EP0494631B1 - Brûleur portatif pour gaz combustible avec deux tubes de mélange - Google Patents

Brûleur portatif pour gaz combustible avec deux tubes de mélange Download PDF

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Publication number
EP0494631B1
EP0494631B1 EP92100132A EP92100132A EP0494631B1 EP 0494631 B1 EP0494631 B1 EP 0494631B1 EP 92100132 A EP92100132 A EP 92100132A EP 92100132 A EP92100132 A EP 92100132A EP 0494631 B1 EP0494631 B1 EP 0494631B1
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EP
European Patent Office
Prior art keywords
mixing tube
burner
burner according
outlet end
nozzle
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
EP92100132A
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German (de)
English (en)
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EP0494631A3 (en
EP0494631A2 (fr
Inventor
Palle Ludvig Jeppesen
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.)
Rothenberger Werkzeugemaschinen GmbH
Original Assignee
Rothenberger Werkzeugemaschinen GmbH
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.)
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Publication date
Application filed by Rothenberger Werkzeugemaschinen GmbH filed Critical Rothenberger Werkzeugemaschinen GmbH
Publication of EP0494631A2 publication Critical patent/EP0494631A2/fr
Publication of EP0494631A3 publication Critical patent/EP0494631A3/de
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Publication of EP0494631B1 publication Critical patent/EP0494631B1/fr
Anticipated expiration legal-status Critical
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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
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • F23D14/64—Mixing devices; Mixing tubes with injectors
    • 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
    • F23D14/38—Torches, e.g. for brazing or heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D23/00—Assemblies of two or more burners

Definitions

  • the invention relates to a portable burner with a first injector nozzle for fuel gas, which is arranged in the region of a first suction point for primary air at the inlet end of a first mixing tube, with a swirl generator, which is at a distance in front of the outlet end of the first mixing tube forming a second nozzle with a nozzle axis this is arranged, and with a second mixing tube, the inner cross-section (F2) of which is larger than the inner cross-section (F1) of the first mixing tube and which is arranged concentrically with the outlet end of the first mixing tube directly generating a burner flame, an inlet end for the burner flame and second suction points for Has secondary air in the region of the outlet end of the first mixing tube and extends in the flow direction to its outlet end.
  • the fuel gas is usually obtained by vaporizing liquefied petroleum gas such as propane, butane or mixtures thereof and their pressure-controlled delivery.
  • a gas jet when entering a gaseous medium which is initially stationary, sets it in motion, to a certain extent entrains it and conveys it in the same direction.
  • This process also known as the injector process, is based on friction, turbulence and diffusion processes. It also takes place in an open atmosphere.
  • the efficiency can be increased by having these processes run in a tubular housing which is composed of nozzles, line sections, inlet and outlet openings.
  • the jet suction device or the jet pump including the diffusion pump
  • the gas burner including the Bunsen burner familiar from school lessons.
  • the initial impulse of the gas jet which is usually generated by a nozzle (conversion of pressure into speed), is distributed over the entrained gas. If there is a lack of guidance, the cross section of the gas jet quickly becomes larger and slower until the energy is used up by friction and / or - after deducting the losses - has been converted back into pressure.
  • the second mixing tube is either (A) in its entire length without openings, or (B) the openings extend to the outlet end or in any case in the immediate vicinity of the outlet end of the second mixing tube.
  • the secondary air flows in essentially in the axial direction, which will be explained in more detail below.
  • the second mixing tube is widened at the inlet end and forms an inlet cone or a type of spatial elbow with the adjacent walls of the combustion chamber, which deflects the cold air drawn in near the wall of the mixing tube in a purely axial direction before the cold air reached the burner flame.
  • Temperature compensation can only be achieved through the divergence of the flame beam and edge turbulence.
  • the outlet opening of the combustion chamber is oval or slit-shaped, this can only be done in one plane.
  • a temperature stratification is maintained at least over a considerable length of the second mixing tube, so that a temperature profile with a maximum in the middle is generated at the outlet opening of the second mixing tube: the hot core of the gas jet extends correspondingly far.
  • the second mixing tube is completely open at the inlet end. Due to the even distribution of the perforations over the whole or most of the length of the mixing tube, this has practically no effect:
  • the hot gas jet acts like a free jet, which is also expressly pointed out.
  • suction takes place essentially in the axial direction: cold air and Hot gas flow essentially parallel to each other, and there is a far-reaching gas jet with a hot core, ie with a temperature stratification, which is only gradually reduced, ie with increasing distance from the combustion chamber, by jet divergence and mixing.
  • EP-OS 0 240 751 discloses a low-pressure hand burner in which a hot flame core is separated from the combustion chamber wall by a jacket flow of cool ambient air without a swirl generator. Here too, a hot, far-reaching flame is generated, which emerges from the combustion chamber.
  • the sheath flow cooling the combustion chamber wall is achieved by sucking in the ambient air through the rear of the burner, in which there are openings which produce an air flow parallel to and in the immediate vicinity of the combustion chamber wall. This parallel flow is wanted and complicates a mixing process.
  • a non-generic burner with two series-connected injection systems for the suction of primary and secondary air is known, which is to be screwed stationary with a fixed line with the vertical alignment of all nozzles. It should be achieved by several adjusting devices and the design specification for the flow channels that the respective gas-air mixture completely fills the cross-section of the flow channel arranged downstream of each nozzle and that such a flow speed with graded stoichiometric mixing ratios is achieved that the burner flame does not strike back into the flow channels . According to regulations, no flame burns in the last, cold injection tube. Rather, a far-reaching hot flame emerges from the last mouth. A turbulence of the gases within the burner should even be explicitly avoided.
  • the invention is therefore based on the object of improving a burner of the type specified in such a way that it produces a hot gas stream of relatively low temperature and with a temperature distribution which is as uniform as possible when the length of the second mixing tube is limited.
  • no visible flame should emerge from the outlet opening of the second mixing tube in order to use the burner to temperature-sensitive materials such as roofing felt, roofing foils and the like, even when operated improperly. to be able to process.
  • the feature a) prevents or suppresses the formation of an axially parallel flow of the secondary air from the start.
  • Characteristic b) ensures that the sucked-in secondary air hits the starting section of the burner flame at a right angle and favors its swirling and mixing with the secondary air at a very early point in time.
  • the secondary air drawn in transversely thus serves, as it were, to break up any cool edge or jacket flow that would be expected due to the swirl generator and to prevent it from forming again.
  • the transversely entering secondary air not only slows down the swirl and centrifugal effect, which is desirable in the end of the first mixing tube, but also the formation of an excessive axial speed in the area of the jet axis. The result is great uniformity in the diametrical temperature profile at the outlet end of the second mixing tube.
  • the average temperature of the hot gas is relatively low; it is between about 500 and 650 ° C. Above all, no flame emerges from the burner, so that temperature-sensitive materials such as roofing felt and roof foils can be processed even by inexperienced people.
  • the burner's inherent safety is due to the warranty obligation e.g. a roofing company of crucial importance.
  • the design of the first injector system is such that a largely stoichiometric gas mixture is generated which already allows complete combustion.
  • the addition of large amounts of secondary air does not serve to continue the combustion process, but to lower the temperature while increasing the mean flow rate, since the heat transfer is improved with the flow rate.
  • the relative shortness of the second mixing tube makes production cheaper and easier to use.
  • the absence of any openings in the area beyond the second suction points favors the mixing process over the entire cross section of the second mixing tube.
  • energy losses occur due to the spreading of the hot gas flow and mixing with air volumes lying apart, as is the case in the prior art with such second mixing tubes which are large over their entire length or at least most of their length Openings are provided so that practically a free jet is formed. This in turn leads to temperature stratification.
  • a particularly simple burner design is obtained if the filler body is designed as a rotationally symmetrical part with an inner bore for inserting the first mixing tube and with at least one outer surface for attaching the second mixing tube.
  • the packing is the only and also simply designed and rigid coupling part between the two mixing tubes.
  • the filling body is provided with axial suction openings for secondary air. If you now close the radial suction openings in the second mixing tube, the flame emerges from the second mixing tube in the form of a hot core. In this case, the burner can also be lit at the outlet opening of the second mixing tube, which also demonstrates the insufficient gas mixture. With the radial inflow according to the invention, this does not succeed because the ignition limit of the gas mixture is clearly undershot at all points. In this case you have to use the burner ignite through the radial suction openings.
  • outlet end of the first mixing tube forming the nozzle protrudes from the end face of the filling body by 4 to 15 mm, preferably by 6 to 12 mm.
  • a practically proven value is 9 mm.
  • the nozzle at the end of the first mixing tube is, so to speak, the injector nozzle for the second mixing tube.
  • Their effect is not necessarily dependent on the nozzle being formed by narrowing the first mixing tube; the increase in gas velocity through the combustion process is already sufficient to produce an intake effect.
  • the ratio of the distance (d) from the end face of the swirl generator to the end edge of the outlet end of the first mixing tube to the inside diameter (D1) of the first mixing tube is at least 1.0, preferably 1.1 to 1.5.
  • the swirl generator has guide vanes which are distributed around the axis (AA) of the first mixing tube and whose angle of attack with respect to the axis (AA) on the outer diameter of the swirl generator is less than 40 degrees, preferably less than 35 degrees. It has been shown that the angle of attack should be selected to be smaller with increasing burner output given the dimensions of the mixing tubes. It is also advantageous if the swirl generator is chamfered significantly on the inlet side and if the angle of the surface lines of the bevel with respect to a radial plane at least largely corresponds to the angle of attack of the guide vanes with respect to the axis AA.
  • the second suction points are designed as axially parallel slots distributed over the circumference of the second mixing tube, the end portions of which are oriented towards the filler body or the nozzle at least partially overlap with the partial section of the first mixer tube protruding from the end face of the filler body.
  • the proportion of all slots, as seen in the circumferential direction, should be at least 50 percent of the total circumference of the second mixing tube.
  • An upper limit is only given by the strength limits of the material of the second mixing tube, since the slots naturally weaken the material.
  • the ratio of the sum of the cross-sectional areas of all the slots to the inner cross section of the second mixing tube should be at least 1.2 and should preferably be between 1.4 and 1.5.
  • the ratio of the length of each individual slot to the length of the second mixing tube projecting beyond the packing is between 0.10 and 0.20, preferably between 0.14 and 0.17. This ensures a sufficiently large closed length of the second mixing tube.
  • the burner is attached to a cross member with several identical burners with their axes (A-A) aligned parallel to one another and forming a burner battery and connected to a common gas supply line running parallel to the cross member.
  • the burner battery is provided with castors, whose horizontal axes of rotation are perpendicular to the burner axes (A-A).
  • baffle plates are arranged on both sides of the burner battery, the vertical main planes of which run parallel to the burner axes.
  • FIG. 1 shows a basic element of a portable burner 1 with a first injector nozzle 2, to which the fuel gas is fed via a line 3 from a liquid gas container, not shown.
  • the injector nozzle 2 is arranged in the region of a first suction point 4 for primary air at the inlet end 5 of a first mixing tube 6.
  • the suction point 4 consists of four radial bores 7 distributed over the circumference.
  • An insert 8, which forms a Venturi tube, is located in the first mixing tube immediately following the bores 7.
  • the insert 8 is followed by a mixing section 9 which merges into a swirl generator 10 which consists of a hub with radially projecting guide vanes 11.
  • the guide vanes can also be formed by material sections between oblique bores in a cylindrical body.
  • the angle of attack of the guide vanes 11 on the outer diameter of the swirl generator 10 or the axes of the bores with respect to the axis (A-A) is 30 degrees.
  • the swirl generator 10 has an end face 12 which is arranged at a distance "d" of 32 mm in front of the outlet end 13 of the first mixing tube 6 which forms a second nozzle with a nozzle axis.
  • the swirl generator 10 has five guide vanes 11 and five intermediate channels 11a with an angle of attack of 30 degrees.
  • the swirl generator is tapered in order to form a chamfer, and at the same angle of 30 degrees, but with respect to a radial plane to the axis A-A. This favors the flow and more air / fuel gas mixture can be passed through to increase performance.
  • the diameter of the smallest circumferential edge on the chamfer is approximately the core diameter of the swirl generator 10.
  • the circular end edge 14 of the outlet end 13 of the first mixing tube 6 is rounded inward so far that the free diameter "Dd" of the nozzle is 21 mm, i.e. the diameter is reduced by 19.23%, the cross section by 34.76%; the exit speed is increased accordingly.
  • the downstream end of the first mixing tube 6 is inserted into an inner bore 15 of a filler body 16, which is designed as a rotationally symmetrical part and has at least one outer surface 17 for fitting a second mixing tube 18.
  • the ratio of the internal cross section (F2) of the second mixing tube 18 to the internal cross section (F1) of the first mixing tube 6 is therefore approximately 4.31.
  • the second mixing tube 18 is arranged concentrically to the outlet end 13 of the first mixing tube 6 and has an inlet end 19 for the burner flame and second suction points 20 for secondary air.
  • the radial distance between the outlet end 13 of the first mixing tube 6 and the inlet end 19 of the second mixing tube is closed by the filler body 16.
  • the end face 21 of the filling body extends essentially radially to the nozzle axis (A-A), and the outlet end 13 of the first mixing tube 6, which forms the second nozzle, projects from it by a predetermined dimension "s", which in the present case is 9 mm.
  • the second suction points 20 for the secondary air are arranged exclusively in the area of the outlet end 13 of the first mixing tube 6 and are radially aligned with the nozzle axis A-A. As a result, the secondary air is directed essentially perpendicularly to the initial section of the burner flame running in the direction of the nozzle axis.
  • the second mixing tube 18 has a closed jacket part 18a, the length of which is 5.17 times the axial extent of the second suction points 20. Particular attention should be paid to the location and dimensions of these second suction points:
  • the second suction points 20 are distributed axially parallel to the circumference of the second mixing tube 18 Slots 24 formed. There are 7 slots with a width of 13 mm, which are rounded in a semicircle at both ends. The length "LS" is 47 mm, so that an entry cross section of 475 mm2 per slot or a total cross section of 3,325 mm2 is calculated. The ratio of this total cross section to the inside cross section of the second mixing tube is 1.45.
  • the length of the slots also ensures that the secondary air has a considerable amount of air Part of the initial section of the flame, not shown, strikes and forces it to swirl.
  • FIG. 1 shows the basic building block for various stages of the burner according to the invention.
  • FIG. 4 shows that a hand torch can be formed from this by attaching a handle 26 with a connecting thread 27 for a gas hose to the filling body 16.
  • a connecting piece 28 between the handle 27 and the filler 16 there is a gas valve 29 with an adjustment button 29a.
  • the connecting piece 28 is connected beyond the gas valve 29 to the injector nozzle 2 via a gas line 30.
  • the hand torch can be supplemented by a piezo igniter, one ignition electrode of which is located in front of the end edge 14 of the first mixing tube (not shown).
  • FIG. 5 and 6 show a burner battery 31 for simultaneous heating of large areas.
  • the burner battery is formed in that a burner 1a according to FIG. 1 with several similar burners 1b, 1c, 1d,... Is attached to a cross member 32 with their axes (AA) parallel to one another and to a common gas supply line running parallel to the cross member 33 are connected.
  • a guide rod 34 with a handle 35 is attached to the cross member 32, and a feed line 36 with a gas valve 37 is attached to the guide rod, which is connected to a gas hose 38, which leads to a liquid gas container, not shown, with a pressure regulator.
  • the burner battery 31 is provided with castors 39, only one of which is shown and whose horizontal axes of rotation are perpendicular to the burner axes.
  • baffles 40 and 41 are arranged on both sides of the burner battery, the vertical main planes of which run parallel to the burner axes.
  • the lower edges 42 of the guide plates are located just above the processing area.
  • the baffles are pivotally attached upwards and backwards.

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

Claims (17)

  1. Brûleur portable (1) comportant une première buse d'injection (2) pour du gaz combustible, laquelle est agencée dans la région d'un premier emplacement d'aspiration (4) pour de l'air primaire à l'extrémité d'entrée d'un premier tube de mélange (6), comprenant un générateur de tourbillons (10), qui est agencé dans le premier tube de mélange et à distance avant l'extrémité de sortie (13) de ce premier tube de mélange, ladite extrémité formant une seconde buse avec un axe de buse, et comprenant un second tube de mélange (18), dont la section transversale intérieure (F2) est supérieure à la section transversale intérieure (F1) du premier tube de mélange, et qui est agencé concentriquement par rapport à l'extrémité de sortie du premier tube de mélange qui produit directement une flamme de brûleur, ledit second tube de mélange (18) possédant une extrémité d'entrée (19) pour la flamme et des seconds emplacements d'aspiration (20) pour de l'air secondaire dans la région de l'extrémité de sortie (13) du premier tube de mélange (6), et s'étendant en direction d'écoulement jusqu'à son extrémité de sortie (23),
    caractérisé en ce que
    a) entre l'extrémité de sortie (13) du premier tube de mélange (6) et l'extrémité d'entrée (19) du second tube de mélange (18) est agencé un corps de remplissage (16), qui remplit au moins essentiellement la distance radiale entre les deux extrémités de tube et présente une surface frontale (21) qui s'étend sensiblement radialement par rapport à l'axe de buse (A-A), l'extrémité de sortie (13) du premier tube de mélange (6), qui forme la seconde buse, dépassant de ce corps de remplissage (16) d'une distance "s" prédéterminée, et en ce que
    b) les seconds emplacements d'aspiration (20) pour l'air secondaire sont agencés exclusivement dans la région de l'extrémité de sortie (13) du premier tube de mélange (6) et sont dirigés radialement vers l'axe de buse (A-A), de telle sorte que l'air secondaire atteint sensiblement perpendiculairement le tronçon initial de la flamme de brûleur qui s'étend dans la direction de l'axe de buse, et que le second tube de mélange (18) présente entre les seconds emplacements d'aspiration (20) et son extrémité (23) une partie d'enveloppe fermée (18a), dont la longueur est au moins le triple de l'extension axiale des seconds emplacements d'aspiration (20).
  2. Brûleur selon la revendication 1, caractérisé en ce que le corps de remplissage (16) est réalisé sous la forme d'une pièce à symétrie de révolution, comportant un perçage intérieur (15) pour la mise en place du premier tube de mélange (6), et au moins une surface extérieure (17) pour la mise en place du second tube de mélange (18).
  3. Brûleur selon la revendication 1, caractérisé en ce que l'extrémité de sortie (13) du premier tube de mélange (6), qui forme la buse, dépasse de 4 à 15 mm, de préférence de 6 à 12 mm, au-delà de la surface frontale (21) du corps de remplissage (16).
  4. Brûleur selon la revendication 1, caractérisé en ce que l'arête frontale circulaire (14) de l'extrémité de sortie (13) du premier tube de mélange (6) est incurvée vers l'intérieur et de manière arrondie, sur 15 à 25 %, de préférence 19 à 21 %, du diamètre intérieur du premier tube de mélange (6).
  5. Brûleur selon la revendication 1, caractérisé en ce que le rapport entre la distance (d) depuis la surface frontale terminale (12) du générateur de tourbillons (10) jusqu'à l'arête frontale (14) de l'extrémité de sortie du premier tube de mélange (6), et le diamètre intérieur (D1) du premier tube de mélange (6) s'élève à au moins 1,0, de préférence 1,1 à 1,5.
  6. Brûleur selon la revendication 1, caractérisé en ce que le générateur de tourbillons (10) possède des pales de guidage (11) réparties autour de l'axe (A-A) du premier tube de mélange (6), dont l'angle d'inclinaison par rapport à l'axe (A-A) au niveau du diamètre extérieur du générateur de tourbillons est inférieur à 30°, de préférence inférieur à 20°, et en ce que l'angle d'inclinaison est choisi plus faible pour des capacités croissantes de brûleur, pour des dimensions données.
  7. Brûleur selon la revendication 1, caractérisé en ce que le rapport entre la section transversale intérieure (F2) du second tube de mélange (18) et la section transversale intérieure (F1) du premier tube de mélange (6) est compris entre 4,0 et 4,8, de préférence environ 4,3.
  8. Brûleur selon la revendication 1, caractérisé en ce que les seconds emplacements d'aspiration (20) sont réalisés sous la forme de fentes (24) parallèles à l'axe et réparties à la périphérie du second tube de mélange (18), dont les tronçons d'extrémité (24a) dirigés vers le corps de remplissage (16) recouvrent au moins partiellement le tronçon partiel du premier tube de mélange (6) qui dépasse au-delà de la surface frontale (21) du corps de remplissage (16).
  9. Brûleur selon la revendication 8, caractérisé en ce que la proportion de toutes les fentes (24), vues dans la direction périphérique, s'élève à au moins 50 %, par rapport à la circonférence totale du second tube de mélange (18).
  10. Brûleur selon la revendication 9, caractérisé en ce que le rapport entre la somme des surfaces de section transversale de toutes les fentes (24) et la section transversale intérieure "F2" du second tube de mélange (18) s'élève à au moins 1,2, et est de préférence compris entre 1,4 et 1,5.
  11. Brûleur selon la revendication 8, caractérisé en ce que le rapport entre la longueur "LS" de chaque fente individuelle (24) et la longueur "L" du second tube de mélange (18) qui dépasse au-delà du corps de remplissage (16) est compris entre 0,10 et 0,20, de préférence entre 0,14 et 0,17.
  12. Brûleur selon la revendication 1, caractérisé en ce que le générateur de tourbillons (10) présente un chanfrein sur son côté amont, le diamètre de la plus petite arête périphérique du chanfrein correspondant sensiblement au diamètre de l'âme (diamètre extérieur moins longueur radiale des pales de guidage).
  13. Brûleur selon la revendication 12, caractérisé en ce que l'angle d'inclinaison des pales de guidage (11) par rapport à l'axe (A-A) est sensiblement égal à l'angle entre les lignes enveloppes du chanfrein et un plan radial par rapport à l'axe (A-A).
  14. Brûleur selon la revendication 1, caractérisé en ce que le brûleur (1, 1a) est fixé avec plusieurs brûleurs du même type (1b, 1c, 1d, ...), avec agencement parallèle de leurs axes (A-A) les uns par rapport aux autres et en formant une batterie de brûleurs (31), sur un élément de support transversal, et ils sont raccordés à une conduite d'alimentation en gaz commune (33).
  15. Brûleur selon la revendication 14, caractérisé en ce que la batterie de brûleurs (31) est dotée de galets de déplacement (39), dont les axes de rotation s'étendent perpendiculairement aux axes des brûleurs (A-A).
  16. Brûleur selon la revendication 14, caractérisé en ce que des tôles de guidage (40, 41) sont agencées des deux côtés de la batterie de brûleurs (31), dont les plans principaux s'étendent parallèlement aux axes des brûleurs (A-A).
  17. Brûleur selon la revendication 16, caractérisé en ce que les tôles de guidage (40, 41) sont agencées de manière à pouvoir basculer sur l'élément de support transversal (32).
EP92100132A 1991-01-11 1992-01-07 Brûleur portatif pour gaz combustible avec deux tubes de mélange Expired - Lifetime EP0494631B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4100657 1991-01-11
DE4100657A DE4100657A1 (de) 1991-01-11 1991-01-11 Tragbarer brenner fuer brenngas mit zwei mischrohren

Publications (3)

Publication Number Publication Date
EP0494631A2 EP0494631A2 (fr) 1992-07-15
EP0494631A3 EP0494631A3 (en) 1992-12-02
EP0494631B1 true EP0494631B1 (fr) 1995-05-24

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EP92100132A Expired - Lifetime EP0494631B1 (fr) 1991-01-11 1992-01-07 Brûleur portatif pour gaz combustible avec deux tubes de mélange

Country Status (5)

Country Link
US (1) US5213494A (fr)
EP (1) EP0494631B1 (fr)
DE (2) DE4100657A1 (fr)
DK (1) DK0494631T3 (fr)
NO (1) NO177547C (fr)

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US6827573B2 (en) * 2002-10-25 2004-12-07 Brown & Williamson Tobacco Corporation Gas micro burner
US7488171B2 (en) * 2002-10-25 2009-02-10 R.J. Reynolds Tobacco Company Gas micro burner
DE10306229A1 (de) * 2003-02-13 2004-08-26 Rasmusson, Hans Selektiv ansteuerbare Brennermodule für gasförmige und flüssige Brennstoffe
US20050227195A1 (en) * 2004-04-08 2005-10-13 George Kenneth R Combustion burner assembly having low oxides of nitrogen emission
US20070231755A1 (en) * 2004-04-30 2007-10-04 Icopal A/S Gas Fired Heating Device and a Method of Generating a Flow of Hot Air
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NO177547B (no) 1995-06-26
DE59202271D1 (de) 1995-06-29
NO177547C (no) 1995-10-04
EP0494631A3 (en) 1992-12-02
EP0494631A2 (fr) 1992-07-15
DE4100657A1 (de) 1992-07-16
DK0494631T3 (da) 1995-10-09
NO920133D0 (no) 1992-01-10
US5213494A (en) 1993-05-25
NO920133L (no) 1992-07-13

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