EP0898687B1 - Brenner - Google Patents

Brenner Download PDF

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Publication number
EP0898687B1
EP0898687B1 EP96915860A EP96915860A EP0898687B1 EP 0898687 B1 EP0898687 B1 EP 0898687B1 EP 96915860 A EP96915860 A EP 96915860A EP 96915860 A EP96915860 A EP 96915860A EP 0898687 B1 EP0898687 B1 EP 0898687B1
Authority
EP
European Patent Office
Prior art keywords
oxidizer
fuel
port
ports
primary
Prior art date
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
Application number
EP96915860A
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English (en)
French (fr)
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EP0898687A1 (de
EP0898687A4 (de
Inventor
James K. Nabors, Jr.
William C. Andrews
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Xothermic Inc
Original Assignee
Xothermic Inc
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Filing date
Publication date
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Publication of EP0898687A1 publication Critical patent/EP0898687A1/de
Publication of EP0898687A4 publication Critical patent/EP0898687A4/de
Application granted granted Critical
Publication of EP0898687B1 publication Critical patent/EP0898687B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M5/00—Casings; Linings; Walls
    • F23M5/02—Casings; Linings; Walls characterised by the shape of the bricks or blocks used
    • F23M5/025—Casings; Linings; Walls characterised by the shape of the bricks or blocks used specially adapted for burner openings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/00012—Liquid or gas fuel burners with flames spread over a flat surface, either premix or non-premix type, e.g. "Flächenbrenner"
    • F23D2900/00013—Liquid or gas fuel burners with flames spread over a flat surface, either premix or non-premix type, e.g. "Flächenbrenner" with means for spreading the flame in a fan or fishtail shape over a melting bath

Definitions

  • the present invention relates to a burner apparatus for the combustion of fuel and an oxidizer in the combustion chamber according to the preamble of claim 1.
  • burners utilize oxygen enriched air for efficiency improvements and emission reductions.
  • enriched air there are additional problems with the burner operation.
  • combustion temperatures increase and a higher rate of material degradation occurs.
  • the burner uses a stabilized combustion away from the burner exit which enables heat transfer closer to the target and further from the burner, thereby increasing efficiency and extending burner/furnace equipment life.
  • the ability to adjust the flame pattern away from the fuel and oxidizer ports for temperature sensitive equipment is even more critical as preheated oxidizers are used.
  • Preheated oxidizers result in even higher combustion temperatures causing very rapid material degradation should flame patterns not be regulated.
  • the adjustability aspect is important as it pertains to use with preheated oxidizer. Should oxidizer temperatures vary during a given interval, momentum changes can be performed to maintain consistent flame performance.
  • While the fuel (solid, liquid or gaseous) introduced has a particular momentum, it is in magnitude typically less than that of the oxidizer. This is not to say that the fuel momentum does not play a role in the flame pattern but rather to emphasize the degree of control it influences the overall reaction. Realizing this, control of the oxidizer is crucial in adjustment of the flame pattern. In many operational situations, a change of hydrocarbon fuels is required. This change of fuel is readily incorporated by the burner's ability to vary oxidizer momentum. Solid fuels such as coal and wood possess much different transport and combustion characteristics than liquid fuels such as oil or alcohol. In turn, gaseous fuels such as natural gas and propane are different in the same regard as solid and liquid fuels.
  • a solid fuel is typically crushed into small particles and transported by a portion of the oxidizer, usually air, into the final combustion process.
  • a liquid fuel is transported as a liquid and atomized into small droplets, usually in the form of an atomizing medium comprised of a portion of the oxidizer and introduced into the combustion process.
  • Gaseous fuels are on occasion mixed with a portion of the oxidizer and introduced into the combustion process, but in most cases are transported and introduced as their original composition.
  • the common factor in all three fuel types is that the fuel is supplied in particles, droplets or molecules small enough that it begins to display characteristics of a gaseous medium.
  • the burner's adjustment capability also enable the operator to fine tune the performance to minimize any pollutants produced.
  • a change in fuel will necessitate a change to the oxidizer flow configuration. This change will also effect the production of many pollutants in particular derivatives of nitrogen and sulfur. These derivatives are influenced by many factors, temperature and resident time among the most important. With the ability to adjust oxidizer momentum and in effect the flame pattern and temperature undesirable pollutants can be minimized, by adjustment, for any fuel used.
  • Momentum adjustment to the oxidizer is performed by varying flow among several ports.
  • Four sets of ports are positioned about the fuel port to form a diamond shape fashion.
  • the oxidizer ports are further divided into primary and secondary ports.
  • the primary ports are closest to the fuel port and may have an angular direction toward the fuel.
  • the secondary oxidizer ports are further away from the fuel and may be angled but not necessarily in the same degree as the primary ports.
  • the oxidizer is diverted between primary and secondary ports. This diversion changes the overall momentum as well as the direction of the diverted flow, since primary and secondary ports may not pass the same angles or intersection points.
  • flow may be redirected away from or towards a particular port set. This provides the means necessary to redirect or compensate flame patterns for fuel changes, operational requirements or pollutants reduction.
  • a combustion apparatus has independent flow streams, one for an oxidizer and one for a fuel with an adjustable control capability to permit various flame configurations and reproducible combustion rates at different oxidizer and gaseous fuel flow rates.
  • a burner block was used having primary and secondary oxidizer passageways positioned at angles. The burner also had a gaseous fuel supply separated into primary and secondary gaseous fuel paths.
  • US-A-4,494,923 shows an oxy-fuel burner having plural feed ports around an electric ignition system.
  • US-A-4,378,205 shows an oxygen fuel furnace having a plurality of oxidant jets positioned in a spaced relationship to a fuel jet and having a velocity sufficient to cause an aspiration of the furnace gases into the oxidant jets to mix the fuel.
  • US-A-4,622,007 refers to a variable heat generating method and apparatus which uses a hydrocarbon fuel having separately supplied streams of fuel and at least two oxidizing gases to react with the fuel.
  • US-A-4,541,796, refers to an oxygen aspirator burner for firing a furnace having a plurality of oxidant jets in spaced relationship to the fuel jets.
  • US-A-4,954,076, shows a nozzle mixed oxy-fuel burner using an oxidant fed at high velocity to aspirate recycled products of combustion.
  • US-A-4,790,743 refers to a method of reducing NOX-emissions during combustion of fuel containing nitrogen which feeds a coal dust along with its carrier gas to a primary burner.
  • US-A-4,933,163 is related to a process of removing hydrogen sulfide from exhaust gas in which oxygen and air are fed through multiple tubes to the combustion chamber.
  • US-A-4,957,050 describes a combustion process using oxygen or oxygen enriched air as an oxidant in which a liquid fuel is fed to the combustion chamber separate from the oxidants.
  • US-A-4,988,285 shows a combustion method in which oxidants are separately injected into the combustion zone in a defined velocity relationship and combustion gases are aspirated into the oxygen stream prior to mixture with the fuel.
  • US-A-5,267,850 discloses a fuel jet burner using a high velocity central fuel stream and a low velocity annular coaxial oxidant stream to carry out stable steady combustion in the expanding combusting stream.
  • US-A-4 439 132 discloses a method and an apparatus for combustion of the generic kind with a minimum of NOX-emission and uses a burner block having a fuel exit port connected to a fuel conduit, primary oxidizer exit ports positioned around the fuel exit port and each being connected to a primary oxidizer conduit, and secondary oxidizer exit ports positioned around the fuel exit port which are spaced from the primary oxidizer exit ports in relation to the fuel exit port, and each being connected to a secondary oxidizer conduit.
  • the burner apparatus comprises further oxidizer lines each connected to the primary oxidizer conduit and the secondary oxidizer conduit, and oxidizer biasing valves located in each secondary oxidizer conduit.
  • the secondary oxidizer ports are arranged circumferentially and parallel to the axis of the fuel exit port, while the primary oxidizer port extend radially inwardly of the secondary oxidizer ports over a predetermined sector angle. There are no flow valves associated with the primary oxidizer ports.
  • US-4 475 885 discloses an adjustable flame burner similar to that of the generic kind with standard control means to adjust the relative amount of oxidizer for providing flame relief patterns varying between a short cylindrical flame and a long intense all radial flame.
  • the burner apparatus of the present invention allows use where adjustments to a particular flame pattern geometry is critical to the performance of the combustion process and is especially useful in applications where a variety of hydrocarbon fuels are constantly used and removal of the burner apparatus is not possible.
  • the oxidizing medium is supplied to the combustion process by a series of ports that can be varied in momentum and resultant flow direction by simple adjustment of control valves. This adjustment provides the means necessary to utilize a variety of fuels, such as solid, liquid or gaseous, without the need to alter or remove the burner because of a fixed oxidizer design.
  • the oxidizer ports can also be adjusted independent of each other allowing the flame geometry and direction to be changed as required. Variations in the oxidizer flow path enables optimization of thermal efficiencies while at the same time providing the means to minimize oxygen related emissions, such as those involving nitrogen and sulfur.
  • the disclosed apparatus is specifically designed for flexibility of operation. Its oxidizer adjustability enables alterations to the flame pattern as required, such as load demand changes or heat transfer inputs. Heat transfer and flame shape vary with different fuels and adjustment capability is critical when a change to fuel type is made. The oxidizer variable momentum and resultant flow direction provide the diversity needed to acquire desirable flame results.
  • the present invention is a burner where the oxidizer may have a variable momentum to obtain the needed limits of adjustments.
  • the need for a high degree of adjustment is required to maintain safe and tolerable operation using a highly enriched oxidizer and to provide the means to utilize different fuel types while maintaining a consistently acceptable flame geometry and to enable performance adjustments for maximum attainable emission reductions.
  • a variety of flame patterns are possible. With the broad fuel input base it is necessary to provide large selection of adjustable flame patterns. Larger particles, as used in solid fuels, need more momentum to provide flame pattern stability while gaseous fuels require less momentum for the same flame pattern geometry.
  • the oxidizer adjustment capabilities provide not only the means necessary to utilize different fuels but also the ability to change flame patterns as needed with each fuel to optimize combustion performance.
  • primary and secondary oxidizer port area ratios may vary depending on specific application parameters.
  • the oxidizer port area ratio is defined as the cross-sectional area of the secondary oxidizer port divided by the cross sectional area of the primary oxidizer port of the same burner side. Ratios are independent of other burner sides and may differ depending on requirements. In one instance, a high turndown ability may be desired in which case a higher ratio would provide the necessary large momentum change. Yet in another instance, a fine adjustment to flame pattern through a narrow range of operating loads would dictate a lower ratio. In the case of the described invention, a ratio of approximately four to one provides for the flame pattern adjustment illustrated. Specific ratios would be chosen to optimize the specific area of operational interest while still providing the means to adjust flame pattern for a variety of fuels.
  • FIGs 1 and 2 an isometric view of a burner block is shown in which the majority of flame adjustments are derived from the oxidizer.
  • Fuel enters the burner through the fuel inlet 1 and passes through the fuel conduit 2 into burner block 7 and exits through the fuel exit port 12.
  • the fuel type may vary so no attempt has been made to detail any more than the means necessary to introduce fuel to the burner. Transport and conditioning are different for each fuel type but as earlier described, all fuels can be treated as a gaseous medium.
  • the oxidizer is a gaseous medium with any concentration of oxygen purity and is introduced into the burner through four oxidizer lines, two of which can be seen in FIG. 1.
  • the oxidizer inlet line 3 on the top and oxidizer inlet line 5 on the right side.
  • the oxidizer from the line 3 passes through oxidizer assembly 4 into the burner block 7.
  • the burner block 7 is labeled into four distinct regions; the burner block top 8, the burner block right side 9, the burner block bottom 10, and the burner block left side 11.
  • FIG. 2 shows the burner face where the oxidizer and fuel exit to form the flame pattern.
  • the oxidizer exits through the following ports: oxidizer primary top port 13, oxidizer primary right side port 14, oxidizer primary bottom port 15, oxidizer primary left side port 16, oxidizer secondary top port 17, oxidizer secondary right side port 18, oxidizer secondary bottom port 19, and oxidizer secondary left side port 20.
  • the oxidizer primary exit ports are arranged 90 degrees apart with respect the fuel conduit centerline.
  • the oxidizer secondary exit ports are arranged 90 degrees apart from each other with respect to the fuel conduit centerline 40 of FIG. 4, but not necessarily the same orientation as the oxidizer primary exit ports.
  • the oxidizer primary and secondary exit ports can be of any diameter as required by the load and may be spaced to contact adjacent ports (primary and secondary) or up to approximately one hundred port diameters between adjacent ports.
  • the burner block 7 has port face planes including the primary exit face top 21, the primary exit face right side 22, the primary exit face bottom 23, the primary exit face left side 24, the secondary exit face top 25, the secondary exit face right side 26, the secondary exit face bottom 27, and the secondary exit face left side 28.
  • Exit or port faces can be best described as planes surrounding individual ports.
  • Each port has an exit face and each exit face has its own angular orientation with respect to the fuel conduit centerline 40 of FIG. 4.
  • An exit face angular orientation of zero degrees would be normal to the conduit centerline 40, a positive angle would position the exit face towards the fuel conduit centerline 40 and conversely a negative angle would position the exit face away from the fuel conduit centerline 40.
  • Exit face orientation is independent of the oxidizer port angle and is dictated by the particular application.
  • FIG. 3 a section view shows the oxidizer bottom assembly 30 and the oxidizer top assembly 31. All four oxidizer assemblies possess the same control hardware but for clarity only two are shown.
  • the oxidizer entering through the oxidizer top line 3 and bottom line 29 passes through oxidizer flow control valves 36 (top) and 38 (bottom). These flow control valves regulate the oxidizer flow to the respective oxidizer assemblies and the flow to each may be different due to operational requirements.
  • the oxidizer fed to each assembly is split between the oxidizer primary conduit (top 32 and bottom 34) and the oxidizer secondary conduit (top 33 and bottom 35).
  • oxidizer biasing valve top 37 and bottom 39.
  • the oxidizer passes through the burner block 7 and to their respective exit ports where the oxidizer combines with the fuel.
  • a typical oxidizer adjustment may call for a high momentum for rapid combustion.
  • the biasing valve would be closed down to force the majority of oxidizer flow through the primary conduit increasing the overall velocity.
  • the biasing valve would be opened to allow flow to pass through both primary and secondary ports, thus slowing the overall velocity.
  • FIG 4 is a more detailed view of Figure 3 showing the burner block 7 and fuel conduit centerline 40.
  • the top oxidizer primary conduit angle 45 is the angle between the fuel conduit centerline 40 and top oxidizer primary conduit centerline 41.
  • the bottom oxidizer primary conduit angle 46 is the angle between the fuel conduit centerline 40 and bottom oxidizer primary conduit centerline 43.
  • the top oxidizer secondary conduit angle 47 is the angle between the fuel conduit centerline 40 and the top oxidizer secondary conduit centerline 42.
  • the bottom oxidizer secondary conduit angle 48 is the angle between the fuel conduit centerline 40 and the bottom oxidizer secondary conduit centerline 44.
  • Typically a high oxidizer conduit angle results in a more rapid and intense combustion due to the elevated mixing caused by the severe angles of impact.
  • FIG. 5 shows a detail of the top oxidizer secondary conduit 33.
  • the fuel conduit centerline 40 and top oxidizer secondary conduit centerline 42 are overlapping which would indicate that they are both parallel from this perspective. This perspective is from the fuel conduit centerline outward or in a radial direction.
  • Figure 6 shows the same view as in Figure 5 except that the fuel conduit centerline 40 and oxidizer secondary conduit centerline 42 are no longer parallel.
  • the angle is called the oxidizer secondary conduit radial angle and can vary.
  • Each oxidizer has its own radial angle and each may be different. This radial angle provides an additional means to adjust the rate of combustion.
  • Figures 7 and 8 show different oxidizer momentum adjustments and the effect on flame pattern. To achieve a symmetrical flame pattern all oxidizer mass flow is divided evenly through each burner block side 8,9,10,11 of 'the oxidizer assembly. Each oxidizer primary conduit is equal in mass flow and each oxidizer secondary conduit is also equal in mass flow.
  • Figure 8 shows the same symmetrical mass flow arrangement as Figure 7 but with the oxidizer biasing valves adjusted to pass the majority of the oxidizer through the oxidizer primary conduits and the minority through the oxidizer secondary conduits. The result is an increase in the combustion rate due to the higher momentum and steeper angle.
  • the high momentum flame pattern 51 is much shorter than the low momentum flame pattern 50 in Figure 7. Both flame patterns have nearly the same flame pattern beginning (50A, 51A) but the high momentum flame pattern end 51B is much closer to the flame pattern beginning than is the low momentum flame pattern end 51B. In addition, the high momentum flame pattern 51 is much larger in cross section than the low momentum flame pattern 50. Flame pattern 51 totally covers the oxidizer secondary ports where it does not in flame pattern 50.
  • a representation of a nonsymmetrical flame pattern 52 is created for directional flame pattern requirements. It is comparable in momentum to the low momentum flame pattern 50 of Figure 7.
  • the oxidizer flow control valves on the burner block top 8 and burner block left side 11 have been adjusted to pass a majority of the total of the oxidizer mass flow while the oxidizer flow control valves on the burner block right side 9 and burner block bottom 10 pass a minority of the oxidizer.
  • This nonsymmetrical adjustment forces the nonsymmetrical flame pattern end 52B below and to the right of the nonsymmetrical flame pattern beginning 52A.
  • This flame pattern can be shortened by increasing the overall oxidizer momentum as in Figure 8 but will still retain the nonsymmetrical characteristics.
  • the flame pattern can also be rotated about the fuel conduit centerline by adjustment to distribution of the overall oxidizer flow to each oxidizer assembly.
  • Figure 10 offers another possible adjustment where a flat wide flame pattern 53 is desired.
  • Both oxidizer assemblies 31 (top) and 30 (bottom) pass a majority of oxidizer flow while oxidizer assemblies left and right side pass a minority of the oxidizer.
  • the oxidizer biasing valves are in a low momentum adjustment.
  • This flow arrangement forces the fuel between the two colliding oxidizer flows and produces a flat wide flame pattern beginning 53A and flat wide flame pattern end 53B similar to that in Figure 7 but with a flat wide flame pattern right side 53C and flat wide flame pattern left side 53D and a large cross-sectional diameter.
  • This flat flame pattern is also much thinner from top 53E to bottom 53F.
  • This flat wide flame pattern can also be reproduced in the same manner in any orientation about the fuel conduit centerline 40.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Gas Burners (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Addition Polymer Or Copolymer, Post-Treatments, Or Chemical Modifications (AREA)
  • Regulation And Control Of Combustion (AREA)
  • Control Of Combustion (AREA)

Claims (3)

  1. Brennervorrichtung für die Verbrennung eines Brennstoffs und eines Sauerstoffträgers in einer Verbrennungskammer, wobei die Brennervorrichtung
    einen Brennerblock (7)
    mit einem Brennstoffauslasskanal (12), der mit einer Brennstoffleitung (2) verbunden ist,
    mit primären Sauerstoffauslasskanälen (13 bis 16), die um den Brennstoffauslasskanal (12) herum angeordnet sind und von denen jeder mit einer primären Sauerstoffträgerleitung (32, 34) verbunden ist, und
    mit sekundären Sauerstoffträgerauslasskanälen (17 bis 20), die um den Brennstoffauslasskanal (12) herum angeordnet sind und einen Abstand von den primären Sauerstoffträgerauslasskanälen (13 bis 16) bezogen auf den Brennstoffauslasskanal (12) haben, und von denen jeder mit einer sekundären Sauerstoffleitung (33, 35) verbunden ist,
    Sauerstoffträgerzuführleitungen (3, 29), von denen jede mit einer primären Sauerstoffträgerleitung (32, 34) und mit einer sekundären Sauerstoffträgerleitung (33, 35) verbunden ist, und
    Sauerstoffträgersteuerventile (37, 39) aufweist, die in jeder sekundären Sauerstoffträgerleitung (33, 35) angeordnet sind
    gekennzeichnet
    durch vier primäre Sauerstoffträgerkanäle (13 bis 16) und vier benachbarte beabstandete sekundäre Sauerstoffträgerkanäle (17 bis 20), wobei die Kanäle (13 bis 20) um 90° voneinander entfernt um den Brennstoffauslasskanal (12) positioniert sind und
    durch Sauerstoffträgerdurchflusssteuerventile (36, 38), die in jeder Sauerstoffträgerzuführleitung (3, 29) positioniert sind,
    wobei die primären Sauerstoffträgerkanäle (13 bis 16) und die sekundären Sauerstoffträgerkanäle (17 bis 20) in Richtung zu dem Brennstoffkanal (12) im Winkel angeordnet sind.
  2. Brennervorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass jeder primäre Sauerstoffträgerkanal (13 bis 16) von jedem benachbarten sekundären Sauerstoffträgerkanal (17 bis 20) in einem Abstand angeordnet ist, der zwischen einem direkten Kontakt und 100 Kanaldurchmessern liegt.
  3. Brennervorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass jeder primäre Sauerstoffträgerkanal (13 bis 16) und jeder benachbarte sekundäre Sauerstoffträgerkanal (17 bis 20) insgesamt parallel zueinander verlaufen.
EP96915860A 1996-05-17 1996-05-17 Brenner Expired - Lifetime EP0898687B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1996/007051 WO1997044618A1 (en) 1996-05-17 1996-05-17 Burner apparatus and method

Publications (3)

Publication Number Publication Date
EP0898687A1 EP0898687A1 (de) 1999-03-03
EP0898687A4 EP0898687A4 (de) 2000-02-23
EP0898687B1 true EP0898687B1 (de) 2002-08-14

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96915860A Expired - Lifetime EP0898687B1 (de) 1996-05-17 1996-05-17 Brenner

Country Status (8)

Country Link
EP (1) EP0898687B1 (de)
AT (1) ATE222341T1 (de)
AU (1) AU5751996A (de)
CA (1) CA2254978C (de)
CZ (1) CZ292563B6 (de)
DE (1) DE69623048T2 (de)
MX (1) MXPA98009613A (de)
WO (1) WO1997044618A1 (de)

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US8915731B2 (en) * 2010-12-30 2014-12-23 L'air Liquide Societe Anonyme Pour L'etude Et L'exploitation Des Procedes Georges Claude Flameless combustion burner
JP6998548B2 (ja) * 2017-04-18 2022-01-18 パナソニックＩｐマネジメント株式会社 燃料電池システム
JP6633028B2 (ja) * 2017-07-10 2020-01-22 大陽日酸株式会社 酸素富化バーナ及び酸素富化バーナを用いた加熱方法
GB201808070D0 (en) * 2018-05-18 2018-07-04 Rolls Royce Plc Burner
CN112902159A (zh) * 2021-01-22 2021-06-04 成都光华科技发展有限公司 一种三通道多氧燃烧器
KR102462131B1 (ko) * 2021-03-25 2022-11-03 현대제철 주식회사 용해로 버너 장치

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Also Published As

Publication number Publication date
CZ292563B6 (cs) 2003-10-15
WO1997044618A1 (en) 1997-11-27
DE69623048T2 (de) 2003-04-30
CA2254978C (en) 2008-09-09
AU5751996A (en) 1997-12-09
CA2254978A1 (en) 1997-11-27
EP0898687A1 (de) 1999-03-03
ATE222341T1 (de) 2002-08-15
EP0898687A4 (de) 2000-02-23
DE69623048D1 (en) 2002-09-19
CZ369798A3 (cs) 1999-04-14
MXPA98009613A (es) 2004-03-10

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