EP0834040B1 - Foyer avec un dispositif de brûleur et procédé de fonctionnement d'un foyer - Google Patents

Foyer avec un dispositif de brûleur et procédé de fonctionnement d'un foyer Download PDF

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Publication number
EP0834040B1
EP0834040B1 EP97924865A EP97924865A EP0834040B1 EP 0834040 B1 EP0834040 B1 EP 0834040B1 EP 97924865 A EP97924865 A EP 97924865A EP 97924865 A EP97924865 A EP 97924865A EP 0834040 B1 EP0834040 B1 EP 0834040B1
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EP
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Prior art keywords
combustion
combustion air
fuel
combustion chamber
distributor
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EP97924865A
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German (de)
English (en)
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EP0834040A1 (fr
Inventor
Ahmad Al-Halbouni
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WALTER BRINKMANN GMBH
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AL HALBOUNI AHMAD
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • 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
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2201/00—Staged combustion
    • F23C2201/20—Burner staging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2205/00—Assemblies of two or more burners, irrespective of fuel type

Definitions

  • the invention relates to a combustion chamber with a burner device and a corresponding method for an NO x - and CO-lean combustion in accordance with the preamble of claim 1 and 13 respectively.
  • the combustion air is usually either in a so-called mixing tube gradually added to the fuel (see GB 1444 673 A) or it is added to the Mostly outside of the fuel jet and outside the flame area supplied annular distributor. (see DE-OS 4 419 345 and DE-OS 4 231 788).
  • Other Constructions have multiple slots or openings on the combustion chamber wall and / or Fuel rating within the combustion chamber (see US Pat. No. 5,461,865 A and US Pat. No. 4 931 012). Because of the considerable spatial distance of the combustion air distribution devices from the flame area, is in practical operation with such Burners uniform mixing of fuel and combustion air or a staged mix based on given proportions not achieved.
  • the gas burner according to JP 57-058010 A Combustion air to a larger area of the combustion zone by means of an internal one double-walled distribution body and the lower part of the combustion zone enclosing, drilled wall distributed.
  • This type of air grading grants a better one Mastery of the mixing ratios, but in addition to its complexity, it is also ineffective in terms of heat transfer because the outer combustion wall absorbs the heat shields from the actual combustion chamber wall.
  • the invention is therefore based on the object to provide a combustion chamber with a burner device and a method of operating this burner means through which an NO x - and CO-lean combustion and an intensification is the heat release reached at the wall, simple in design and for a Compact design suitable with predominantly separate supply of fuel and combustion air to the combustion chamber, in which the combustion air is fed in as many stages as possible into larger flame areas.
  • this object is achieved by a combustion chamber with a burner device and a method the characterizing features of claim 1 and 13 solved.
  • the basic concept of the invention which also the claimed method for Operating the burner device involves the following: Approx. 70 to 100 vol.% Of total amount of combustion air supplied is determined by means of one or more Combustion air distribution body in a predominantly radial direction in the direction of the flame filled space between the outer wall of the firebox and the contour of the Combustion air distributors along all or a large part of the flame length fed. This results in a large-scale distribution of the combustion air to the entire flame area or on large parts of the flame area.
  • the fuel is fed into the combustion zone exclusively in the area of the flame base located at the foot part of the combustion air distribution body by means of one or more rows of nozzles arranged around the combustion air distribution body.
  • the remaining part of the combustion air required for the combustion ie 0 to approx. 30% by volume, is mixed into the fuel before entering the combustion zone.
  • the admixture of this part of the combustion air increases the momentum of the fuel, improves the mixing of fuel and combustion air and leads to the ignition limit being reached more quickly.
  • the NO x values drop drastically.
  • the advantages of this concept are that the combustion is initially sub-stoichiometric and, with a gradually increasing air supply, only shortly before the tip of the flame changes into stoichiometry or over-stoichiometry, where complete burnout is achieved. In this way, temperature peaks in the entire flame area are suppressed and the formation of pollutants (NO x and CO) is drastically reduced.
  • This type of feeding of the combustion air also has the advantageous effect that the flame is blown away from the combustion air distribution body, so that no direct combustion takes place on the surface of these combustion air distribution bodies. This lowers the thermal load on the combustion air distribution bodies, especially since they are additionally cooled by the combustion air flowing through them.
  • a further advantageous effect of the combustion air supply according to the invention is that they also cool the flame, thereby reducing the formation of NO x .
  • the geometry of the combustion zone is largely determined by the geometry of these combustion air distributors.
  • An essential function of the combustion air distribution body is therefore seen in the fact that the size of the combustion chamber is decisively influenced by the choice of its dimensions.
  • the contour of the combustion air distribution bodies there is a large variety of variants for designing the contour of the combustion air distribution bodies.
  • the choice of a suitable shape for the combustion air distribution body can optimize the NO x and CO emissions and heat transfer.
  • the outer wall 3 consists of a cylindrical jacket wall 3a, a cover wall 3b and one Bottom wall 3c.
  • Firebox details are not shown in the schematic drawing like viewing openings for visual observation of the flame development in the combustion chamber, Openings for the ignition of the gas-air mixture and for temperature measurement in the lower one Part of the firebox.
  • a UV probe for monitoring the Flame and a suction probe for exhaust gas extraction to carry out the concentration analysis of the exhaust gas emerging at the exhaust outlet 6.
  • the exhaust outlet 6 is in the Cover wall 3b of the furnace arranged.
  • the fire or combustion chamber 2 can also polygon shaped as a prism, but always has a horizontal or vertical arranged longitudinal central axis 34.
  • the heat is removed from the outer wall 3 via cooling water, the either in coils 16 and / or in water chambers 17 flows around the outer wall 3.
  • the combustion air distribution body 7 consists of simple sheet steel with a large number of openings 11 for the exit of the combustion air into the combustion zone. While the almost horizontal head part 9 of the combustion air distribution body is closed, the foot part 8 remains open and is screwed into the air supply pipe 18.
  • the total combustion air or most of it (> 70 vol.% of the total for the Combustion air flow rate of 100% required) is via the inner tube 18th of a coaxial tube, the combustion air supply 5 into the interior of the combustion air distribution body 7 by means of a fan 19 provided with a motor 20.
  • the lower end of the inner tube 18 of the coaxial tube opens into the combustion air supply 5.
  • the cylinder ring 21 is directly on the foot part of the combustion air distribution body 7 with a Provide row of nozzles 12.
  • This row of nozzles 12 has a variety of around Combustion air distribution body 7 arranged around fuel nozzles 13 for distribution of the fuel into the combustion zone in two perpendicular to each other Beam directions 14 crossing planes crossing the longitudinal center axis 34 are used (see Figures 3a-3d).
  • the burner output was determined for relatively small combustion air distributors (length 25-30 cm, width at the foot part 2-3 cm and at the head part 0-10 cm, with a length of the fire or Combustion chamber of 80 cm) to values between 10 and 22 kW and the air ratio varies between 1.1 and 1.5.
  • combustion air distributors length 25-30 cm, width at the foot part 2-3 cm and at the head part 0-10 cm, with a length of the fire or Combustion chamber of 80 cm
  • the distribution body shown in FIG. 1a, to which the measured values in FIGS. 4 and 5 relate was at a total length of approx. 30 cm at the foot part approx. 2.5 cm wide.
  • the contour of the combustion air distribution body did not glow and remained relatively cold (below 300 ° C.) in all designs according to FIG. 2a.
  • the exhaust gas analysis showed, as the measurement data in FIGS. 4 a, 4 b, 5 a and 5 b show, particularly with an increased fuel nozzle pulse, extremely low NO x and CO emission values, which are far below the legal limit values for industrial burners.
  • a major advantage of the invention is therefore the possibility of a energy-saving and environmentally friendly incinerator with compact burner and Build combustion chamber shape that is used for heat generation at smaller outputs up to 100 kW (such as in household appliances, wall-mounted heaters and boilers), with medium outputs, > 100 kW to 1 MW (e.g. in heating centers, thermal power stations and biomass combustion) and also for larger capacities> 1 MW (e.g. in power plant furnaces and rotary kilns) is suitable.
  • FIG. 1b schematically shows an arrangement of a plurality of combustion air distribution bodies 7 in a combustion chamber for industrial purposes in power plant technology.
  • the firebox 2 has a square cross section; the combustion air distribution body shown have the same features as in Fig. 1 a and are on the lower wall 3c, as above explained, installed.
  • the heat is dissipated via the built in the outer wall Water pipes 23 and the evaporator and superheater heating surfaces 24 and 25.
  • a further heat extraction is via an air preheater, which the combustion air of the Brenner preheated, reached in the exhaust duct, which is not shown in the schematic drawing is shown.
  • FIG. 2 a shows a schematic representation of different geometric variants of the Combustion air distribution body.
  • These can be square, cylindrical, conical, have polygon prism or pyramidal shape or their contour can be ellipsoidal or be hyperbolic. Other geometric designs are possible.
  • all combustion air distribution bodies have an internal cavity for the supply of Combustion air, a thin surrounding the cavity with a variety of Porous wall with openings, a closed head part and an open one Foot part on.
  • the dimensions of the combustion air distribution body and the number and Geometry of the openings on their circumference should be chosen so that they are one Controlled combustion process to ensure the combustion air distribution body.
  • the length (A) of the combustion air distribution body 7 is ⁇ 40-85% of the combustion chamber length (B), the diameter (C) of the combustion air distribution body 7 at the base part 8 is ⁇ 10% of the combustion chamber diameter (D), and the porosity of the combustion air distribution body is ⁇ 20%.
  • FIG. 3 a shows a schematic illustration of variants of the jet directions of the fuel nozzles 13, which are positioned in a row of nozzles 12 or more rows of nozzles at the foot part of the combustion air distribution body 7 and arranged around the latter.
  • a row of nozzles 12 contains a plurality of nozzles, the jet direction 14 of which can be changed both in the longitudinal central axis and at an angle to it.
  • this allows the fuel to be distributed over different contour areas of the combustion air distribution body, which contributes to the targeted control of the mixing ratios and promotes ignition.
  • fuel swirl can be generated, which leads to more intensive mixing of fuel and combustion air and to the longer residence time of the fuel particles in the flame area.
  • Both fuel nozzle settings (axial and tangential tilt) ensuring together in conjunction with the continuously flowing air from the openings of the combustion air distributor is a NO x - and CO combustion.
  • the tests carried out have shown that the optimum range of the axial and tangential inclination angles of the fuel nozzles is from approximately -45 ° to + 45 ° in relation to the longitudinal direction of the combustion zone.
  • the angle setting depends on the shape of the combustion air distribution body and has a great influence on the quality of the combustion.
  • the admixture of small amounts of air ( ⁇ 30 ° of the combustion air volume flow) with the fuel leads to improved mixing of the fuel and combustion air and to faster reaching the ignition limit due to the increased impulse.
  • the NO x values drop drastically.
  • the rows of nozzles are to be manufactured for different load ranges and should be exchangeable his; that can e.g. B. happen as follows, as Fig 3 b shows: The coaxial ring 21 closed and immediately before the fuel enters the combustion chamber Providing connecting channels 32 for the fuel supply into the combustion chamber, the channels 32 have internal threads 33 and the fuel nozzles 13 have external threads 28. The Fuel nozzles 13 are screwed into the connecting channels 32.
  • oblique bores 29 or an annular gap 30 can be used with an inner swirl generator 31, as shown in FIG. 3 c and 3 d illustrate.
  • the graphs in FIGS. 4 a and 5 a show the NO x and CO emission values measured in the exhaust gas as a function of the burner output at different air ratios for the variant shown in FIG. 1 a with the conical combustion air distribution body.
  • Natural gas H was fed as fuel by means of a single row of nozzles, the nozzles being adjusted such that every second nozzle was provided with a weak swirl. While the burner output for the relatively small pilot plant was varied between 10 and 22 kW, air figures for the usual and interesting range of 1.2 to 1.5 have been set for combustion plants.
  • the NO x and CO emission values shown have been converted to 3 vol.% O 2 in the exhaust gas so that a comparison with the limit values of the TA-Luft is possible.
  • FIG. 4 b shows an admixture of approx. 20% combustion air to the fuel and otherwise the same settings as in FIG. 4 a, extremely low NO x emission values for all air ratios and for all examined load ranges.
  • the axial and tangential setting of the fuel nozzles has a particular influence on the NO x and CO formation, but depending on the combustion air distribution body used there are different optimal angular positions.
  • the NO x and CO emission values of the new burner device are significantly below the limit values of TA-Luft (NO: 114 ppm, CO: 93 ppm) and the new BImSchV (NO: 45 ppm, CO: 55 ppm ) and that even the production of CO-free exhaust gas from combustion processes is possible.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Incineration Of Waste (AREA)

Claims (14)

  1. Chambre de combustion ayant un dispositif à brûleur pour une combustion pauvre en NOx et en CO, avec apport séparé d'une manière prépondérante de combustible et d'air de combustion à la chambre de combustion, tout l'air de combustion ou la plus grande partie de l'air de combustion étant étagé en continu en plusieurs points de l'espace et envoyé à la chambre de combustion,
       caractérisée en ce que
    a) il est prévu un tube (18, 22) coaxial à l'une des extrémités duquel le tube (18) intérieur communique avec au moins un conduit (5) d'alimentation pour l'apport d'air de combustion et le tube (22) extérieur avec au moins un conduit (4) d'alimentation pour l'apport de combustible ou d'un mélange de combustible et d'air de combustion et à l'autre extrémité duquel un répartiteur (7) d'air de combustion est relié de manière étanche avec le tube (18) intérieur et au moins une rangée (12) de tubes comportant plusieurs buses (13) pour le combustible ferme de manière étanche l'anneau (21) cylindrique compris entre le tube (18) intérieur et le tube (22) extérieur,
    b) le répartiteur (7) pour l'air de combustion est constitué d'une cavité intérieure s'étendant en longueur qui est entourée d'une paroi mince perforée ou poreuse et comporte une tête (9) fermée, un pied (18) ouvert et une pluralité d'orifices (11) répartis pour la sortie de l'air de combustion dans la zone de combustion,
    c) le répartiteur (7) pour l'air de combustion est relié de manière étanche par son pied (8) au tube (18) intérieur du tube coaxial,
    d) le rapport (A/B) de la longueur (A) du répartiteur (7) pour l'air de combustion à la longueur (B) de la chambre (2) de combustion et le rapport (C/D) du diamètre (C) extérieur du répartiteur (7) pour l'air de combustion au pied (8) au diamètre (D) intérieur de la chambre (2) de combustion sont tels qu'il se forme un mélange inflammable et qu'il s'établit une combustion stable,
    e) la direction (14) du jet des buses de combustible dans la même rangée (12) de buses et/ou la direction (14) du jet des buses pour le combustible de la rangée (12) de buses voisine sont réglées de manière séparée,
    f) le dispositif de combustion dans la chambre (2) de combustion est tel qu'il passe à travers la paroi (3) extérieure qui l'entoure et a avec elle une liaison étanche et l'extrémité du tube (18, 22) coaxial avec les conduits (5 et 4) d'alimentation pour l'apport d'air de combustion et de combustible reste en dehors de la chambre (2) de combustion, toute la longueur du répartiteur (7) pour l'air de combustion se trouve dans la chambre (2) de combustion et les buses (13) pour le combustible font saillie dans la chambre (2) de combustion, mais la distance du pied (8) du répartiteur (7) pour l'air de combustion au début des orifices (11) n'est pas dépassée,
    g) la zone de combustion dans la chambre (2) de combustion est en même temps la zone pour le mélange complet de l'air de combustion sortant des orifices (11) au combustible ou au mélange de combustible et d'air sortant des buses (13) pour le combustible,
    h) le volume et la géométrie de la zone de combustion correspondent sensiblement au volume et à la géométrie de l'espace (1) vide qui est délimité par la paroi (3) extérieure entourant la chambre (2) de combustion, par le contour extérieur du répartiteur (7) pour l'air de combustion et par un plan (10) imaginaire à l'intérieur de la chambre (2) de combustion et passant par l'extrémité de la tête (9) du répartiteur (7) pour l'air de combustion.
  2. Chambre de combustion suivant la revendication 1, caractérisée en ce que
    a) la porosité du répartiteur (7) pour l'air de combustion est telle qu'il s'établit approximativement dans la zone de combustion des domaines de valeurs prescrits de l'indice λ d'air d'un domaine hypostoechiométrique au voisinage du pied (8) au domaine hyperstoechiométrique au voisinage de la tête (9),
    b) la position et le nombre des orifices (11) sur le contour du répartiteur (7) pour l'air de combustion sont choisis de façon que la quantité de mouvement des courants d'air de combustion sortant des orifices (11) éloigne la flamme du répartiteur (7) pour l'air de combustion de sorte qu'il n'y a pas de combustion sur la paroi du répartiteur (7) pour l'air de combustion et que cette paroi n'est pas portée au rouge,
    c) il est prévu, au voisinage des buses pour le combustible, des moyens d'inflammation du mélange se formant dans la zone de combustion.
  3. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que la cavité intérieure du répartiteur (7) pour l'air de combustion est entourée d'une paroi unique qui a la forme d'un parallélépipède, d'un cylindre, d'un cône, d'un prisme polygonal ou d'une pyramide ou son contour est ellipsoïdal ou hyperbolique.
  4. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que la paroi du répartiteur (7) pour l'air de combustion est en un matériau céramique poreux ou en un matériau métallique qui est conformé en tamis, en tôle perforée, en toile métallique, en grille ou en treillis métallique, ou en ce que le répartiteur (7) pour l'air de combustion est constitué sous la forme d'un comprimé en fil métallique ou d'un corps fritté.
  5. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que le répartiteur (7) pour l'air de combustion a des dispositifs de déviation pour produire un courant turbulent de l'air de combustion.
  6. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que répartiteur (7) pour l'air de combustion et/ou les buses (13) ou les rangées (12) de buses sont constitués de manière à pouvoir être remplacés.
  7. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que la direction (14) du jet des buses (13) pour le combustible dans la même rangée (12) de buses et/ou dans les rangées (12) voisines de buses est dirigée sur des parties de longueurs différentes du répartiteur (7) pour l'air de combustion et/ou les buses (13) pour le combustible sont inclinées de façon à donner de la turbulence au courant de combustible.
  8. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que les buses (13) pour le combustible sont dans une rangée (12) de buses constituées sous la forme d'orifices (29) inclinés ou de fentes (30) annulaires ayant un dispositif (31) intérieur de production de turbulence.
  9. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que la chambre (2) de combustion est cylindrique et comporte une paroi (3, 16, 17) pour l'évacuation de la chaleur.
  10. Chambre de combustion suivant la revendication 1, caractérisée
       en ce que la longueur (A) du répartiteur (7) représente de 30 % à 85 % de la longueur (B) de la chambre (2) de combustion, en ce que le diamètre (C) du répartiteur (7) dans la région des sorties du combustible, représente entre 10 % et 60 % du diamètre (D) intérieur de la paroi (3a) de la chambre de combustion.
  11. Chambre de combustion suivant la revendication 9, caractérisée
       en ce qu'il est prévu dans la chambre (2) de combustion en aval du répartiteur (7) un autre échangeur (24) de chaleur.
  12. Chambre de combustion suivant la revendication 7, caractérisée
       en ce que les buses (13) pour le combustible sont disposées parallèlement les unes aux autres et en étant inclinées par rapport à l'anneau (21) cylindrique, de manière à obtenir un tourbillonnement annulaire, ou sont disposées en étant inclinées sur l'anneau (21) cylindrique en divergeant ou en convergeant par rapport au cercle (35) de buses de manière à obtenir un courant s'élargissant ou se contractant, ou sont disposées inclinées sur l'anneau (21) cylindrique en étant inclinées dans les deux directions.
  13. Procédé pour faire fonctionner une chambre de combustion suivant les revendications 1 à 12, caractérisé en ce que
    a) on envoie environ 70 à 100 % en volume du débit total d'air de combustion apporté au moyen d'au moins un répartiteur (7) pour l'air de combustion principalement en direction radiale dans la zone de combustion emplie des flammes le long de toute la longueur des flammes ou d'une grande partie de la longueur des flammes et on les mélange au combustible ou au mélange d'air et de combustible sortant des buses (13) de combustible,
    b) on envoie le combustible dans la zone de combustion au moyen des buses (13) pour le combustible, dans la région de la base des flammes, au pied du répartiteur (7) pour l'air de combustion et autour de celui-ci,
    c) on ajoute au combustible avant l'entrée dans la zone de combustion la proportion restante en volume de l'air de combustion nécessaire à la combustion,
    d) on allume le mélange formé dans la zone (1) de combustion à proximité des buses (13) de combustible et on le brûle dans la même zone sans autre répartition,
    e) la flamme se forme dans tout l'espace de la zone (1) de combustion et les gaz brûlés de combustion sortent sans obstacle à travers le plan (10) imaginaire et quittent la chambre de combustion par l'orifice (6) de sortie des gaz brûlés,
    f) suivant les paramètres de fonctionnement et le type de combustible, on prévoit un réglage déterminé de l'angle des buses (13) pour le combustible, des orifices (29) ou du dispositif (31) de production de turbulence en combinaison avec un rapport déterminé de mélange de l'air de combustion dans le courant de combustible pour obtenir une flamme invisible ou visible et/ou des valeurs minimum d'émission de NOx et de CO dans les gaz brûlés.
  14. Procédé suivant la revendication 13, caractérisé en ce que
    on envoie le combustible ou le mélange de combustible et d'air dans un intervalle angulaire d'environ -45° à +45° rapporté à la direction longitudinale de la zone de combustion et
    la proportion de l'air de combustion dans le courant de combustible envoyé est comprise dans un intervalle de valeur représentant de 0 à 30 % en volume environ de tout le débit d'air de combustion qui est apporté.
EP97924865A 1996-04-20 1997-04-18 Foyer avec un dispositif de brûleur et procédé de fonctionnement d'un foyer Expired - Lifetime EP0834040B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19615761 1996-04-20
DE19615761 1996-04-20
PCT/DE1997/000817 WO1997040315A1 (fr) 1996-04-20 1997-04-18 BRULEUR ET PROCEDE DE FONCTIONNEMENT D'UN BRULEUR DESTINE A UNE COMBUSTION PAUVRE EN NOx ET EN CO

Publications (2)

Publication Number Publication Date
EP0834040A1 EP0834040A1 (fr) 1998-04-08
EP0834040B1 true EP0834040B1 (fr) 2000-08-09

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EP97924865A Expired - Lifetime EP0834040B1 (fr) 1996-04-20 1997-04-18 Foyer avec un dispositif de brûleur et procédé de fonctionnement d'un foyer

Country Status (6)

Country Link
US (1) US6419480B2 (fr)
EP (1) EP0834040B1 (fr)
AT (1) ATE195367T1 (fr)
DE (2) DE19717721A1 (fr)
ES (1) ES2151273T3 (fr)
WO (1) WO1997040315A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013019934A1 (de) 2013-11-25 2015-05-28 Brinkmann Industrielle Feuerungssysteme Gmbh Verfahren und Vorrichtung zur Erzeugung von Heiß-/Trocknungsgasen

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Publication number Priority date Publication date Assignee Title
AT406507B (de) * 1997-11-24 2000-06-26 Vaillant Gmbh Brenner mit separater zufuhr von brennstoff
AT407565B (de) * 1998-08-03 2001-04-25 Vaillant Gmbh Gebläsebrenner
AT406899B (de) * 1998-10-08 2000-10-25 Vaillant Gmbh Einrichtung zur erzeugung von elektrischem strom und wärme mit mindestens einer brennstoffzelle
AT408266B (de) * 1999-02-19 2001-10-25 Vaillant Gmbh Heizeinrichtung
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DE59702133D1 (de) 2000-09-14
US20010018171A1 (en) 2001-08-30
DE19717721A1 (de) 1997-10-30
ATE195367T1 (de) 2000-08-15
EP0834040A1 (fr) 1998-04-08
US6419480B2 (en) 2002-07-16
WO1997040315A1 (fr) 1997-10-30
ES2151273T3 (es) 2000-12-16

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