EP0175875A1 - Brûleur à huile ou à gaz pour la génération de gaz à chaud - Google Patents

Brûleur à huile ou à gaz pour la génération de gaz à chaud Download PDF

Info

Publication number
EP0175875A1
EP0175875A1 EP85109292A EP85109292A EP0175875A1 EP 0175875 A1 EP0175875 A1 EP 0175875A1 EP 85109292 A EP85109292 A EP 85109292A EP 85109292 A EP85109292 A EP 85109292A EP 0175875 A1 EP0175875 A1 EP 0175875A1
Authority
EP
European Patent Office
Prior art keywords
mixing tube
openings
burner according
nozzle
diameter
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.)
Granted
Application number
EP85109292A
Other languages
German (de)
English (en)
Other versions
EP0175875B1 (fr
Inventor
Winfried Prof. Dr.-Ing. Buschulte
Erich Adis
Manfred Bader
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.)
Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsches Zentrum fuer Luft und Raumfahrt eV
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 Deutsches Zentrum fuer Luft und Raumfahrt eV filed Critical Deutsches Zentrum fuer Luft und Raumfahrt eV
Priority to AT85109292T priority Critical patent/ATE34447T1/de
Publication of EP0175875A1 publication Critical patent/EP0175875A1/fr
Application granted granted Critical
Publication of EP0175875B1 publication Critical patent/EP0175875B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details
    • F23D11/40—Mixing tubes; Burner heads

Definitions

  • the invention relates to a burner for generating hot gas with a nozzle from which a fuel jet enters a mixing tube, with a diaphragm surrounding the outlet of the nozzle, which burner housing into an upstream prechamber accommodating the nozzle and a downstream combustion chamber accommodating the mixing tube divided, with a central passage in the orifice for the passage of the fuel jet emerging from the nozzle and with a number of openings in the orifice surrounding the passage through which combustion air enters the mixing tube from the prechamber, the openings being located within a surface , which results from the projection of the clear mixing tube cross-sectional area onto the screen.
  • combustion air is supplied to the fuel, which is fed centrally via a nozzle, through openings are arranged in an aperture surrounding the nozzle.
  • the combustion air and the fuel are mixed downstream of the nozzle in a mixing chamber which is arranged in a mixing tube in the known burners.
  • a flame front forms during operation, from which hot gases outside the mixing tube flow back to a recirculation opening at the upstream end of the mixing tube.
  • This object is achieved according to the invention in a burner of the type described in the introduction in that the distance between the edges of adjacent openings is at least 50% of the opening diameter and / or in that the openings in the diaphragm in the flow direction are preceded by at least one air duct which is at least in the radial direction outer edges of the openings smoothly merging into the openings.
  • the openings surrounding the nozzle in the diaphragm had been arranged so that the edges. Adjacent openings are close together in order to achieve the largest possible passage area for the combustion air, it has been found that an increase in this distance leads to a reduction in noise. Accordingly, the distance between adjacent openings in the circumferential direction of a pitch circle should be at least 50% of the opening diameter. Such an increase in the distance between the combustion air openings leads to a reduction in the noise level of a few dB ( A ).
  • An air duct upstream of the openings directs the combustion air approximately parallel before it passes through the openings and before it enters the mixing chamber, so that less disturbed flow can be achieved. This prevents turbulence from being carried into the mixing chamber which would otherwise continue in the flame and in the recirculation flow and would lead to increased combustion noises.
  • An arrangement has proven to be particularly advantageous in which the longitudinal axes of the openings are inclined to converge in the flow direction with respect to the longitudinal axis of the mixing tube, preferably with an angle of inclination between 3 ° and 6 °.
  • This can be achieved by arranging the openings in the diaphragm itself or by deforming the diaphragm in such a way that the longitudinal axes of the openings are inclined with respect to the longitudinal axis of the mixing tube.
  • the channel is formed by a tube piece surrounding the nozzle at a concentric distance.
  • a common air supply channel is thus assigned to all openings, which is formed by the annular gap between the inner wall of the pipe socket and the nozzle.
  • the annular gap can be arranged along a cone narrowing in the direction of flow. This additionally achieves an effect which reduces the turbulence in the air flow, which is particularly advantageous in particular in combination with an opening with an inclined longitudinal axis.
  • the noise-reducing effect of the pipe section is particularly favorable if its length is between 10 and 120% of its inside diameter in the transition area to the openings; this length is preferably between 20 and 70% of the inside diameter, and it is very particularly favorable if this length is between 30 and 50% of the inside diameter of the pipe piece.
  • each opening is assigned its own air duct, which merges smoothly into the opening. It can also be provided here that the air guide channels narrow conically in the flow direction.
  • the air ducts can be arranged on a cylindrical surface concentrically surrounding the nozzle, in a modified embodiment they are arranged on a conical outer surface concentrically surrounding the nozzle. It is advantageous if the longitudinal axis of the channels is inclined between 3 ° and 6 ° with respect to the longitudinal axis of the mixing tube, since then optimal mixing takes place in the interior of the mixing tube without the undesirable turbulence occurring.
  • the air duct can be worked into a common guide body concentrically surrounding the nozzle.
  • the length of these air supply ducts corresponds to 0.5 to 4 times the radial distance of the openings from the longitudinal axis of the nozzle, preferably to 2 to 3 times the radial distance of these openings from the longitudinal axis of the nozzle.
  • annular gap concentrically surrounding the nozzle which is immediately adjacent, is arranged in the diaphragm and is connected to the antechamber. Combustion air can also flow into the mixing chamber very close to the longitudinal axis of the nozzle through this annular gap which immediately surrounds the passage opening of the nozzle through the orifice.
  • the openings in the diaphragm can have a circular cross section, but it is also possible to use other cross sections, for example the openings can have the shape of ring sections.
  • the adjacent openings can be on a common circle around the nozzle axis, but they can also be offset from one another in the radial direction, so that, for example, openings are arranged on two concentrically arranged partial circles which are offset from one another.
  • the distance between the edges of adjacent openings is more than 50% of the opening diameter, in particular more than 100%.
  • the mixing tube has a larger diameter at its upstream end than at its downstream end.
  • the mixing tube can narrow in steps or conically.
  • the upstream end of the mixing tube has an inner diameter which is larger than the diameter of a circumferential circle lying on the outer sides of the openings; in a modified embodiment, the inner diameter can also be chosen so that it is equal to the diameter of this circumferential circle.
  • recirculation openings are provided in the jacket of the upstream end of the mixing tube which adjoins the orifice and are arranged at a distance from the orifice so that there is a closed piece of pipe between the orifice and the recirculation openings located.
  • the length of the pipe section preferably corresponds to approximately 1/4 of the mixing pipe diameter.
  • a further pipe section adjoins the mixing tube downstream, the diameter of which is at most as large as that of the downstream end of the mixing tube.
  • This piece of pipe is advantageously at a distance from the downstream end of the mixing tube which is between 1/10 and 1/4 of the diameter of the mixing tube. It is advantageous if the length of this pipe piece is between 1/2 and 1 diameter of the mixing tube, preferably 2/3 of this diameter. Also by this measure The overall sound level is reduced, namely by pressing a core flow again through a constriction after leaving the large mixing tube part, with the aim of dampening the vortex formation occurring at the inner mixing cone of the flow.
  • each of the measures relating to the supply of the combustion air into the mixing tube also contributes to a desired reduction in noise on its own.
  • Each of these measures can be combined to further reduce the noise with each of the features relating to the design of the mixing tube. Protection is therefore expressly claimed for the combination of all of these features or some of these features as well as for the individual features relating to the combustion air supply to the mixing tube.
  • the invention relates to a wide variety of oil or gas burners and is discussed below using the example of a so-called blue burner, ie a burner in which oil is completely burned with a blue flame.
  • a so-called blue burner ie a burner in which oil is completely burned with a blue flame.
  • the Erfin but is not limited to such blue burners, for example, the desired noise reduction can be achieved with the described design measures even with warming-up burners and yellow burners.
  • the burner shown in FIGS. 1 and 2 comprises a cylindrical burner housing 1, which is subdivided into an upstream antechamber 3 and a downstream combustion chamber 4 by a wall, which is referred to below as an orifice 2.
  • the orifice 2 has a central passage 5 , in which a nozzle 6 is inserted, which is connected to a fuel supply line 7.
  • the longitudinal axis of the nozzle 6 coincides with the longitudinal axis of the burner housing.
  • a cylindrical mixing tube 8 Downstream of the orifice 2 is connected to this a cylindrical mixing tube 8 which, via circumferential slots 9 immediately after the orifice 2, forms a connection between its interior 10 forming the mixing space and an annular space 11 serving as a recirculation space, which surrounds the mixing tube 8 concentrically.
  • An ignition device 12 is led from the prechamber through the diaphragm 2 and ends at the outlet end of the mixing tube 8, so that ignition can take place in this area.
  • a measuring probe 13 is inserted from the antechamber through the orifice 2 into the combustion chamber 4.
  • a number of openings 14 are arranged, each with a circular cross section, which ver create bond between the prechamber 3 and the interior 10 surrounded by the mixing tube 8 in the combustion chamber 4.
  • the nozzle 6 is surrounded at a distance by a cylindrical pipe section 15 which extends up to the diaphragm 2.
  • the inside diameter of this pipe section 15 is selected such that the inner wall of the pipe section 15 merges smoothly into the openings 14 in the region of the outer edges of the openings 14, as is clear from FIG. 2.
  • the radius of the circle on which the openings 14 lie lies between the outer radius of the nozzle 6 and the radius of the inner wall of the pipe section 15, so that the openings 14 with the inner region of their edge are the envelope of the nozzle 6 touch, with the outside area the inner wall of the pipe section 15.
  • the number of openings 14 along the circle surrounding the nozzle is selected such that webs 16 remain between the openings, the width of which is at least 50% of the diameter of the openings 14. It is particularly advantageous if the inside diameter of the pipe section 15 is slightly smaller than the inside diameter of the mixing pipe 8. This allows a maximum distance of adjacent openings in the circumferential direction to be achieved with a given cross-sectional area of the openings 14, this maximum distance leading to the best possible noise reduction. If the inside diameter of the pipe section is increased beyond the inside diameter of the mixing tube, there is again an increase in noise despite the even greater distances between adjacent bores.
  • fuel for example gas or oil
  • the nozzle can in use; of oil as an atomizer nozzle.
  • Combustion air is introduced through the openings 14 into the interior 10 of the mixing tube 8, so that fuel and combustion air mix intimately with one another in the interior 10.
  • this mixture is ignited and burns in a flame front which is located approximately in the area of the outlet-side end of the mixing tube in accordance with the respective flow rate.
  • the combustion air is passed through the pipe section 15 through an annular channel 17 surrounding the nozzle 6 before the combustion air can enter the interior 10 of the mixing pipe 8 through the openings 14.
  • the air flow is calmed, so that the air passes through the openings 14 largely without turbulence.
  • the turbulence is also reduced in the mixing tube 8 and in the combustion area compared to a construction in which the air enters the mixing tube 8 directly from the prechamber without a guide channel upstream of the openings 14. Due to the low turbulence, there is a significant reduction in noise during the burning process itself.
  • the tube piece 15 is cylindrical in the embodiment shown in Figure 1 (solid lines).
  • the pipe section 15 has the shape of a truncated cone, and a parallel inner wall forms with the pipe section an annular gap 17 running along a truncated cone jacket.
  • Such an arrangement is shown in Figure 1 with dash-dotted lines. This arrangement also contributes to a calming of the air flow.
  • FIGS. 3 and 4 A burner of similar construction is shown in FIGS. 3 and 4, parts corresponding to one another have the same reference numerals.
  • the mixing tube 8 is frustoconical, the inlet end having an outer diameter which is substantially larger than the diameter of the circle on which the openings 14 are arranged. It has been found that this conical narrowing of the mixing tube leads to an additional reduction in noise during the burning process.
  • an air supply duct comparable to the pipe section 15 is missing. Instead, the openings 14 are chamfered on their side facing the prechamber 3. These chamfers, which are incorporated directly into the diaphragm 2, also form air guide channels which lead to a substantial calming of the combustion air flowing into the mixing tube and thus to a reduction in noise. These chamfers are effective in their own right in reducing noise, but their effect can be combined particularly advantageously with other upstream air supply ducts, for example with the pipe section 15 of the exemplary embodiment in FIGS. 1 and 2.
  • the nozzle 6 is surrounded by a guide body 18, in which axially parallel channels 19 are incorporated, in such a way that each opening 14 is assigned its own channel 19.
  • the channels 19 enter the respective opening 14 smoothly.
  • the channels 19 have the same cross section over their entire length, but it can be provided that the channels 19 narrow in the direction of flow.
  • the channels 19 can run axially parallel in the guide body, as shown in solid lines in FIG. 5, but they can also be arranged on a conical jacket, as is indicated by dash-dotted lines in FIG. It is advantageous if the inclination of the channels 19 with respect to the longitudinal axis of the nozzle is between 3 ° and 6 °. It has been found that optimal noise reduction can be achieved with such an arrangement. In this case, too, the channels themselves can still narrow in the direction of flow. It is important in this context that in all cases the channels 19 pass into the openings 14 smoothly, so that no turbulence can occur in this transition area.
  • the mixing tube 8 is extended compared to the exemplary embodiments in FIGS. 1 to 4, so that the length is approximately up to three times as large as the inside diameter of the mixing tube inlet.
  • This extension of the mixing tube also contributes to an additional reduction in noise.
  • the extended mixing tube has an ignition in one of the orifices To allow 2 near area, the mixing tube points in this.
  • FIG. 7 A further preferred exemplary embodiment of a burner is shown in FIG. 7, in which corresponding parts are again identified by the same reference numerals.
  • annular space 21 which surrounds the nozzle 6 in the region of the opening 5 and which opens into an annular gap 22 surrounding the opening 5 is incorporated into the guide body 18.
  • the annular gap 22 can be formed by the opening 5 itself, which then has a diameter which is somewhat larger than the diameter of the nozzle 6 in this area.
  • the annular space 21 communicates with the prechamber 3 via channels 23, which run essentially radially in the guide body 18, so that combustion air can enter the interior not only via the channels 19 and the openings 14, but also for the channels 23, the annular space 21 and the annular gap 22. Since this combustion air occurs in the immediate vicinity of the fuel entering the interior, a particularly effective mixing can take place here, the introduction of turbulence into the interior by the combustion air being largely avoided. This measure also serves to reduce noise.
  • the mixing tube 8 is extended and has jacket openings 20.
  • the part 24 of the mixing tube located upstream of the jacket opening 20 has a larger diameter than the part 25 located downstream of the jacket opening 20.
  • the diameter of the part 24 is considerably larger than the diameter of the circle on which the openings 14 lie.
  • the axes of the openings 14 run parallel to the longitudinal axis of the mixing tube 8.
  • these openings in the diaphragm in such a way that their longitudinal axes are convergingly inclined in the flow direction with respect to the longitudinal axis of the mixing tube, for example with an inclination angle between 3 ° and 6 °.
  • This inclination can be generated by appropriately incorporating the openings into the orifice or by deforming the orifice in the region of the openings 14. It has been found that this slight inclination of the longitudinal axis of the opening and thus of the direction of flow inclined in the direction of the longitudinal axis of the mixing tube Incoming combustion air while improving the mixing results in an additional reduction in noise.
  • the combustion air can be introduced into the mixing chamber largely without turbulence, so that this results in a considerable reduction tion of noise can be achieved.
  • the overall sound level can be reduced, for example, by 8 to 10 dB (A) of the absolute value if you compare the noise level with that of a burner in which the combustion air enters the mixing room directly through the openings in the panel without suitable protective measures.
  • the exemplary embodiment in FIG. 8 is constructed in the region of the prechamber and the air inlet ducts like the exemplary embodiment in FIG. 3, so that reference is made to this exemplary embodiment.
  • the burner differs from the exemplary embodiment in FIG. 5, to the explanatory description of which reference is made only in that the circumferential slots 9 are at a distance from the orifice 2, so that a between the orifice 2 and the circumferential slots 9 Pipe piece 30 is formed with a closed outer surface.
  • This pipe section 30 has a length which corresponds to approximately 1/4 of the mixing pipe diameter. It has been found that this has an effect on the formation of vortices in the mixing tube which reduces the overall sound level.
  • the burner in the region of the prechamber is designed in the same way as in the exemplary embodiment in FIG. 8.
  • the structure differs from the exemplary embodiment in FIG. 7 only in that the inner diameter of the upstream part 24 of the mixing tube 8 the diameter of the circumference corresponds to the circle, which surrounds the openings 14 on the outside.
  • the inside diameter of the downstream part 25 is correspondingly smaller. This version also helps to reduce the overall sound level.
  • FIG. 10 largely corresponds to that of FIG. 8. It differs from this only in that the mixing tube 8 is followed by a further, coaxially arranged pipe section 40 which is at a distance from the end of the mixing tube which is between 1/10 and 1 / 4 of the mixing tube diameter.
  • the length of the pipe section 40 is between 1/2 and 1 mixing pipe diameter, preferably 2/3 of this diameter.
  • the inside diameter of the pipe section 40 can be equal to the inside diameter of the mixing pipe 8 at its outlet, but the inside diameter of the pipe section 40 is preferably smaller, as is shown in the exemplary embodiment in FIG. 10.
  • mixing tube can also be combined with one another in another way, for example a mixing tube can have circumferential slots 9 offset downstream and a pipe section 40 attached downstream, the mixing tube can also narrow in the flow direction.
  • the different mixing tube configurations can be combined in any way with the different configurations in the area of the antechamber, which are discussed in the context of this application.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Feeding, Discharge, Calcimining, Fusing, And Gas-Generation Devices (AREA)
  • Nitrogen Condensed Heterocyclic Rings (AREA)
  • Heterocyclic Carbon Compounds Containing A Hetero Ring Having Nitrogen And Oxygen As The Only Ring Hetero Atoms (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Spray-Type Burners (AREA)
  • Treating Waste Gases (AREA)
EP85109292A 1984-08-16 1985-07-24 Brûleur à huile ou à gaz pour la génération de gaz à chaud Expired EP0175875B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109292T ATE34447T1 (de) 1984-08-16 1985-07-24 Oel- oder gasbrenner zur heissgaserzeugung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3430010 1984-08-16
DE19843430010 DE3430010A1 (de) 1984-08-16 1984-08-16 Brenner zur heissgaserzeugung

Publications (2)

Publication Number Publication Date
EP0175875A1 true EP0175875A1 (fr) 1986-04-02
EP0175875B1 EP0175875B1 (fr) 1988-05-18

Family

ID=6243088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109292A Expired EP0175875B1 (fr) 1984-08-16 1985-07-24 Brûleur à huile ou à gaz pour la génération de gaz à chaud

Country Status (9)

Country Link
US (1) US4629414A (fr)
EP (1) EP0175875B1 (fr)
JP (1) JPS61125511A (fr)
AT (1) ATE34447T1 (fr)
CA (1) CA1259557A (fr)
DE (2) DE3430010A1 (fr)
DK (1) DK160642C (fr)
FI (1) FI86106C (fr)
NO (1) NO160314C (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1988008503A1 (fr) * 1987-04-30 1988-11-03 May Michael G Procede et agencement de combustion de combustible
WO1993019326A1 (fr) * 1992-03-21 1993-09-30 Deutsche Forschungsanstalt Für Luft- Und Raumfahr T E.V. Bruleur exempt de depots

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4673350A (en) * 1986-08-26 1987-06-16 Eclipse, Inc. Burner assembly for radiant tube heating system
US4705022A (en) * 1986-09-25 1987-11-10 Eclipse, Inc. Recuperative radiant tube heating system
DE3801681C1 (en) * 1988-01-21 1989-05-18 Deutsche Forschungs- Und Versuchsanstalt Fuer Luft- Und Raumfahrt Ev, 5300 Bonn, De Method for burning gaseous or liquid fuel and burner for carrying out this method
DE3801679C1 (en) * 1988-01-21 1989-05-11 Deutsche Forschungs- Und Versuchsanstalt Fuer Luft- Und Raumfahrt Ev, 5300 Bonn, De Burner for gaseous or liquid fuel
DE4201060C2 (de) * 1992-01-17 1994-07-14 Man B & W Diesel Ag Brenner für vergasten flüssigen Brennstoff
DE4201059C2 (de) * 1992-01-17 1994-06-09 Man B & W Diesel Ag Flammrohr für einen Brenner für vergasten flüssigen Brennstoff
DE4201061C2 (de) * 1992-01-17 1994-06-23 Man B & W Diesel Ag Brenner für vergasten flüssigen Brennstoff
ES2094512T3 (es) * 1992-02-28 1997-01-16 Fuellemann Patent Ag Quemador, en especial quemador de gasoleo o quemador combinado de gasoleo/gas.
US5393224A (en) * 1993-12-02 1995-02-28 American Standard Inc. Ignitor assembly for power burner furnace
US5927963A (en) * 1997-07-15 1999-07-27 Gas Electronics, Inc. Pilot assembly and control system
DE10004475C2 (de) * 2000-02-02 2002-08-22 Bosch Gmbh Robert Drallbrenner mit einem Drallkörper als Brennerelement in einer Brennkammer
EP1279895A1 (fr) * 2001-07-25 2003-01-29 Compagnie Europeenne de Bruleurs Tête de combustion d'un brûleur comprenant une zone de pré-vaporisation du combustible liquide
US6743010B2 (en) 2002-02-19 2004-06-01 Gas Electronics, Inc. Relighter control system
US20050255416A1 (en) * 2002-07-19 2005-11-17 Frank Haase Use of a blue flame burner
AU2003250146A1 (en) * 2002-07-19 2004-02-09 Shell Internationale Research Maatschappij B.V. Use of a yellow flame burner
DE502006005173D1 (de) * 2006-02-22 2009-12-03 Tempratec Ltd Vorrichtung und Verfahren zum Verbrennen eines Brennstoffes
JP4739275B2 (ja) * 2006-08-11 2011-08-03 Ｊｘ日鉱日石エネルギー株式会社 バーナ
DE102016113222A1 (de) * 2016-07-18 2018-01-18 Webasto SE Brenner und Fahrzeugheizgerät

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2712564A1 (de) * 1977-03-22 1978-10-05 Weishaupt Max Gmbh Brenner fuer fluessige brennstoffe
DE3109988A1 (de) * 1981-03-14 1982-12-02 Klaus 2000 Hamburg Eckloff Vergaser-oelbrenner
EP0115858A1 (fr) * 1983-02-08 1984-08-15 M.A.N. MASCHINENFABRIK AUGSBURG-NÜRNBERG Aktiengesellschaft Brûleur à monter dans les installations de chauffage et de production de vapeur

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2857961A (en) * 1954-07-13 1958-10-28 Brown Fintube Co Oil burners
DE1401849B2 (de) * 1960-08-01 1972-02-24 Webasto-Werk GmbH, 8031 Stockdorf Brenner fuer industrieoefen
US3609073A (en) * 1968-02-26 1971-09-28 Dickinson S Ltd Oil burner apparatus
US3545902A (en) * 1968-09-23 1970-12-08 Frank W Bailey Blue-flame gun burner process and apparatus for liquid hydrocarbon fuel
DE2545234C2 (de) * 1975-10-09 1983-09-15 Fa. J. Eberspächer, 7300 Esslingen Mischeinrichtung für Brenner
DE2700671C2 (de) * 1977-01-08 1988-07-28 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Blaubrennender Ölbrenner
US4364725A (en) * 1977-01-08 1982-12-21 Deutsche Forschungs- Und Versuchsanstalt Fur Luft- Und Raumfahrt E.V. Blue-flame oil burner
DE2821932A1 (de) * 1978-05-19 1979-11-22 Karl Bodemer Mischeinrichtung zur verbrennung von fluessigen kohlenwasserstoffen, insbesondere heizoel und dieseloel
DE2918416C2 (de) * 1979-05-08 1985-05-15 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Vergasungsölbrenner
DE3035707A1 (de) * 1980-09-22 1982-04-08 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Oel- und gasbrenner zum einbau in heizungs- und dampferzeugungskessel
JPS58200911A (ja) * 1982-05-17 1983-11-22 Inax Corp 液体燃料の燃焼装置
JPS6367086A (ja) * 1986-09-08 1988-03-25 Matsushita Electric Ind Co Ltd 映像信号処理装置

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2712564A1 (de) * 1977-03-22 1978-10-05 Weishaupt Max Gmbh Brenner fuer fluessige brennstoffe
DE3109988A1 (de) * 1981-03-14 1982-12-02 Klaus 2000 Hamburg Eckloff Vergaser-oelbrenner
EP0115858A1 (fr) * 1983-02-08 1984-08-15 M.A.N. MASCHINENFABRIK AUGSBURG-NÜRNBERG Aktiengesellschaft Brûleur à monter dans les installations de chauffage et de production de vapeur

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1988008503A1 (fr) * 1987-04-30 1988-11-03 May Michael G Procede et agencement de combustion de combustible
WO1993019326A1 (fr) * 1992-03-21 1993-09-30 Deutsche Forschungsanstalt Für Luft- Und Raumfahr T E.V. Bruleur exempt de depots
US5433601A (en) * 1992-03-21 1995-07-18 Deutsche Forschungsanstalt Fuer Luft- Und Raumfahrt E.V. Deposit-free burner

Also Published As

Publication number Publication date
EP0175875B1 (fr) 1988-05-18
DK370785D0 (da) 1985-08-15
FI86106C (fi) 1992-07-10
CA1259557A (fr) 1989-09-19
NO853217L (no) 1986-02-17
DE3562819D1 (en) 1988-06-23
FI853128L (fi) 1986-02-17
JPH0240924B2 (fr) 1990-09-13
DE3430010A1 (de) 1986-02-27
DK160642B (da) 1991-04-02
DK370785A (da) 1986-02-17
DK160642C (da) 1991-09-02
DE3430010C2 (fr) 1987-11-12
NO160314B (no) 1988-12-27
ATE34447T1 (de) 1988-06-15
FI86106B (fi) 1992-03-31
FI853128A0 (fi) 1985-08-15
NO160314C (no) 1989-04-05
US4629414A (en) 1986-12-16
JPS61125511A (ja) 1986-06-13

Similar Documents

Publication Publication Date Title
EP0175875B1 (fr) Brûleur à huile ou à gaz pour la génération de gaz à chaud
EP0438682B1 (fr) Système d'échappement avec filtre à particules et brûleur de régénération
DE2143012C3 (de) Brenneranordnung bei einer Gasturbinen-Brennkammer
DE2131490C2 (de) Brenner-Mischdüse
DE3217674C2 (de) Brennkammer für eine Gasturbine
DE3842842A1 (de) Atmosphaerischer brenner
WO2006042796A2 (fr) Bruleur pour turbine a gaz
DE3321697A1 (de) Sauerstoff-schneidbrenner
DE3244854A1 (de) Brenner
DE1932881A1 (de) Brennkammer
DE2511500C2 (de) Brenner zur Verbrennung von flüssigem Brennstoff
DE4323300C2 (de) Mischvorrichtung für einen Brenner
DE2345838A1 (de) Brenner
DE69818909T2 (de) Brennerkopf für Gasbrenner
EP0428174B1 (fr) Dispositif de mélange avec flamme tourbillonnante pour brûleur à huile
DE4244400A1 (de) Brenner zur Heißgaserzeugung
DE1960754C2 (de) Brenner für gasförmige Brennstoffe
EP0864812A2 (fr) Dispositif de mélange pour brûleur à gaz et à huile
DE3801681C1 (en) Method for burning gaseous or liquid fuel and burner for carrying out this method
DE3005042C2 (de) Brenner für flüssigen Brennstoff mit einer Wirbelkammer
DE3801679C1 (en) Burner for gaseous or liquid fuel
DE2528813C3 (de) Brenner für flüssige Brennstoffe mit einem Gemischverteilerkörper
DE970002C (de) Brenner fuer Heizgeraete
DE3147564A1 (de) Doppelmuendungsbrennstoffduese
DE2319494A1 (de) Brennkammer fuer fluessige oder gasfoermige brennstoffe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19860319

17Q First examination report despatched

Effective date: 19861215

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

ITF It: translation for a ep patent filed
REF Corresponds to:

Ref document number: 34447

Country of ref document: AT

Date of ref document: 19880615

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3562819

Country of ref document: DE

Date of ref document: 19880623

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
EPTA Lu: last paid annual fee
EAL Se: european patent in force in sweden

Ref document number: 85109292.4

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20040628

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20040713

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20040720

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 20040722

Year of fee payment: 20

Ref country code: AT

Payment date: 20040722

Year of fee payment: 20

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20040723

Year of fee payment: 20

Ref country code: LU

Payment date: 20040723

Year of fee payment: 20

Ref country code: CH

Payment date: 20040723

Year of fee payment: 20

Ref country code: BE

Payment date: 20040723

Year of fee payment: 20

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20050723

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20050724

BE20 Be: patent expired

Owner name: *DEUTSCHE FORSCHUNGS- UND VERSUCHSANSTALT FUR LUFT

Effective date: 20050724

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

EUG Se: european patent has lapsed
NLV7 Nl: ceased due to reaching the maximum lifetime of a patent

Effective date: 20050724

BE20 Be: patent expired

Owner name: *DEUTSCHE FORSCHUNGS- UND VERSUCHSANSTALT FUR LUFT

Effective date: 20050724