WO1995023315A1 - Procede et appareil de brûlage d'un combustible gazeux tres reactif - Google Patents

Procede et appareil de brûlage d'un combustible gazeux tres reactif Download PDF

Info

Publication number
WO1995023315A1
WO1995023315A1 PCT/NL1995/000059 NL9500059W WO9523315A1 WO 1995023315 A1 WO1995023315 A1 WO 1995023315A1 NL 9500059 W NL9500059 W NL 9500059W WO 9523315 A1 WO9523315 A1 WO 9523315A1
Authority
WO
WIPO (PCT)
Prior art keywords
flame
gas
fuel gas
burner
combustion
Prior art date
Application number
PCT/NL1995/000059
Other languages
English (en)
Inventor
Abraham Van Der Drift
Original Assignee
Stichting Energieonderzoek Centrum Nederland
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Stichting Energieonderzoek Centrum Nederland filed Critical Stichting Energieonderzoek Centrum Nederland
Priority to AU15920/95A priority Critical patent/AU1592095A/en
Publication of WO1995023315A1 publication Critical patent/WO1995023315A1/fr

Links

Classifications

    • 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 
    • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
    • F23C9/006—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber the recirculation taking place in the combustion chamber
    • 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
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • 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
    • F23D14/48—Nozzles
    • F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
    • 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
    • F23D14/74—Preventing flame lift-off
    • 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 
    • F23C2202/00—Fluegas recirculation
    • F23C2202/40—Inducing local whirls around flame
    • 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 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/9901—Combustion process using hydrogen, hydrogen peroxide water or brown gas as fuel

Definitions

  • the present invention relates to a method for burning a fuel gas, which method comprises the following steps: a) mixing the fuel gas with another gas which contains at least 3% oxygen, in such an amount that the amount of oxygen in the gas mixture thus obtained is at least 60% of the stoichiometric amount required for complete combustion of the fuel gas, b) passing the gas mixture thus obtained through a burner body having several outlet orifices, c) maintaining a flame above the burner body, which flame comprises several flame jets.
  • the US Patent 4,919.609 discloses such a method for burning natural gas. This involves the use of a burner in the form of a highly porous ceramic crucible having a porosity of approximately J0% or more, which is provided with expanded metal composed of iron. With this burner, an output of more than 3.000 kW/m 2 can be achieved, because the presence of the expanded metal - an essential element of said burner - promotes the recirculation of the gases produced during combustion, as a result of turbulent flue gas circulation zones being formed, which stabilize the flame. None is mentioned in this article, however, concerning the combustion of highly reactive fuels or concerning the N0 X emission of such combustion.
  • U.S. patent 5.102,392 describes a burner and a method for burning a fuel gas with low N0 X emission.
  • a burner plate comprises slot issues to which the fuel gas and combustion air are separately fed and from which they are separately discharged into the combustion chamber, thereby preventing flame propagation into the burner.
  • stable ignition of the fuel - i.e. a common fuel gas - is sustained by recirculation of hot combustion products in the areas between slots downstream of the burner plate. To achieve this, the spacing between the slots should be 5 to 8 inches.
  • this burner provides very low N0 X resulting from the low residence time of the nitrogen (from the combustion air) in the high intensity flame and the avoidance of hot spots within the flame due to the turbu ⁇ lence and uniform air-to-fuel ratio throughout the combustion chamber volume.
  • this reference is not related to the combustion of highly reactive fuel gases, i.e. fuel gases containing more than 70 % hydrogen, in which said highly reactive fuel gas is premixed with the combustion air.
  • the Dutch Patent Application 9200620 by Applicant discloses a ceramic burner for burning natural gas, which is formed from a highly porous ceramic foam, by means of which a large pressure drop and reduced N0 X emission can be achieved, the reduced N0 X emission being a result of a lower combustion temperature.
  • these burners having 60 pores per inch, can be used for burning hydrogen/natural gas mixtures containing at most S ⁇ % hydrogen, with an excess of air of 30% , a halving of the N0 X emission to approximately -.0 ppm being achievable.
  • the ceramic natural-gas burners described in said prior art cannot be used, however, for burning highly reactive fuels such as pure hydrogen or hydrogen/methane mixtures containing more than 70% of hydro ⁇ gen with a low excess of air (less than 50$), since a higher flame tem ⁇ perature is obtained and as a result the emission of nitrogen oxides (N0 X emission) increases greatly.
  • the object of the present invention is therefore to provide a method for burning highly reactive fuel/air mixtures, low N0 X emission being achieved at the same time.
  • a further object of the invention is to provide such a method in which stable and complete combustion without flashback or blow-off of the flame is achieved.
  • the distance between said flame jets is such that recirculation is achieved of the gases produced during combustion.
  • said internal flue gas circula- tion which according to the invention amounts to some tens up to perhaps even some hundreds of per cent, an N0 X emission is* achieved, surprisingly, which is much lower than the emission to be expected on the basis of the flame temperature.
  • the invention further relates to an appliance for burning a fuel gas in accordance with the abovementioned method, which appliance comprises a burner body which is provided with several spaced outflow orifices, characterized in that the distance between the outflow orifices is between 4.5 and 20 mm and the total area of the outflow orifices is from 0.5 to 30% , preferably from 1 to 4% of the total area of the burner body.
  • Figure 1 is a sectional side-view of a burner plate of the invention, which schematically depicts the flame jets and the internal flue gas circulation according to the invention;
  • FIGS. 2 - 5 are schematic top views of burner plates which can be used with the method according to the invention.
  • Figure 6 is a graph which depicts the N0 X emission for the combustion of 100% hydrogen as a function of the number of outlet ori ⁇ fices for various values of the excess of air and the output;
  • Figure 7 is a graph which depicts the N0 X emission for the combustion of the hydrogen/methane mixture as a function of the per ⁇ centage of hydrogen for various values of the excess of air and the out ⁇ put;
  • Figure 8 is a graph which depicts the N0 X emission for the combustion of 100% hydrogen as a function of the distance between the outlet orifices;
  • Figure 9 is a graph which depicts the H 2 emission for the combustion of 100% hydrogen as a function of the porosity of the burner plate for various values of the excess of air and the output;
  • Figure 10 is a graph which depicts the CO emission for the combustion of hydrogen/methane mixtures as a function of the output for various values of the hydrogen/methane ratio and the excess of air;
  • Figure 11 is a graph which depicts the CH, conversion for the combustion of hydrogen/methane mixtures as a function of the output for various values of the hydrogen/methane ratio and the excess of air;
  • Figure 12 is a graph which depicts the N0 X emission as a func ⁇ tion of the ratio between the outflow velocity of the gas mixture and the flame speed;
  • Figure 13 is a schematic sectional side-view of the open burner set-up used in the examples.
  • Figure 14 is a schematic sectional side-view of the enclosed burner set-up used in the examples.
  • Figure 15 is a schematic top view of the burner plate used in the examples.
  • the spacing between the flame jets in this application is to be understood as the distance between the middle (centre, centre line) of the flame jet and the middle of the nearest flame jet, as depicted in Figure 1.
  • the flame speed is to be understood, in this application, as the laminar flame speed of a freely propagating adiabatic flame.
  • Highly reactive fuel gases are to be understood, in this appli ⁇ cation, as mixtures of hydrogen and customary fuel gases, which contain at least 70% and preferably at least 80% hydrogen.
  • the customary fuel gas is in this context preferably selected from hydrocarbons such as methane, ethane, propane, butane, ethene, propene, butene, acetylene and the like, although it is also possible, for example, to use petrol vapour, methanol, ethanol and the like.
  • the highly reactive fuel gas is more preferably a mixture of at least 80% hydrogen and natural gas or methane. Further, according to a specific preferred embodiment of the invention, pure hydrogen gas is used.
  • the highly reactive hydrogen-containing fuel gases used in the invention have a high reactivity (high flame speed) and a high flame tem ⁇ perature, compared with, for example, natural gas. Consequently, these mixtures cannot be burnt by means of the highly porous natural-gas burners from the prior art without encountering flashback and/or unacceptably high N0 X emission.
  • a burner is used, of which but a small fraction of the surface is permeable, for example a burner having a small number of small straight-through outlet orifices.
  • 1 is the burner plate
  • 2 are the outlet orifices
  • 3. are the flame jets
  • 4 is the centre line of the flame jet, 5. being the recirculation.
  • N0 X during the combustion of nitrogen- containing fuel gases generally proceeds via equilibrium reactions in the flame, such reactions being generally known to those skilled in the art.
  • One example. is the Zeldovich mechanism: 0 + N 2 - NO + N N + 0 2 - NO + 0
  • the reduction in the N0 X emission in the case of the method according to the invention is a consequence of the shift of the abovementioned equi ⁇ libria to the left, which shift is achieved by the recirculation of the gases produced in the flame.
  • a lowering of the flame tempera ⁇ ture, a shorter residence time in the flame and further known factors are contributing, separately or in combination, to the reduction in the N0 X emission.
  • the distribution of the flame jets is therefore such that the recirculation flows cannot interfere with one another.
  • the distance between the flame jets is not less than 4.5 mm and preferably not less than 6 mm.
  • the maximum distance between the flame jets is not essential and is generally 20 mm, preferably 10 mm.
  • the highly reactive fuel gas is mixed, in a first step, with another gas which contains at least 3%. preferably at least 10%, oxygen.
  • another gas which contains at least 3%. preferably at least 10%, oxygen.
  • air or oxygen- enriched air is preferably used.
  • the oxygen-containing gas is admixed in such an amount, that the amount of oxygen present after mixing is at least 60%, preferably at least 80%, of the stoichiometric amount required for complete combustion of the fuel gas.
  • the combustion is preferably carried out with an excess of air of 0-50%, and more preferably 10-30%. Said excess of air can also be expressed in the parameter n, the ratio between the amount of oxygen present (in moles) and the amount of oxygen (in moles) which is required for complete combustion of the fuel gas.
  • n is at least 0.8, preferably 1.0 - 1.5 and more preferably 1.1 - 1.3.
  • the premixed combustible gas mixture is then passed through a burner body having various outlet orifices, while maintaining, above the burner body, a flame which consists of several flame jets.
  • flame jets refers to the separate small flames, indicated by 3. i n Figure 1, which together form the entire flame above the burner.
  • These flame jets generally correspond to the outlet orifices in the burner body, the shape, the distribution and the spacing of the flame jets being defined by the shape, the distance and the mutual distribution of the outlet orifices. It is also possible for an assembly of various very small outlet orifices to produce one flame jet.
  • the burner body and the outlet orifices may have any shape desired, as long as the desired ratio of the outflow velocity of the gas mixture and the flame speed is achieved, and the desired recirculation of the gases produced during combustion is obtained.
  • the outlet orifices may have the form of narrow slits, irregularly shaped openings, a plurality of concentric circles or assemblies of very small holes (for example in rows running parallel). Further possibilities will be evident to those skilled in the art.
  • the outlet orifices are preferably straight-through small holes, in particular round holes, which are distributed uniformly over the burner body, for example in the form of a star, a grid, rows running parallel, or concentric circles.
  • the shape of the burner body is likewise not essential.
  • the body may take the shape of a cylinder, a cone or a sphere, or a sec ⁇ tion thereof, as will be evident to those skilled in the art.
  • a burner plate is used. A number of possible burner plates is depicted in the Figures
  • Figure 2 depicts a burner plate 6 which is provided with straight-through outlet orifices 2 which are assembled in the shape of a star.
  • Figure 3 depicts a burner plate 8 which is provided with slit- shaped outlet orifices 9. running parallel.
  • Figure 4 depicts a burner plate 10 which is provided with con- centric circular outlet orifices 11.
  • Figure 5 depicts a burner plate 12 which is provided with a number of very small outlet orifices 13. which are assembled as rows running parallel. In this case, each row of the small outlet orifices 13 will produce a separate flame jet.
  • the burner body may further be made of any material suitable for the purpose, including metals such as iron, copper and the like.
  • the burner body is preferably a ceramic burner body and more preferably a ceramic burner plate.
  • the combustion of the highly reactive air/fuel mixture is carried out at a ratio between the gas velocity and the flame speed of from 5.0 to 45.0. If this ratio is greater than 45.0, the flame is blown off, whereas with a ratio of less than 5.0 flashback occurs.
  • the flame speed is a variable which can be calculated theoreti- cally and can be used to describe combustion. This parameter is known to those skilled in the art, , as are methods for determining it. Reference is made, inter alia, to Kirk-Othmer Encyclopedia of Chemical Technology,
  • the flame speed generally depends on the fuel mix used, the excess of air and the output supplied. The precise value of the flame speed may differ, however, depending on the method used for the determi ⁇ nation thereof, as is generally known to those skilled in the art.
  • the outflow velocity of the gas mixture in this application also referred to as the gas/air velocity, is controlled by the size and distribution of the outlet orifices (in particular, the ratio between the area of the outlet orifices and the total area of the burner plate) , the amount of fuel gas fed in per unit time, and the excess of air (these last two values, together with the composition of the fuel gas, also determine the output supplied). These parameters are controlled in such a way, according to the invention, that the desired outflow velocity is obtained, which is within the scope of those skilled in the art.
  • the area of the outflow orifices is 0.5 ⁇ 6%, preferably 1-4%, of the total area of the burner plate. In the case of the conventional ceramic natural-gas burners, said area forms more than 30% and often more than 60% of the total area.
  • the size of the outlet orifices is not critical. If the outlet orifices are too large, however, the risk of flashback becomes greater and, depending on the number of orifices, the flame speed may decrease unduly. If the orifices are too small, the pressure drop across the plate becomes too. high.
  • the outlet orifices are therefore preferably, for example, round holes having a diameter of less than 5 mm, more preferably of less than 3 mm.
  • the width of the slit is less than 5 mm, preferably less than 3 mm. Therefore, in general at least one of the dimensions of the orifices should be smaller than 5 mm, preferably smaller than 3 mm, and with a general minimum of 0.001 mm, preferably 0.01 mm.
  • the burner is a ceramic burner plate which is provided with round outlet orifices having a diameter of 0.5 - 1-5 mm. said holes being uniformly distributed over the area at 2 holes/cm 2 , for example in the form of a star, a grid or concentric circles.
  • the burner may also modulate, for example in a ratio of at least 1:5.
  • the output achieved essentially depends on the gas flow rate and is generally between 500 and 2000 kW/m 2 .
  • FIG. 7 depicts the N0 X emission for the combustion of hydrogen/methane mixtures as a function of the percentage of hydrogen for various values for the output and the excess of air (ceramic burner plate having 2.42 outlet orifices/cm 2 , dia ⁇ meter 1 mm) .
  • the driving force for internal flue gas circulation is the dynamic pressure differential created by velocity. Therefore: degree of recirculation: R • * - ⁇ p
  • degree of recirculation R • * - ⁇ p
  • the porosity is a measure for the ratio between the total area of the outlet orifices and the total area of the burner plate.
  • porosity in [%] O.785 • [number of holes/cm 2 ]
  • the porosity of the burner plate is therefore 0.5 ⁇ 30%, preferably 1-4%.
  • N0 X emission increases with an increase in the porosity, a reduction in the excess of air and/or a reduction in output, as is shown by Figure 6, in which the N0 X emission for the combustion of hydrogen is depicted as a function of the number of outlet orifices per cm 2 (round straight-through outlet orifices of dia- meter 1 mm) for various values of the output and the excess of air.
  • Figure 8 shows, an increase in the N0 X emission is produced if the distance between the outlet orifices (uniformly distributed round holes of diameter 1 mm) decreases with constant porosity, as a result of the interference between the recirculation flows.
  • the fraction of unburnt fuel which results according to the
  • FIGS 9 and 10 can also be explained. Flue gas recirculation is employed in many commercial burners in order to increase the stability of the flame. The mechanism is simple: the hot gases flowing back ignite the as yet unburned gases at an early stage. Consequently, the flame remains attached to the surface in spite of its high speed.
  • the mechanism applying- to a sur ⁇ face burner also operates: at a low gas/air velocity the plate will radiate, and the risk of flashback increases. A certain minimum velocity is therefore desirable to prevent this effect.
  • An increase in the velocity will, on the one hand, lead to greater "blow-off behaviour", but will, on the other hand, via flue gas recirculation, enhance the stability of the flame (attachment) . This lowers the surface temperature and enhances the flame stability and consequently the fuel slip.
  • the ratio between the outflow velocity of the gas mixture, the gas/air velocity, and the flame speed is a measure for the ratio between the degree of flue gas recirculation and surface temperature increase.
  • Stability ratio (gas/air velocity)/(flame speed).
  • the so-called "surface burner mechanism” will predominate and the surface will therefore become hot and it will be possible, therefore, for flashback to occur.
  • the internal flue gas recirculation predominates. If the ratio is too high, the flame will blow off.
  • H 2 is replaced by CH / ,.
  • the gas/air velocity hardly changes. It is therefore clear that stabilization of a CH/,/H 2 flame presents problems if the burner has been adapted for stable combustion of 100% H 2 .
  • n 1.3, admixture of 20% CH ⁇ is possible (the gas/air velocity is then 10 m/s) .
  • N0 X emission of less than 5 ppm is found to require a distance of at least 7 mm between the various holes.
  • the effect of a change in the excess of air can be ascribed to the change in •flame tem ⁇ perature going hand in hand with it.
  • Lowering n results in a higher N0 X emission and a lower fuel slip.
  • a minimum gas/air velocity of from 10 to 15 m/s is required to prevent flashback at 100% H 2 .
  • the fuel slip is considerable (a few hundred ppm) in the vicinity of this limit.
  • the invention further relates to an appliance for burning a fuel gas, said appliance comprising a burner body, the burner body being provided with several outlet orifices, the distance between the outlet orifices being between 4.5 and 15 mm and the total area of the outlet orifices being from 0.5 to 6%, preferably from 1 to 4%, of the total area of the burner body.
  • the burner body in this arrangement is, as specified above, preferably a ceramic burner body and more preferably a ceramic burner plate.
  • the burner body is a ceramic burner plate which is provided with uniformly distributed straight-through round outlet ori ⁇ fices having a diameter of from 0.5 to 1.5 mm.
  • the appliance may possibly also contain other known elements of burner appliances, such as a fuel gas supply, an air supply and a means for premixing the air and the fuel gas. All these and other elements and also their application will be evi ⁇ dent to those skilled in the art.
  • Figure 13 depicts a burner set-up with a supply 14 for the air/fuel gas mixture. This mixture is passed through the orifices 16 of a burner pate 15, said burner plate being clamped in the clamping construe- tion 17. The combustion of the fuel gas takes place in the combustion zone 18.
  • Figure 14 depicts an enclosed burner set-up, the fuel gas/air mixture being supplied via supply 19 and then being passed through the orifices 21 of a burner plate 20. The combustion takes place in the combustion zone 22. Then the discharge gases are passed over a heat exchanger 23 and discharged via discharge 24. Discharge 24 is provided with a flue gas sampling arrangement 25.
  • the set-up further comprises cooled walls 26, a peep hole for an IR pyrometer 27, a pyrometer 28 operating with suction, and thermocouples 29.
  • %H 2 percentage of hydrogen in the fuel gas
  • CO measured amount of carbon monoxide after combustion in ppm
  • C0 2 % measured amount of C0 2 in the flue gas in per cent
  • N0 X N0 X emission in ppm
  • C X H X hydrocarbon slip in ppm
  • Tplate°C temperature of the plate in °C.
  • Example I The combustion of 100% H 2 was carried out with a modified
  • the measures were carried out with the burner set-up depicted in Figure 13•
  • the emissions were measured by means of a probe (a water-cooled double tube for isokinetic flue gas sampling, which was positioned closely above the surface of the plate) , and the heat exchanger used was a quartz tube having a diameter of 100 mm and a length of 200 mm.
  • This plate is depicted in Figure 15 and comprises a ceramic plate 30 which is provided with round outlet orifices 31 (diameter 1 mm) . Owing to the reduced number of holes, the velocity per hole decreases and the flames shorten. Ignition is likewise improved, without an increase in the N0 X emission. TABLE 2
  • Example VI In this example, a ceramic burner plate was used with an area of 90 x 90 cm 2 with 196 uniformly distributed holes of diameter 1 mm. With this burner it was possible for 100% hydrogen to be burnt stably.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)

Abstract

Procédé consistant (a) à mélanger un gaz combustible à un autre gaz renfermant au moins 3 % d'oxygène, et ce selon une quantité telle que la quantité d'oxygène dans le mélange gazeux ainsi obtenu est égale à au moins 60 % de la quantité st÷chiométrique nécessaire à la combustion totale du gaz combustible; (b) à faire passer le mélange gazeux ainsi obtenu dans un corps de brûleur (1) comportant plusieurs orifices de sortie (2); et (c) à créer au-dessus du corps de brûleur (1) une flamme comportant plusieurs jets de flamme. Le gaz combustible est un gaz combustible très réactif que l'on fait passer dans le corps de brûleur (1) de telle manière que la distance entre les jets de flamme soit comprise entre 4,5 et 20 mm, et l'on réalise la combustion de sorte que le rapport entre le débit de sortie du mélange gazeux et la vitesse des flammes soit compris entre 5,0 et 45,0. Le corps de brûleur est de préférence une plaque de brûleur céramique (1) dans laquelle la superficie totale des orifices de sortie (2) représente 0,5 à 30 %, et de préférence 1 à 4 %, de la superficie totale de la plaque de brûleur (1). Ladite plaque est pourvue d'orifices de sortie ronds (2) dont le diamètre est compris entre 0,5 et 1,5 mm. Le gaz combustible très réactif est, de préférence, de l'hydrogène ou un mélange d'hydrogène et de méthane constitué à plus de 90 % d'hydrogène.
PCT/NL1995/000059 1994-02-23 1995-02-14 Procede et appareil de brûlage d'un combustible gazeux tres reactif WO1995023315A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AU15920/95A AU1592095A (en) 1994-02-23 1995-02-14 Method and apparatus for burning highly reactive gaseous fuel

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
NL9400280A NL9400280A (nl) 1994-02-23 1994-02-23 Werkwijze voor de verbranding van hoogreaktieve gasvormige lucht/brandstof-mengsels en branderinrichting voor het uitvoeren van deze werkwijze.
NL9400280 1994-02-23

Publications (1)

Publication Number Publication Date
WO1995023315A1 true WO1995023315A1 (fr) 1995-08-31

Family

ID=19863871

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/NL1995/000059 WO1995023315A1 (fr) 1994-02-23 1995-02-14 Procede et appareil de brûlage d'un combustible gazeux tres reactif

Country Status (3)

Country Link
AU (1) AU1592095A (fr)
NL (1) NL9400280A (fr)
WO (1) WO1995023315A1 (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997027428A1 (fr) * 1996-01-26 1997-07-31 Ygnis Holding S.A. Surface de bruleur
EP1154010A2 (fr) * 2000-05-09 2001-11-14 Linde Gas Aktiengesellschaft Procédé d'opération d'un brûleur
WO2011069839A1 (fr) 2009-12-11 2011-06-16 Bekaert Combustion Technology B.V. Brûleur pourvu d'une plateforme de brûleur à faible porosité
WO2019172925A3 (fr) * 2018-03-09 2019-12-26 Siemens Aktiengesellschaft Système de combustion à répartition à faible intervalle pour une turbine à gaz
JP2020063868A (ja) * 2018-10-16 2020-04-23 東京瓦斯株式会社 表面燃焼バーナ
WO2020182902A1 (fr) 2019-03-12 2020-09-17 Bekaert Combustion Technology B.V. Procédé d'actionnement de brûleur de modulation
DE102020121934B3 (de) * 2020-08-21 2021-05-20 Viessmann Werke Gmbh & Co Kg Gasbrennervorrichtung und Verfahren zum Betrieb einer Gasbrennervorrichtung
WO2021140036A1 (fr) * 2020-01-08 2021-07-15 Bekaert Combustion Technology B.V. Brûleur à gaz et appareil chauffant
NL2024623B1 (en) * 2020-01-08 2021-09-07 Bekaert Combustion Tech Bv Gas burner and heating appliance
EP3875854A1 (fr) 2020-03-06 2021-09-08 Robert Bosch GmbH Brûleur permettant de brûler un écoulement mixte carburant-air, ainsi que appareil de chauffage doté d'un tel brûleur
EP3879176A1 (fr) 2020-03-13 2021-09-15 Bosch Thermotechnology Ltd (UK) Chaudière avec un brûleur pare-flamme à prémélange
WO2022174864A1 (fr) * 2021-02-18 2022-08-25 Viessmann Climate Solutions Se Procédé pour faire fonctionner un brûleur à gaz
EP4092322A1 (fr) * 2021-05-20 2022-11-23 Beckett Thermal Solutions Ltd. Membrane de brûleur à gaz
EP4108985A1 (fr) 2021-06-21 2022-12-28 FERROLI S.p.A. Cellule de combustion pour un système de chauffage
WO2022269433A1 (fr) * 2021-06-21 2022-12-29 Ferroli S.P.A. Système de chauffage de gaz prémélangé pour h2
NL2028637B1 (en) * 2021-07-06 2023-01-12 Bekaert Combustion Tech Bv Premix gas burner system and method
WO2023078949A1 (fr) * 2021-11-04 2023-05-11 Bekaert Combustion Technology B.V. Brûleur à gaz à prémélange
DE102022212226A1 (de) 2022-11-17 2024-05-23 Robert Bosch Gesellschaft mit beschränkter Haftung Brenner

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3936003A (en) * 1973-12-03 1976-02-03 Raytheon Company Multiport high density burner
US4316881A (en) * 1978-06-08 1982-02-23 Sid Richardson Carbon & Gasoline Co. Carbon black process utilizing an improved burner
US4421474A (en) * 1982-08-25 1983-12-20 Meyer Stanley A Hydrogen gas burner
JPH01310217A (ja) * 1988-06-09 1989-12-14 Rinnai Corp 燃焼プレート
US5102329A (en) * 1991-04-15 1992-04-07 Coen Company, Inc. High intensity burner
EP0536706A2 (fr) * 1991-10-08 1993-04-14 Lüdi, Roger Procédé pour la fabrication d'un stabilisateur de flamme pour un brûleur radiant et stabilisateur de flamme produit selon ce procédé
WO1993007420A1 (fr) * 1991-10-03 1993-04-15 Nefit Fasto B.V. Procede et installation de combustion d'un melange gazeux

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3936003A (en) * 1973-12-03 1976-02-03 Raytheon Company Multiport high density burner
US4316881A (en) * 1978-06-08 1982-02-23 Sid Richardson Carbon & Gasoline Co. Carbon black process utilizing an improved burner
US4421474A (en) * 1982-08-25 1983-12-20 Meyer Stanley A Hydrogen gas burner
JPH01310217A (ja) * 1988-06-09 1989-12-14 Rinnai Corp 燃焼プレート
US5102329A (en) * 1991-04-15 1992-04-07 Coen Company, Inc. High intensity burner
WO1993007420A1 (fr) * 1991-10-03 1993-04-15 Nefit Fasto B.V. Procede et installation de combustion d'un melange gazeux
EP0536706A2 (fr) * 1991-10-08 1993-04-14 Lüdi, Roger Procédé pour la fabrication d'un stabilisateur de flamme pour un brûleur radiant et stabilisateur de flamme produit selon ce procédé

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 14, no. 107 (M - 0942) 27 February 1990 (1990-02-27) *

Cited By (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1997027428A1 (fr) * 1996-01-26 1997-07-31 Ygnis Holding S.A. Surface de bruleur
EP1154010A2 (fr) * 2000-05-09 2001-11-14 Linde Gas Aktiengesellschaft Procédé d'opération d'un brûleur
EP1154010A3 (fr) * 2000-05-09 2004-01-28 Linde AG Procédé d'opération d'un brûleur
EP2510281B1 (fr) 2009-12-11 2017-10-25 Bekaert Combustion Technology B.V. Brûleur pourvu d'une plateforme de brûleur à faible porosité
CN102597624A (zh) * 2009-12-11 2012-07-18 贝卡尔特燃烧技术股份有限公司 具有低孔隙率的燃烧器层面的燃烧器
JP2013513774A (ja) * 2009-12-11 2013-04-22 ベーカート・コンバスチョン・テクノロジー・ベスローテン・フェンノートシャップ 低多孔率バーナデッキを有するバーナ
WO2011069839A1 (fr) 2009-12-11 2011-06-16 Bekaert Combustion Technology B.V. Brûleur pourvu d'une plateforme de brûleur à faible porosité
KR101817371B1 (ko) * 2009-12-11 2018-01-11 베카에르트 컴버스천 테크놀러지 비.브이. 다공도가 낮은 버너 데크를 구비한 버너
EP3282187A1 (fr) * 2009-12-11 2018-02-14 Bekaert Combustion Technology B.V. Brûleur doté d'un pont de brûleur à faible porosité
WO2019172925A3 (fr) * 2018-03-09 2019-12-26 Siemens Aktiengesellschaft Système de combustion à répartition à faible intervalle pour une turbine à gaz
US11248795B2 (en) 2018-03-09 2022-02-15 Siemens Energy Global Gmbh & Co Kg Finely distributed combustion system for a gas turbine engine
JP2020063868A (ja) * 2018-10-16 2020-04-23 東京瓦斯株式会社 表面燃焼バーナ
WO2020182902A1 (fr) 2019-03-12 2020-09-17 Bekaert Combustion Technology B.V. Procédé d'actionnement de brûleur de modulation
NL2024623B1 (en) * 2020-01-08 2021-09-07 Bekaert Combustion Tech Bv Gas burner and heating appliance
WO2021140036A1 (fr) * 2020-01-08 2021-07-15 Bekaert Combustion Technology B.V. Brûleur à gaz et appareil chauffant
EP3875854A1 (fr) 2020-03-06 2021-09-08 Robert Bosch GmbH Brûleur permettant de brûler un écoulement mixte carburant-air, ainsi que appareil de chauffage doté d'un tel brûleur
EP3879176A1 (fr) 2020-03-13 2021-09-15 Bosch Thermotechnology Ltd (UK) Chaudière avec un brûleur pare-flamme à prémélange
DE102020121934B3 (de) * 2020-08-21 2021-05-20 Viessmann Werke Gmbh & Co Kg Gasbrennervorrichtung und Verfahren zum Betrieb einer Gasbrennervorrichtung
WO2022037747A1 (fr) 2020-08-21 2022-02-24 Viessmann Werke Gmbh & Co Kg Dispositif de brûleur à gaz et procédé pour faire fonctionner un dispositif de brûleur à gaz
WO2022174864A1 (fr) * 2021-02-18 2022-08-25 Viessmann Climate Solutions Se Procédé pour faire fonctionner un brûleur à gaz
EP4092322A1 (fr) * 2021-05-20 2022-11-23 Beckett Thermal Solutions Ltd. Membrane de brûleur à gaz
EP4108985A1 (fr) 2021-06-21 2022-12-28 FERROLI S.p.A. Cellule de combustion pour un système de chauffage
WO2022269433A1 (fr) * 2021-06-21 2022-12-29 Ferroli S.P.A. Système de chauffage de gaz prémélangé pour h2
NL2028637B1 (en) * 2021-07-06 2023-01-12 Bekaert Combustion Tech Bv Premix gas burner system and method
WO2023280923A1 (fr) * 2021-07-06 2023-01-12 Bekaert Combustion Technology B.V. Système et procédé de brûleur à gaz à pré-mélange
WO2023078949A1 (fr) * 2021-11-04 2023-05-11 Bekaert Combustion Technology B.V. Brûleur à gaz à prémélange
NL2029630B1 (en) * 2021-11-04 2023-06-02 Bekaert Combustion Tech Bv Premix gas burner
DE102022212226A1 (de) 2022-11-17 2024-05-23 Robert Bosch Gesellschaft mit beschränkter Haftung Brenner

Also Published As

Publication number Publication date
AU1592095A (en) 1995-09-11
NL9400280A (nl) 1995-10-02

Similar Documents

Publication Publication Date Title
WO1995023315A1 (fr) Procede et appareil de brûlage d'un combustible gazeux tres reactif
US5275552A (en) Low NOx gas burner apparatus and methods
US5980243A (en) Flat flame
EP0007697A1 (fr) Brûleur pour combustibles gazeux et/ou liquides ayant une teneur en NOx minimisée
US3990433A (en) Gas burner flame temperature amplifier
US4088741A (en) Carbon black process
US4669398A (en) Pulverized fuel firing apparatus
EP0537244A1 (fr) Procedes et appareil pour la combustion des gaz
US4250145A (en) Carbon black reactor with improved burner
US5448969A (en) Fluidic burner
US5551869A (en) Gas staged burner
CA1245544A (fr) Methodes et dispositifs de combustion a faible degagement de no.sub.x
CA2131863A1 (fr) Systeme de combustion a flamme blanche
US3255802A (en) Method and apparatus for producing flame jet and controlling temperature and flame stability of same
US4316881A (en) Carbon black process utilizing an improved burner
CA2531326C (fr) Dispositifs de chauffage alimentes en oxygene et combustible
US5216968A (en) Method of stabilizing a combustion process
AU2008200617B2 (en) Burner and method for combusting fuels
EP0506043B2 (fr) Brûleur pour la production de la suie et four utilisant un tel brûleur pour accumuler de la suie
Blevins et al. A study of radiant tube flame structure and NOx emissions
CA1245543A (fr) Methodes et dispositifs de combustion a faible degagement de no.sub.x
CA2244103A1 (fr) Surface de bruleur
US20240110699A1 (en) Process burner with distal flame holder
Negishi Lean premixture combustion on a coaxial burner
Raghavan et al. Burners for gaseous fuels

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AM AT AU BB BG BR BY CA CH CN CZ DE DK EE ES FI GB GE HU JP KE KG KP KR KZ LK LR LT LU LV MD MG MN MW MX NL NO NZ PL PT RO RU SD SE SI SK TJ TT UA US UZ VN

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): KE MW SD SZ UG AT BE CH DE DK ES FR GB GR IE IT LU MC NL PT SE BF BJ CF CG CI CM GA GN ML MR NE SN TD TG

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
NENP Non-entry into the national phase

Ref country code: CA

REG Reference to national code

Ref country code: DE

Ref legal event code: 8642

122 Ep: pct application non-entry in european phase