, can be connected via means such as the electric control valve 37 (FIG. 1) to a source of pressurized fuel-gas, such as natural gas, propane, or the like.
  • a source of pressurized fuel-gas such as natural gas, propane, or the like.
  • each of the flame tubes 25a is provided with a plurality of primary combustion air inlet apertures 280 that are tangentially spaced around the lower edge of its cylindrical vertical sidewall, while, as particularly shown in FIGS. 4, 5 and 7, the upper edge of the cylindrical sidewall of each of the flame tubes 25a is provided with a plurality of secondary combustion air inlet apertures 29a which extend radially towards the axial center of the tube 250.
  • these alternate form of primary combustion air inlet apertures 280 are provided with intake portions 2812 that extend tangentially from the sidewall of the flame tubes 25a.
  • the plural flame tubes 25a are interconnected by a plurality of generally horizontally arranged cross-over tubes 29b which are axially aligned with one another and with igniter means, such as a spark plug 39a or the like, that is generally horizontally arranged at the left end of the series of flame tubes 250 at a point vertically spaced between the primary combustion air inlet apertures 38a and the secondary combustion air inlet apertures 29a.
  • igniter means such as a spark plug 39a or the like
  • combustion air is introduced into the flame tubes 25a through the primary and secondary air inlet apertures 28a and 29a under pressure that is provided by means such as the combustion-air blower means 30 shown in H6. 1, with the combustion-air blower means 30 having its outlet connected via its discharge conduit means 33 to an alternative form of combustion air supply plenum 340 that is located around all of the flame tubes 25a.
  • the gas fuel is introduced upwardly into each of the flame tubes 25a by the gas inlet aperture 360 and is turbulently mixed with the pressurized primary combustion air that is tangentially introduced (FIG. 6) into the flame tube lower end by the primary combustion air inlet apertures 280.
  • This rich combustible mixture of pressurized gas fuel and primary combustion air produces a vortex flow pattern within the lower portion of each flame tube 250 which moves upwardly toward the aligned cross-over tubes 39b, at which point it is ignited by means of a high voltage spark that is produced in a well-known manner by the igniter 390.
  • This ignited mixture of pressurized gas fuel and primary combustion air is then further turbulently mixed (FIG.
  • the alternative form of heat exchanger means 224 provided in accordance with the present invention comprises a plurality of generally vertically arranged hollow tubes 430 which have their lower ends individually fluid-connected to the upper end of an associated one of the plurality of flame tubes 25a.
  • the remaining structure of this alternative form of heat exchanger means 22a is generally similar to the presently preferred form 22 shown in FIGS. 1-3, with the upper ends of the alternative form of heat exchanger tubes 43a being fluid-connected in parallel to an exhaust plenum or header which directs the waste products of combustion to an atmospheric vent that extends outwardly from the air conditioning unit cabinet through an opening provided in the upper end of the cabinet right sidewall (FIG. 1).
  • the outer surfaces of these alternative form of hollow tubes 43 are provided within fins 47a of the so called spine-fin type" and are generally similar to those finned tubes described in detail in the aforenoted commonly-assigned prior-art US. patent except that the tubes 43a and fins 47a for the alternative form of heat exchanger 22a are preferably formed of a ferrous metal such as steel, rather than of non-ferrous aluminum or copper as in the air-cooling exchanger described in the aforenoted prior-art patent.
  • the alternative form of high efficiency heat exchanger means 22a is also similar to the preferred form in that turbulence promoters, not shown but otherwise similar to the turbulence promoters 48 illustrated in FIGS. 2 and 3, are provided in the upper or exit end of each of the alternative form of heat exchanger tubes 43a in order to provide a balance of heat transfer between the finned outer surfaces and bare inner surfaces of the tubes 43a.
  • the total volume of the combination of the highly efficient heat exhanger means 22 or 22a and the high intensity combustor means 23 or 230, which comprises the improved gas-fired heater means 14 of the present invention is such that this combination has a heat release rate to the air stream of at least 45 BTU of heat released per hour per cubic inch of the material forming the combination, or around five times greater than the similar heat release rate heretofore achieved with the aforenoted conventional heater means.
  • this combination of the far less bulky and lighter weight heat exchanger means 22 or 22a and the high intensity combustor means 23 or 230 which comprises the improved gas-fired Space heater means 14 of the present invention, provides geometry that is much smaller and, hence, far more compatible in size and shape with the rather compact conventional aircooling equipment than has previously been the case with the aforenoted prior-art heater means. Therefore, the improved gas-fired heater means 14 of the present invention are particularly suited for combination within the cabinet 16 (H6. 1) with air-cooling means (not shown) to thus provide means for both heating and cooling the air stream 15, whereby the airconditioning unit 10 can comprise a combined air heating and cooling unit of far less bulk and weight than has heretofore been possible.
  • Improved gas-fired space heater means comprising the combination of:
  • heat exchanger means for transferring heat generated by the combustion of a combustible gas-air mixture to air circulated between said heat exchanger means and the space to be heated and combustor means for mixing fuel-gas with pressurized air to produce said combustible gas-air mixture and to burn said mixture;
  • said heat exchanger comprising a plurality of tubes provided with fins on the exterior thereof;
  • said combustor means comprising burner means including a generally horizontal trough-shaped member forming a primary mixing area and a secondary mixing area spaced apart by an ignition area, means including a plurality of gas inlet apertures adjacent the bottom of said troughshaped member for supplying pressurized fuel-gas to said primary mixing area; and
  • means for supplying pressurized air to said mixing areas including primary air inlet apertures adjacent the lower portion of said trough-shaped member and above said gas inlet apertures and secondary air inlet apertures along the upper portion of said trough-shaped member.
  • Improved gas-fired space heater means comprising the combination of:
  • heat exchanger means for transferring heat generated by the combustion of a combustible gas-air mixture to air circulated between said heat exchanger means and the space to be heated and combustor means for mixing fuel-gas with pressurized air to produce said combustible gas-air mixture and to burn said mixture;
  • said combustor means comprising burner means including a horizontal trough having spaced side walls and a bottom wall forming a primary mixing area and a secondary mixing area spaced apart by an ignition area, means for supplying pressurized fuel-gas to said primary mixing area, and means for supplying pressurized air to said mixing areas;
  • said means for supplying pressurized fuel-gas including a plurality of gas inlet apertures adjacent the bottom wall of said trough;
  • said means for supplying pressurized air to said mixing areas includes primary air inlet apertures in the primary mixing area of said trough and above said gas inlet apertures and secondary air inlet apertures along the upper portion of said trough side walls.
  • a gas-fired space heater means comprising the combination of:
  • burner means including an elongate horizontally extending member of generally U-shaped cross section including opposed walls and an interconnecting wall;
  • means for supplying pressurized fuel-gas to said burner means including a plurality of gas inlet apertures adjacent said interconnecting wall and extending substantially the length of said member;
  • said opposed walls having at least one row of primary air apertures extending longitudinally thereof adjacent said gas inlet apertures and at least one row of secondary air apertures spaced from said row of primary air apertures; means for supplying pressurized air to said apertures;
  • a heat exchanger comprising a plurality of parallel finned tubes
  • elongate conduit means extending substantially the length of said elongate member connecting the open side of said elongate member to said heat exchanger.
  • a gas-fired heater means including a pressurized air supply plenum surrounding the side walls of said elongate member.
  • a gas-fired space heater means comprising the combination of:
  • burner means including an elongate horizontal member of generally U-shaped cross section including opposed walls and an interconnecting wall;
  • a perforated fuel gas pipe positioned within said member adjacent said interconnecting wall and extending substantially the length of said member;
  • each of said opposed walls having at least one row of primary air apertures extending longitudinally of said member adjacent said gas pipe and at least one row of secondary air apertures spaced from said gas pipe;
  • a heat exchanger comprising a plurality of finned tubes
  • elongate conduit means extending substantially the length of said elongate member connecting said elongate member to one end of said heat exchanger tubes.
  • a gas-fired space heater means in which said perforated gas pipe introducing fuel gas generally parallel to said opposed walls and said air apertures introducing air under pressure horizontally into said elongate member.

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  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
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  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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US47433A 1970-06-18 1970-06-18 Gas-fired heater means Expired - Lifetime US3670713A (en)

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GB (1) GB1343446A (fr)
SE (1) SE375370B (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3809052A (en) * 1970-08-29 1974-05-07 Hughes J Ryffin Heating apparatus
US3935855A (en) * 1971-05-24 1976-02-03 N.V. Werktuigenfabrieke Mulder Air heater, especially for connection to a central heating system
US4412523A (en) * 1980-08-11 1983-11-01 Alzeta Corporation Catalytic gas-fired furnace system and method
US4476850A (en) * 1982-09-02 1984-10-16 Carrier Corporation Noise reducing heat exchanger assembly for a combustion system
US4515145A (en) * 1983-10-03 1985-05-07 Yukon Energy Corporation Gas-fired condensing mode furnace
US4860725A (en) * 1983-08-24 1989-08-29 Yukon Energy Corporation Power burner-fluid condensing mode furnace
US6889686B2 (en) * 2001-12-05 2005-05-10 Thomas & Betts International, Inc. One shot heat exchanger burner
US20060157232A1 (en) * 2005-01-14 2006-07-20 Thomas & Betts International, Inc. Burner port shield
US20140014047A1 (en) * 2011-01-27 2014-01-16 Industrias Haceb S.A. Continuous flow water heater that mitigates the effect of altitude

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
EP0041862A3 (fr) * 1980-06-10 1982-02-03 Thorn Emi Energy Developments Limited Réchauffeur d'air
DE3726862A1 (de) * 1986-08-12 1988-03-10 Hitachi Heating Appl Kraftfahrzeugheizung
CN102338465B (zh) * 2011-08-22 2013-09-25 洛阳佳嘉乐农业产品开发有限公司 一种高温灭菌用的热风炉
CN106801994A (zh) * 2017-03-27 2017-06-06 魏景锋 热风炉及制热系统

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US2281106A (en) * 1939-06-10 1942-04-28 Henry J De N Mccollum Room heater
US2555546A (en) * 1946-08-26 1951-06-05 Holly Mfg Company Gas furnace
US2737173A (en) * 1953-08-11 1956-03-06 Delta Heating Corp Combustion type unit heater
US2876763A (en) * 1955-06-15 1959-03-10 Hunter Multiple fuel burner and space heater
US3315655A (en) * 1967-04-25 Firing mechanism for multiple burner heating apparatus
US3364916A (en) * 1965-07-29 1968-01-23 Wilkins & Mitchell Ltd Heating devices

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US3315655A (en) * 1967-04-25 Firing mechanism for multiple burner heating apparatus
US2281106A (en) * 1939-06-10 1942-04-28 Henry J De N Mccollum Room heater
US2555546A (en) * 1946-08-26 1951-06-05 Holly Mfg Company Gas furnace
US2737173A (en) * 1953-08-11 1956-03-06 Delta Heating Corp Combustion type unit heater
US2876763A (en) * 1955-06-15 1959-03-10 Hunter Multiple fuel burner and space heater
US3364916A (en) * 1965-07-29 1968-01-23 Wilkins & Mitchell Ltd Heating devices

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3809052A (en) * 1970-08-29 1974-05-07 Hughes J Ryffin Heating apparatus
US3935855A (en) * 1971-05-24 1976-02-03 N.V. Werktuigenfabrieke Mulder Air heater, especially for connection to a central heating system
US4412523A (en) * 1980-08-11 1983-11-01 Alzeta Corporation Catalytic gas-fired furnace system and method
US4476850A (en) * 1982-09-02 1984-10-16 Carrier Corporation Noise reducing heat exchanger assembly for a combustion system
US4860725A (en) * 1983-08-24 1989-08-29 Yukon Energy Corporation Power burner-fluid condensing mode furnace
US4515145A (en) * 1983-10-03 1985-05-07 Yukon Energy Corporation Gas-fired condensing mode furnace
US6889686B2 (en) * 2001-12-05 2005-05-10 Thomas & Betts International, Inc. One shot heat exchanger burner
US20050161036A1 (en) * 2001-12-05 2005-07-28 Thomas & Betts International, Inc. One shot heat exchanger burner
US20060157232A1 (en) * 2005-01-14 2006-07-20 Thomas & Betts International, Inc. Burner port shield
US7726386B2 (en) 2005-01-14 2010-06-01 Thomas & Betts International, Inc. Burner port shield
US20140014047A1 (en) * 2011-01-27 2014-01-16 Industrias Haceb S.A. Continuous flow water heater that mitigates the effect of altitude
CN103597295A (zh) * 2011-01-27 2014-02-19 哈斯堡实业股份有限公司 减轻海拔效应的连续流水加热器

Also Published As

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GB1343446A (en) 1974-01-10
DE2129826A1 (de) 1971-12-23
SE375370B (fr) 1975-04-14
FR2099250A5 (fr) 1972-03-10

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