EP3118520B1 - Hochleistungsstrahlungsbrenner mit wärmetauscheroption - Google Patents

Hochleistungsstrahlungsbrenner mit wärmetauscheroption Download PDF

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Publication number
EP3118520B1
EP3118520B1 EP16181257.3A EP16181257A EP3118520B1 EP 3118520 B1 EP3118520 B1 EP 3118520B1 EP 16181257 A EP16181257 A EP 16181257A EP 3118520 B1 EP3118520 B1 EP 3118520B1
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EP
European Patent Office
Prior art keywords
burner
fuel gas
gas
cavity
combustion
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Application number
EP16181257.3A
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English (en)
French (fr)
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EP3118520A1 (de
Inventor
Redwood D. Stephens
John Porensky
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Cascade Designs Inc
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Cascade Designs Inc
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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
    • F23D14/28—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid in association with a gaseous fuel source, e.g. acetylene generator, or a container for liquefied gas
    • 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
    • F23D14/12—Radiant burners
    • F23D14/151—Radiant burners with radiation intensifying means other than screens or perforated plates
    • 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
    • F23D14/12—Radiant burners
    • F23D14/16—Radiant burners using permeable blocks
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/72—Safety devices, e.g. operative in case of failure of gas supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/24—Preventing development of abnormal or undesired conditions, i.e. safety arrangements
    • F23N5/247—Preventing development of abnormal or undesired conditions, i.e. safety arrangements using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/105—Porous plates

Definitions

  • the present invention relates to controlled combustion and more particularly to pressurized hydrocarbon gas burners and most particularly to a liquid pressurized gas (LPG) stove/cookware system that includes a high efficiency heat exchanger working in conjunction with a fully aerated radiant burner.
  • LPG liquid pressurized gas
  • JetBoil, Inc. offer gas combustion apparatus with heat exchangers that boost efficiency from conventional stove and pot combinations (35% - 55%) to (45% - 65%). Because these apparatus are limited by free convection heat transfer coefficients and dilution of the combustion gases with secondary air, higher efficiency values for apparatus of these designs are limited.
  • nitrous oxides is of particular concern with respect to domestic gas water heaters.
  • Initial combustion of gases in natural convection heaters occurs at high temperatures which are conducive to nitrous oxide formation.
  • the combustion gases are diluted by freely convecting air where some additional combustion occurs but gas departure and velocities drop.
  • US 5240411A discloses an atmospheric gas burner assembly producing relatively low oxides of nitrogen (NOx) emissions.
  • US 5511974A discloses an atmospheric reticulated ceramic foam burner which is retrofittable into existing residential heat exchanger designs and has been developed to reduce NOx and CO emissions.
  • the present invention utilizes a radiant burner and optional heat exchanger arrangement to achieve high heat transfer values to containers through forced convection and hotter undiluted combustion gases, which increase overall efficiency of the system from (70% to 85%), without adding excessive heat exchanger surface area.
  • the burner also greatly lowers the temperature at which complete combustion occurs, thereby greatly reducing nitrous oxide emissions.
  • a feature of the invention is that as power output is increased, the driving pressure for forced convection with the optional heat exchanger is also increased, and thus heat transfer efficiency is generally constant over a wide range of power outputs.
  • the result of this arrangement provides for a radiant burner that is highly fuel efficient, that has increased resistance to the deleterious effects of wind on the burner, that greatly increases the safety of operation of the radiant burner, and that significantly reduces the output of nitrous oxides. When used in combination with the optional heat exchanger, fuel efficiency is further increased and emissions further decreased.
  • the radiant burner comprises a generally enclosed cavity defined, at least in part, by a fuel gas impermeable surrounding and a lower surface of a fuel gas permeable burner element, wherein the cavity has at least one opening exposed to an oxidizer source.
  • Sealingly coupled to the at least one opening is a mix tube that defines a longitudinal axis, and has a first end and a second end wherein the first end occupies the at least one opening and the second end extends into and is exposed to the pressure cavity.
  • any structure capable of mixing a gaseous fuel with a gaseous oxidizer can be used as a mix tube, and therefore such structures are considered as an equivalent.
  • a fuel gas injector which during use of the burner is in fluid communication with a source of fuel gas, is positioned to introduce fuel gas into the mix tube, preferably at or proximate to the first end, thereby encouraging momentum transfer of the oxidizer into the fuel gas stream when the oxidizer is also introduced at or proximate to this location.
  • pre-combustion gasses diffuse from the lower surface of the burner element to the upper surface. Pre-combustion gasses at the upper surface may then be ignited, such as by an igniter that is associated with the burner, whereupon combustion takes place.
  • a plurality of openings is present in the pressure cavity.
  • a corresponding number of cylindrical mix tubes are fluidly coupled to the openings, and are exposed to the ambient environment at their first end and to the cavity at their second ends.
  • the ambient environment provides the oxidizer source, i.e., oxygen.
  • a corresponding number of fuel gas injectors are preferably positioned at the first end of the mix tubes such that the fuel gas, when introduced into the mix tubes, entrains a volume of air and mixes the two gasses to form a pre-combustion gas.
  • the pre-combustion gasses are preferably further mixed and turbulence imparted into the pre-combustion gas stream by a plurality of static mixing posts.
  • the mixing posts also preferably serve to radiate heat that may accumulate in the burner housing through exposure to the cool pre-combustion gasses.
  • a feature of the burner is the incorporation of a thermal fuse (trip filter) disposed between the fuel gas source and the gas injector(s).
  • This fuse may be constructed from any material that will be predictably responsive to heat such that when exposed to heat higher than a certain temperature for an established period of time, the material changes form, which operates to interrupt fuel flow to the gas injector(s).
  • the filter is a eutectic metal such as cadmium, lead tin alloy, which is formed into a washer that operatively keeps a check valve in the open position.
  • containment vessels such as pots
  • containment vessels can be specially adapted to exploit the quantity and quality of heat output by the radiant burner.
  • a primary mode of adaptation involves the use of heat exchanging structure at or near the bottom of the containment vessel, which preferably comprises a plurality of fins, either as fin elements integral with the vessel or as fin bodies attachable to the vessel, arranged to maximize radiant and convective heat transfer of combustion gasses from the burner.
  • Each relevant containment vessel will have a bottom surface and a lower side surface that is linked to the bottom surface by a shoulder.
  • the intention of the heat exchanging structure is to increase the duration of the vessel's exposure to the burner output, thereby further increasing the efficiency of the system employing the radiant burner.
  • the described and illustrated burners provide a user with exceptional efficiency and significantly decreased undesirable combustion byproducts.
  • CO emissions are about 8 times less than a comparably sized conventional stove.
  • nitrogen oxides are significantly reduced (approximately 80-93%) when compared to commercially available competing stoves.
  • burner element 60 comprises a porous metal foam material sold under the trademark METPORE by Porvair Advanced Materials, Inc. of Hendersonville, North Carolina.
  • METPORE Porvair Advanced Materials, Inc. of Hendersonville, North Carolina.
  • other gas porous, heat resistant materials can be used, such as ceramics and metal-ceramic composites.
  • Burner 10 comprises metallic base 12, which provides fuel delivery infrastructure 30 (discussed below) and which partially defines cavity 24. Cavity 24 is further defined by metal surround 14 and burner element 60. As will be described in more detail below, cavity 24 is generally sealed from the environment with two major exceptions. First, mix tubes 50a and 50b are sealingly attached to surround 14 and are exposed to the environment proximal ends 52a and 52b (see Fig. 3 ). Second, burner element 60 is porous to gasses (see Fig. 2 ).
  • gasses introduced at proximal ends 52a and 52b of mix tubes 50a and 50b travel the length of the mix tubes until expelled into cavity 24 at distal ends 54a and 54b.
  • burner element 60 is highly porous, a gas pressure gradient exists between cavity 24 and the environment at outer surface 64 such that gasses present in cavity 24 will diffuse through burner element 60 towards outer surface 64.
  • Fuel gas such as Liquid Pressurized Gas (LPG) is delivered to burner element 60 in the following manner.
  • An LPG bottle (not shown) is rotationally coupled to inlet 30, as is best shown in Figs. 2 and 2A .
  • inlet 30 includes threaded portion 32, preferably conforming to the 8-188 standards to ensure wide compatibility with gas bottle suppliers.
  • probe 36 opens a valve in the LPG bottle and pressurized gas travels through probe 36 and into chamber 26.
  • Chamber 26 is generally defined by inlet housing 27 and seat 28.
  • Within chamber 26 are ball 29 and compression spring 25. Compression spring 25 provides an outward bias to ball 29, which is prevented from translational movement by seat 28 reacting against outlet housing 31 via thermal fuse body 38.
  • LPG occupies both chamber 26 and area 26', which is in fluid communication with outlet conduit 40 via port 39. Outlet conduit 40 then permits LPG to discharge into regulator 42.
  • a feature of the disclosed arrangement is directed towards a thermal LPG interrupt that functions to autonomously stop the flow of gas from the container to the burner.
  • seat____ functions to prevent ball 29 from extending into contact with sealing surface 41.
  • seat 28 which is in a compression mode through the bias imparted by spring 25 to ball 29, reacts against outlet housing 31 via thermal fuse 38. But for the presence of fuse 38, seat 28 would be urged to translate away from compression spring 25, thereby permitting ball 29 to come in sealing contact with sealing surface 41, and thereby occlude further gas passage into outlet conduit 40.
  • fuse 38 is intentionally constructed to loose structural cohesion at or above a general temperature to prevent potentially explosive conditions such as might be encountered during a "light back" or reverse ignition propagation event. While the ultimate determination of the appropriate temperature is a matter of design consideration, the disclosed example that is not an embodiment contemplates thermal conditions of between about 145°C to 200°C as being candidate temperatures for a thermal trip.
  • the compressed gas Upon passing thermal fuse 38, the compressed gas is directed towards regulator and valve assembly 42 for pressure and volume regulation.
  • Control handle 44 provides functionality to assembly 42 as is appreciated by those persons skilled in the art.
  • Regulated gas is then directed to both gas jets 48a and 48b via distribution manifold 46, which in turn direct fuel gas into mix tubes 50a and 50b.
  • Entrainment of an oxidizer in this case oxygen bearing air, occurs at the injector and throughout the length of the mix tube by drawing air into the mix tube at openings 16a and 16b, which represents the only major openings within pressure cavity 24.
  • oxidizer in this case oxygen bearing air
  • surrounding 14 is coaxially surrounded by perforated housing 18. Consequently, a generally annular space is created between surrounding 14 and housing 18, from which air is drawn into openings 16a and 16b. In this manner, any wind impacting perforated housing 18 is diffused prior to entering opening 16a and 16b.
  • the fuel gas and oxidizer combination exits from ends 54a and 54b of mixing tubes 50a and 50b and enters cavity 24, where upon it impinges static mixing and heat transfer posts 56.
  • static mixing and heat transfer posts 56 perform a dual function: Because posts 56 are thermally coupled to base 12, heat generated by burner 10 and transferred to base 12 by radiation, conduction and/or convention is partially removed by contact between posts 56 and incoming cool pre-combustion gas. Beneficially, this drawing of heat from base 12 increases the heat content of pre-combustion gas, which promotes more efficient combustion thereof.
  • Posts 56 also beneficially function to increase mixing of pre-combustion gas prior to combustion and aid in uniform distribution of pre-combustion gas by decreasing the gas velocity so that diffusion of pre-combustion gas through burner element 60 occurs more uniformly.
  • burner 10 As noted earlier, during operation of burner 10, a pressure gradient exists between upper surface 64 of burner element 60, which is exposed to ambient conditions, and lower surface 62 of burner element 60, which is exposed to slightly pressurized pre-combustion gas.
  • piezoelectric igniter 66 may be operated to initiate combustion of pre-combustion gasses, in a manner well known in the art. Upon ignition, combustion migrates to just below upper surface 64 of burner element 60, and is prevented from further propagation by the low bulk thermal conductivity and small pore size of burner element 60. At this point, burner 10 becomes a radiant burner with no perceptible freely convective frame.
  • Screen 20 is provided as a safety feature to prevent unintentional physical contact with burner element 60 and to serve as an interface with cookware employing a heat exchanger as described in detail below. Both screen 20 and perforated housing 18 are secured to burner 10 by way of screen retainer ring 22. Should maintenance of burner 10 become necessary, a user need only remove retainer ring 22 to expose upper surface 64 of burner element 60, or through removal of burner element 60, base 12.
  • heat exchanger 90 can be integrated into a fluid vessel, and more particularly vessel or pot 70.
  • the purpose of heat exchanger 90 is to efficiently extract heat generated by burner 10 by taking advantage of its combustion mode.
  • the mass flow and temperature attributes of heat generated by burner 1O are considered in the design of heat exchanger 90.
  • the constitution of heat exchanger 90 can take many forms. The ultimate selection of one form over another may be driven by design considerations such as the volume of vessel 70, the nature of the liquid to be heated, the fluid dynamic properties of the combustion gasses, and similar factors.
  • the presently illustrated examples that are not embodiments are intended to show several variations, but are by no means representative of an exhaustive inventory of available heat exchangers.
  • the presently illustrated examples that are not embodiments all attempt to maximize the surface area exposed to the radiant heat and combustion gasses of burner 10 without significantly minimizing the benefits achieved through convection heating.
  • the illustrated embodiments employ a plurality of channels having relatively unobstructed exit paths where the channels maximize the distance the combustion gasses must travel from burner element 60 to the ambient environment.
  • a weld-on heat exchanger arrangement is shown.
  • a plurality of fin elements 80 are formed separately from pot 70, and subsequently attached to pot 70 such as by spot welding, brazing or similar heating techniques to create a plurality of channels 86 through which combustion gasses may travel.
  • Fin elements 80 are preferably constructed from aluminum by stamping or similar high volume creation means. Fin elements 80 are preferably formed for placement on bottom surface 78 of pot 70 in a spiral or involute pattern to maximize exposure time of the combustion gasses with the elements.
  • Fig. 58 shows a similar pattern of fin bodies 82 formed on bottom surface 78 of pot 70, however, fin bodies 82 are integral with bottom surface 78.
  • fin bodies 82 may be formed by machining the desired pattern in bottom surface 78 or during casting of bottom surface. While the thermal transfer rates from fin bodies 82 to pot 70 and overall durability are greater than the thermal transfer rates from fin elements 80 to pot 70 due to the more robust association of the former with the pot, manufacturing costs are higher.
  • a preferred means of manufacturing integral fin bodies is by impact extrusion processes. These processes provide the benefits of exceptional thermal conductivity (superior to that of casting), desirable surface finish for the cooking surface (superior to that of casting or machining), low weight (superior to that of casting and machining, which also generates avoidable waste) and low cost (superior to that of machining and welding). While there are size limitations using these processes, they are not material to the form factors commonly used in backpacking cookware.
  • bottom surface 78 need not be planar or flat. Again depending upon design parameters, bottom surface 78 can be conical or frusto-conical like, with the apex at the center of the vessel. Such a geometry will not only beneficially modify the residency of any combustion gasses during operation of a burner, but when used in conjunction with a burner such as burner 10 having screen 20, will restrict properly mate with the burner to the exclusion of other cookware. Alternatively, a plurality of surface features such as convex or concave features can be established in or on bottom surface 78 to alter the egress of combustion gasses to the environment.
  • Fig. 6 illustrates a perimeter heat exchanger arrangement that can be used in conjunction with the heat exchanges of Figs. 5A and 58, or with other arrangements.
  • a plurality of perimeter elements 84 as shown in Fig. 7 , for example, and surrounding the perimeter of pot 70 with such elements, waste heat exiting from channels 86, for example, impinge upon perimeter elements 84 and is redirected along reduced diameter portion 74 of pot 70.
  • additional surface area for heat exchange is created at both perimeter elements 84, which are thermally linked to heat exchanger 90, as well as directly to pot 70.
  • drip ring 76 is provided above reduced diameter portion 74.

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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)

Claims (4)

  1. Flüssigdruckgasofen mit einem Gasbrenner, wobei der Gasbrenner Folgendes umfasst:
    einen Hohlraum (24), der zumindest teilweise durch eine brenngasundurchlässige Umgebung (14) und ein brenngasdurchlässiges Brennerelement (60) mit einer dem Hohlraum ausgesetzten Innenfläche und einer der Umgebung ausgesetzten Außenfläche definiert ist, wobei die brenngasundurchlässige Umgebung eine Vielzahl von Öffnungen (16a, 16b) aufweist;
    eine entsprechende Anzahl von zylindrischen Mischrohren (50a, 50b), wobei jedes Mischrohr eine Längsachse, ein erstes Ende (52a, 52b) und ein zweites Ende (54a, 54b) aufweist, wobei das erste Ende der Umgebung ausgesetzt ist, indem es fluidisch und dichtend mit der entsprechenden Öffnung gekoppelt ist, und das zweite Ende, das fluidisch mit dem Hohlraum gekoppelt ist, sich in den Hohlraum hineinerstreckt; und
    eine entsprechende Anzahl von Brenngaseinspritzern am entsprechenden ersten Ende oder in der Nähe davon zum Einspritzen von Brenngas in das entsprechende Mischrohr und Mitreißen eines für das Mischrohr verfügbaren Oxidationsmittels,
    wodurch innerhalb des Hohlraums ein Volumen von unter Druck stehendem brennbaren Gas erzeugt wird, das von der Innenfläche des Brennerelements zur Außenfläche des Brennerelements diffundiert.
  2. Flüssigdruckgasofen nach Anspruch 1, wobei das Brennerelement ein im Wesentlichen entflammbares poröses Material umfasst.
  3. Flüssigdruckgasofen nach Anspruch 2, wobei das entflammbare poröse Material Metallschaum umfasst.
  4. Flüssigdruckgasofen nach Anspruch 1, wobei der Gasbrenner ferner eine Wärmesicherung zum Verschließen eines Brenngasdurchlasses zwischen einer Brennstoffquelle und den Brenngaseinspritzern umfasst.
EP16181257.3A 2005-08-05 2006-08-07 Hochleistungsstrahlungsbrenner mit wärmetauscheroption Active EP3118520B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US70609605P 2005-08-05 2005-08-05
PCT/US2006/030814 WO2007027379A1 (en) 2005-08-05 2006-08-07 High efficiency radiant burner
EP06789552.4A EP1920191B1 (de) 2005-08-05 2006-08-07 Hochleistungsstrahlungsbrenner

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP06789552.4A Division EP1920191B1 (de) 2005-08-05 2006-08-07 Hochleistungsstrahlungsbrenner
EP06789552.4A Division-Into EP1920191B1 (de) 2005-08-05 2006-08-07 Hochleistungsstrahlungsbrenner

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Publication Number Publication Date
EP3118520A1 EP3118520A1 (de) 2017-01-18
EP3118520B1 true EP3118520B1 (de) 2024-03-13

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EP16181257.3A Active EP3118520B1 (de) 2005-08-05 2006-08-07 Hochleistungsstrahlungsbrenner mit wärmetauscheroption
EP06789552.4A Active EP1920191B1 (de) 2005-08-05 2006-08-07 Hochleistungsstrahlungsbrenner

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US (1) US20080213715A1 (de)
EP (2) EP3118520B1 (de)
JP (1) JP5301992B2 (de)
AU (1) AU2006285272A1 (de)
CA (1) CA2617564C (de)
WO (1) WO2007027379A1 (de)

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Also Published As

Publication number Publication date
JP5301992B2 (ja) 2013-09-25
US20080213715A1 (en) 2008-09-04
EP1920191A1 (de) 2008-05-14
CA2617564C (en) 2016-04-12
AU2006285272A1 (en) 2007-03-08
JP2009503433A (ja) 2009-01-29
WO2007027379A1 (en) 2007-03-08
EP3118520A1 (de) 2017-01-18
CA2617564A1 (en) 2007-03-08
EP1920191B1 (de) 2016-09-21
EP1920191A4 (de) 2010-10-20

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