EP0018602B1 - Vergasungsölbrenner - Google Patents

Vergasungsölbrenner Download PDF

Info

Publication number
EP0018602B1
EP0018602B1 EP80102222A EP80102222A EP0018602B1 EP 0018602 B1 EP0018602 B1 EP 0018602B1 EP 80102222 A EP80102222 A EP 80102222A EP 80102222 A EP80102222 A EP 80102222A EP 0018602 B1 EP0018602 B1 EP 0018602B1
Authority
EP
European Patent Office
Prior art keywords
mixing tube
tube
diameter
orifice plate
orifice
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
Application number
EP80102222A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0018602A3 (en
EP0018602A2 (de
Inventor
Winfried Prof.-Dr.-Ing. Buschulte
Friedhelm Dageförde
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
Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
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 Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR filed Critical Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
Priority to AT80102222T priority Critical patent/ATE3462T1/de
Publication of EP0018602A2 publication Critical patent/EP0018602A2/de
Publication of EP0018602A3 publication Critical patent/EP0018602A3/de
Application granted granted Critical
Publication of EP0018602B1 publication Critical patent/EP0018602B1/de
Expired legal-status Critical Current

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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, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F23D11/402—Mixing chambers downstream of the nozzle

Definitions

  • the invention relates to a gasification oil burner according to the preamble of claim 1.
  • Gasification oil burners of this type (DE-A-2 700 671, FR-A-2 377 002) have the advantage that soot-free stoichiometric combustion can be achieved with them and that the combustion takes place in the flame tube belonging to the burner and is therefore largely independent of the shape and dimensions of the combustion chamber of the boiler. Practice has shown that such burners tend to emit more or less noise, which can be perceived as a nuisance, particularly in domestic heating systems.
  • a gasification oil burner with soot-free stoichiometric combustion with a burner housing serving for the supply of combustion air with an oil atomizing nozzle arranged coaxially therein and an evaporator tube extending coaxially therewith, which extends freely into the combustion chamber of the boiler.
  • the circumference of the evaporator tube is provided with through-holes through which hot fuel gases are to be drawn into the evaporator tube from the outside of the combustion chamber of the boiler.
  • a baffle plate with holes is arranged at a distance from this end via webs, on which the oil-air mixture emerging from the evaporator tube burns out with a flame in the combustion chamber of the boiler.
  • the evaporator tube is to be selected depending on the combustion chamber of the boiler and this accordingly.
  • Such a burner is said to be characterized by low-noise operation (DE-A-2 712 856).
  • the object of the invention is to design oil burners of the generic type such that a substantial reduction in noise emissions is achieved.
  • mixing tube is perforated at least over an area adjacent to the downstream end.
  • Another possibility to reduce the noise emission is to divide the aperture passage into a central opening and a plurality of further air passage openings, which are arranged around the central opening within an area circumscribed by the projection of the clear cross section of the mixing tube.
  • the joint use leads to a cumulative effect and a greater reduction in noise emissions than either of the two measures alone.
  • the burner 2 shown has a chamber 4 in which a pressure atomizing nozzle 6 is mounted in the usual way on a nozzle assembly 8.
  • the oil is conveyed by an oil pump 10, which is driven by an electric motor 12, which at the same time drives a fan rotor 14 in a conventional manner.
  • the pump 10 conveys the oil into the nozzle assembly 8 carrying the atomizing nozzle 6 via an adjustable throttle valve 16 and an electromagnetically operated shut-off valve 18.
  • the fan 14 conveys the combustion air via an air duct 20 into the housing 4, specifically via a throttle valve 22 with an air flap 24, which is adjustable via a motor 26.
  • a pair of ignition electrodes 30, which is connected to an ignition transformer 32, is held with a holder 28 arranged on the nozzle assembly 8.
  • a wall 34 is provided with a diaphragm passage 36.
  • the aperture 36 is coaxial with the axis of the nozzle.
  • a mixing tube 38 is arranged downstream of the orifice passage 36 and is fastened to the orifice wall 34 via retaining webs 40.
  • the mixing tube 38 lies coaxially in a flame tube 42, the upstream end of which is sealingly connected to the diaphragm wall 34.
  • the upstream end 41 of the mixing tube 38 lies at a distance L 4 from the orifice wall 34.
  • a radial passage 35 is formed between the upstream mixing tube end 41 and the orifice wall 34, through which combustion gases can recirculate from the flame space located downstream of the mixing tube.
  • the diameter D 2 of the flame tube essentially corresponds to 2 to 2.5 times the diameter D, of the mixing tube 38.
  • the length L 2 of the flame tube corresponds to at least 2.5 times the diameter D 2 of the flame tube. This length is necessary so that the flame that forms downstream of the mixing tube is safely against the inner flame tube wall and in this way the flame tube is securely closed at its open end by the flame front. This is the prerequisite back for a safe recirculation of part of the gas over the outer circumference of the mixing tube.
  • the recirculation is further achieved in that the air flowing in through the orifice passage 36 generates a negative pressure via the radial passage 35, through which recirculation gas is sucked in.
  • the jet cross section of the combustion air flowing through the orifice passage is smaller than the diameter D of the mixing tube 38.
  • This condition is met if the diameter D 3 of the orifice passage is equal to or less than the diameter D, of the mixing tube.
  • the diaphragm constricts the air flow behind the diaphragm passage, so that even with approximately the same diameters of the diaphragm passage and mixing tube it is ensured that the cross section of the air jet in the area of the radial passage 35 remains smaller than the mixing tube diameter D,.
  • the burner described is further provided with an ionization probe 44 which protrudes into the flame tube up to the flame area and which is connected in the usual way to a control device 46, via which the oil supply by closing the valve 18 and switching off the engine 12 when the flame is extinguished is interrupted.
  • the mixing tube 38 is perforated in an area 37 adjoining the downstream end 39.
  • This perforated area extends over most of the length L :, of the mixing tube.
  • Only a limited section with a length L o which is less than two thirds of the mixing tube diameter D ", is of full-wall design.
  • the proportion of the perforated area should be selected so that gas vibrations which are effective transversely to the axis can relax through the tube wall, but the tube essentially acts as a closed wall for the jet which propagates in the axial direction. This can be achieved with a percentage of holes in the perforated area between 20 and 50%.
  • the proportion of perforated area is additionally limited by the fact that the pipe must maintain a certain radiation area in order to ensure the desired gasification of the oil before it enters the flame zone.
  • the mixing tube 138 is guided up to the orifice wall 34 at its upstream end.
  • the tube is perforated along the length L 4 at the front wall, the holes forming the radial passage through which the recirculation gases are drawn in.
  • the mixing tube 138 is cylindrical over its entire length.
  • the upstream end 139 of the mixing tube 138 is flared toward the orifice wall 34 with a cone angle, which is chosen here at 90 °. The end of the mixing tube thus diverges in the direction of the orifice wall 34.
  • the hole cross section in the region of the radial passage, adjacent to the orifice wall 34, is selected such that a sufficient amount of hot gas is recirculated.
  • the flame tube 42 in the region of the downstream end 39 of the mixing tube, is provided with a plurality of holes and openings 43. These holes also contribute to reduced noise generation. With a flame tube diameter of 75 mm, 6 to 8 holes are expediently distributed over the circumference with a hole diameter of 8-10 mm.
  • Noise reduction can also be achieved by dividing the aperture passage 36 into a plurality of passage openings. Such a subdivision leads to an enlargement of the surface of the air jet passing through the aperture and thus to a more favorable vibration behavior of the combustion air.
  • FIG. 3 One embodiment is shown in FIG. 3.
  • the aperture passage here has a central opening 136 through which the nozzle conveys the oil.
  • a plurality of further air passage openings 137 are arranged around the central opening 136, specifically in such a way that they are within a projection of the clear cross section of the mixing tube 38 .mu.m written area.
  • the further air passage openings 137 are shown on the right with a circular cross section, the center points lying on a common circle.
  • the further air passage openings 137 are formed with a cross section stretched in the radial direction.
  • This cross section can have a teardrop shape, for example, or an approximately trapezoidal shape.
  • Such a cross-sectional shape enables a higher total passage cross-section to be achieved on the limited area or a more favorable arrangement of a predetermined cross-section.
  • the further through openings 137 located on the outside are again designed with a circular cross section, the openings with their centers being arranged alternately on two circles with different diameters.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Spray-Type Burners (AREA)
  • Feeding And Controlling Fuel (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Consolidation Of Soil By Introduction Of Solidifying Substances Into Soil (AREA)
  • Earth Drilling (AREA)
  • Wick-Type Burners And Burners With Porous Materials (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Nonmetallic Welding Materials (AREA)
  • Organic Insulating Materials (AREA)
  • Protection Of Pipes Against Damage, Friction, And Corrosion (AREA)
EP80102222A 1979-05-08 1980-04-25 Vergasungsölbrenner Expired EP0018602B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80102222T ATE3462T1 (de) 1979-05-08 1980-04-25 Vergasungsoelbrenner.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2918416A DE2918416C2 (de) 1979-05-08 1979-05-08 Vergasungsölbrenner
DE2918416 1979-05-08

Publications (3)

Publication Number Publication Date
EP0018602A2 EP0018602A2 (de) 1980-11-12
EP0018602A3 EP0018602A3 (en) 1981-01-14
EP0018602B1 true EP0018602B1 (de) 1983-05-18

Family

ID=6070161

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80102222A Expired EP0018602B1 (de) 1979-05-08 1980-04-25 Vergasungsölbrenner

Country Status (15)

Country Link
US (1) US4318688A (xx)
EP (1) EP0018602B1 (xx)
JP (1) JPS55150412A (xx)
AT (1) ATE3462T1 (xx)
AU (1) AU526030B2 (xx)
CA (1) CA1147252A (xx)
DD (1) DD150642A5 (xx)
DE (1) DE2918416C2 (xx)
DK (1) DK156919C (xx)
ES (1) ES8101244A1 (xx)
FI (1) FI66979C (xx)
GR (1) GR68000B (xx)
IE (1) IE49595B1 (xx)
NO (1) NO156185C (xx)
YU (1) YU41711B (xx)

Families Citing this family (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE3048044C2 (de) 1980-12-19 1983-06-09 Helmut Dipl.-Chem. 8000 München Ulrich Flammrohr aus hitzebeständigem Werkstoff für Brenner, insbesondere Ölbrenner
DE3132948C2 (de) * 1981-08-20 1984-07-19 Kraft Hausherr GmbH & Co KG, 4322 Sprockhövel Brenneraustrittskopf für einen Brenner für flüssige Brennstoffe
DE3241731C2 (de) * 1982-11-11 1986-04-03 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn Vergasungsölbrenner
DE3241730A1 (de) * 1982-11-11 1984-05-17 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn Vergasungsoelbrenner mit einer oelzerstaeubungsvorrichtung
DE3304214A1 (de) * 1983-02-08 1984-04-26 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg Brenner zum einbau in heizungs- und dampferzeugungs anlagen
JPS59158907A (ja) * 1983-02-28 1984-09-08 Inax Corp 燃焼装置
JPS59164810A (ja) * 1983-03-07 1984-09-18 Inax Corp 燃焼装置
US4536152A (en) * 1983-04-04 1985-08-20 Asarco Incorporated High-velocity gas burners
DE3430010A1 (de) * 1984-08-16 1986-02-27 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn Brenner zur heissgaserzeugung
DE3614440A1 (de) * 1986-04-29 1987-11-05 Schneidawind Melitta Heizungsgeraet mit nachbrenner
DE3738623C2 (de) * 1987-11-11 1995-05-04 Wolf Klimatechnik Gmbh Heizkessel mit Rauchgasrezirkulation
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
DE3906854C1 (en) * 1989-03-03 1990-10-31 Buderus Heiztechnik Gmbh, 6330 Wetzlar, De Burner tube for a blue-burning oil burner
DE3919797A1 (de) * 1989-06-16 1991-01-03 Bernhard W Braukmann Oelbrenner
DE3928214A1 (de) * 1989-08-25 1990-03-08 Zimmermann Hans Georg Dipl Ing Brenner mit brenngas-rueckfuehrung fuer fliessfaehige brennstoffe
DE3942747A1 (de) * 1989-12-22 1991-06-27 Eberspaecher J Fahrzeug-heizgeraet, insbesondere kraftfahrzeug-zusatzheizgeraet
DE4021315C1 (en) * 1990-07-04 1992-01-02 Buderus Heiztechnik Gmbh Oil burner with blue frame - incorporates baffle ring on inside of tube outlet
DE4118864C2 (de) * 1991-06-07 1995-10-12 Bta Beheizungstechnik Ag Verfahren zum Verbrennen eines gasförmigen oder flüssigen Brennstoffs und Brenner zur Durchführung des Verfahrens
WO1994025798A1 (en) * 1993-04-30 1994-11-10 Jin Min Choi Device for whirling diffusion of combustion air for turbo burner
DE4412185B4 (de) * 1994-04-08 2005-05-12 Körting Hannover AG Brenner für flüssige oder gasförmige Brennstoffe, insbesondere für Öl
DE19534319C2 (de) * 1995-09-15 1997-12-18 Ceramtec Ag Einsatz für eine Kesselanlage, Kesselanlage und Verfahren zum Betreiben der Kesselanlage
ATE237101T1 (de) * 1998-01-23 2003-04-15 Alstom Switzerland Ltd Brenner für den betrieb eines wärmeerzeugers
US5906485A (en) * 1998-02-27 1999-05-25 Reading Pretzel Machinery Corporation Tunnel-type conveyor oven having two types of heat sources
FR2800844B1 (fr) * 1999-11-08 2002-04-19 Muller Et Cie Dispositif pour ameliorer la combustion d'un bruleur a fioul a air pulse
CH694972A5 (de) * 2004-10-22 2005-10-14 Toby Ag Vormischender Brenner mit einem zylindrischen Flammenhalter sowie Heizkessel mit einem solchen Brenner.
IT1399921B1 (it) * 2010-05-05 2013-05-09 Worgas Bruciatori Srl Bruciatore premiscelato
CN103836622B (zh) * 2014-04-02 2016-03-30 陆奇志 一种液体本生灯
US10711998B2 (en) 2017-10-03 2020-07-14 Lennox Industries Inc. Fresh air intake for low NOx emission furnace
US11187433B2 (en) 2017-10-03 2021-11-30 Lennox Industries Inc. Pre-mix burner assembly for low NOx emission furnace
US10711997B2 (en) 2017-10-03 2020-07-14 Lennox Industries Inc. Burner box liner for low NOx emission furnace
US11353211B2 (en) * 2018-04-09 2022-06-07 Gas Technology Institute High turndown ratio gaseous fuel burner nozzle and control
US11162677B2 (en) * 2019-01-18 2021-11-02 Lennox Industries Inc. Air intake coupling with noise suppression for low NOx emission furnace

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Publication number Priority date Publication date Assignee Title
US2857961A (en) * 1954-07-13 1958-10-28 Brown Fintube Co Oil burners
DE1401127A1 (de) * 1958-08-16 1968-12-12 Willi Broedlin Verfahren und Vorrichtung zum Blaubrand-Betrieb von Zerstaeubungsoelbrennern
US3269448A (en) * 1965-12-02 1966-08-30 Fabricacion De Maquinas Automatic liquid fuel burner control
US3510238A (en) * 1968-04-19 1970-05-05 Gulf Research Development Co Tubular uniform temperature heat source
US3589848A (en) * 1968-08-06 1971-06-29 Liberty Combustion Corp Oil burner control system
US3545902A (en) * 1968-09-23 1970-12-08 Frank W Bailey Blue-flame gun burner process and apparatus for liquid hydrocarbon fuel
BE757232A (fr) * 1969-10-08 1971-04-08 Int Industries Ltd Bruleurs
DE2129346A1 (de) * 1971-06-14 1972-12-21 Schlosser H Einrichtung an Druckzerstauberol und Gasgeblasebrenner zur Fuhrung der Verbrennungsluft in feuerungstechnischen Geraten
JPS52122934A (en) * 1976-04-08 1977-10-15 Tomoe Shokai Kk Burner
DE2700671C2 (de) * 1977-01-08 1988-07-28 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Blaubrennender Ölbrenner
DE2712856A1 (de) * 1977-03-21 1978-09-28 Cary Dipl Ing Brandt Oelbrenneranordnung fuer heizungsanlagen
DE2715456A1 (de) * 1977-04-06 1978-10-12 Karl Bodemer Mischkopf fuer brenner kleiner heizleistungen
DE2751524C2 (de) * 1977-11-18 1986-08-21 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Blaubrennender Ölbrenner
DE2839280A1 (de) * 1978-09-09 1980-03-20 Bosch Gmbh Robert Oelvergasungsbrenner

Also Published As

Publication number Publication date
ATE3462T1 (de) 1983-06-15
AU5786080A (en) 1980-11-13
JPS6152364B2 (xx) 1986-11-13
DK156919B (da) 1989-10-16
IE800946L (en) 1980-11-08
US4318688A (en) 1982-03-09
DK156919C (da) 1990-03-12
NO801347L (no) 1980-11-10
EP0018602A3 (en) 1981-01-14
YU41711B (en) 1987-12-31
ES491252A0 (es) 1980-12-01
EP0018602A2 (de) 1980-11-12
AU526030B2 (en) 1982-12-16
DK181780A (da) 1980-11-09
FI801401A (fi) 1980-11-09
FI66979B (fi) 1984-08-31
ES8101244A1 (es) 1980-12-01
JPS55150412A (en) 1980-11-22
GR68000B (xx) 1981-10-26
DE2918416A1 (de) 1980-11-13
NO156185C (no) 1987-08-05
DD150642A5 (de) 1981-09-09
CA1147252A (en) 1983-05-31
FI66979C (fi) 1984-12-10
IE49595B1 (en) 1985-10-30
NO156185B (no) 1987-04-27
DE2918416C2 (de) 1985-05-15
YU119880A (en) 1983-04-30

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