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WO1999060306A1 - Bruleur de premelange pour combustibles liquides - Google Patents

Bruleur de premelange pour combustibles liquides Download PDF

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Publication number
WO1999060306A1
WO1999060306A1 PCT/DE1999/001420 DE9901420W WO9960306A1 WO 1999060306 A1 WO1999060306 A1 WO 1999060306A1 DE 9901420 W DE9901420 W DE 9901420W WO 9960306 A1 WO9960306 A1 WO 9960306A1
Authority
WO
WIPO (PCT)
Prior art keywords
flame
oil
burner
evaporator
premix burner
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.)
Ceased
Application number
PCT/DE1999/001420
Other languages
German (de)
English (en)
Inventor
Walter Swoboda
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of WO1999060306A1 publication Critical patent/WO1999060306A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F23D11/005—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space with combinations of different spraying or vaporising means
    • F23D11/008—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space with combinations of different spraying or vaporising means combination of means covered by sub-groups F23D5/00 and F23D11/00
    • 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
    • F23D11/402—Mixing chambers downstream of the nozzle
    • 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
    • F23D11/44—Preheating devices; Vaporising devices

Definitions

  • premix burner The principle of the premix burner has long been known for gas. However, premix burners for heating oil are not yet on the market. Burners for gaseous and liquid fuels differ fundamentally in the configuration. Liquid fuels must first be evaporated before they can be mixed with the combustion air and burned.
  • the standard oil burner as it has been used for heating buildings for many years, is the so-called pressure atomizer.
  • the fuel is atomized by means of a nozzle, and the combustion air is mixed into the spray mist via a turbulator. After ignition, a diffusion flame is created, in which the areas of mixing, vaporization and combustion merge. Although very small droplets are formed when the heating oil is atomized, a certain amount of time is required for the evaporation of these droplets.
  • the mixture in this flame is extremely inhomogeneous and the pollutant formation correspondingly high. Since the fuel is processed and mixed with the combustion air in the flame itself, the flame volume is correspondingly large. This inhomogeneity is also the reason why a diffusion flame is very sensitive if the firebox is too cold; in this case soot is formed.
  • gasification burner Another path is taken with the so-called gasification burner.
  • the fuel is evaporated relatively quickly downstream of the nozzle by recirculating exhaust gases.
  • a compact, gaseous flame is created. But even in this case it is not a real premix burner, because partial combustion also takes place here, even before the fuel has completely evaporated.
  • Such a flame is much less sensitive to cold heating surfaces.
  • gasification burners produce a very noisy flame. When it comes to ignition, each blue-burning gasification burner is initially a yellow burner, since gasification can only start when the exhaust gases are available for recirculation. During this time, the exhaust emissions are also stronger.
  • the overlapping preparation steps also make it difficult to achieve functional changes in only one area. Every constructive change always affects all areas.
  • the normal pressure atomizer also has the disadvantage that the minimum powers of less than 10 kW required today cannot be achieved, since the dimensions of the nozzles used cannot be reduced further; the risk of constipation would be too great.
  • Other principles have also been tried to develop low-power burners. So the old compressed air atomizer was brought back to life, but it could not prevail on the market any more than an evaporation burner with a rotating evaporation beaker, which is described in patent applications DE-OS 2649669 and in EP 0283435.
  • a burner which is described in EP-0405481 and which is actually a combination of evaporative burner and, also works in a similar manner Represents compressed air atomizer.
  • the mixture is at least partially generated outside of the body from sintered metal, so that the principle of the premix burner has not been implemented here.
  • D-AS 1 265906 The construction described in D-AS 1 265906 comes closest to a functional premix burner. But even here the problems were not recognized, the solution of which is the prerequisite for a reliable device.
  • Prechambers are also known from diesel engines, but they have not realized the premixing principle, just as a proposal for such a construction for a two-stroke engine in DE-OS 4305468.
  • the heating oil sublimes immediately. There is no liquid film on the surface at all, the heating oil is immediately converted into the vapor state. It must be avoided in any case that drops form, because above a temperature of approx. 360 ° C the Leidenfrost phenomenon occurs with heating oil; the drop surrounded by an insulating layer of vapor literally dances on the hot surface and it takes a long time for the drop to evaporate. During this time, cracking processes take place within the drop, which cause oil coke to form on the evaporator surface.
  • the premix burner according to the invention with the characterizing features of the main claim has the advantage over the prior art that even with insufficient atomization by the thermal treatment, a hot fuel vapor-air mixture is formed, which can be burned like a gas according to the premixing principle. Since the evaporator is preheated for this purpose at the start, the ignition is also easier. With a hot fuel vapor-air mixture, the ignition also generates far fewer pollutants than is the case with a cold mixture.
  • the flame of the premix burner has the lowest volume in relation to all other mixing principles. For this reason, less nitrogen oxides can form because the combustion products stay in the hot area for a shorter time. In addition, there are no mixing processes in the flame, because the mixture is homogeneous during combustion; In this way, so-called hot nests are avoided, which are also responsible for the formation of pollutants.
  • the low flame volume also enables the combustion chambers of the heaters to be designed with a smaller volume that can. In this way, the dimensions of the heat exchangers are also reduced and they are lighter in weight.
  • the principle of the premix burner also includes other options. So z. B. the shape of the flame can be chosen freely. It is only the configuration of the burner head that determines whether a flame should have a cylindrical shape or whether the combustion should take place over a larger area. In this way, the energy density of the flame can also be selected, which has an effect on the residence time of the combustion products in the hot area and thus reduces the formation of nitrogen oxides.
  • infrared emitters can also be implemented. In this case, in particular, a suitable coating is appropriate so that a catalyst is integrated in the burner at the same time.
  • the atomizer nozzle 1 is arranged coaxially in the burner tube 2, which is closed off by the turbulator 3. Downstream of the turbulator is the mixing chamber 4 of the oil evaporator 5, which in this case consists of a tube.
  • the oil evaporator 5 is closed off from the perforated base 6 with the bores 7.
  • the perforated plate 6 is delimited upstream by the pipe socket 8.
  • the perforated base 6 widens radially over the pipe socket 8 into the pipe section 9, in which the tubular heating element 10 is cast.
  • Mantelrofir 11 establishes the connection to the fan housing, not shown.
  • the tip of the thermal sensor 13 is seated in the pipe socket 8.
  • the pipe section 9 forms the combustion chamber 12 in which the flame turbulator 14 is located.
  • the tubular heater 10 is switched on. As soon as the thermal sensor 13 has reached a temperature of approx. 300 ° C., the command is given to the control device, not shown here, which gives voltage to the ignition electrodes 16. Fuel is injected into the mixing sprayed chamber 4 and admixed air via the turbulator. The arrows in the burner tube 2 show the direction of the air flow from the fan (not shown here). The fuel is evaporated on the hot perforated plate 6 and a fuel-vapor / air mixture enters the flame turbulator 14 downstream from the holes 7 in the perforated plate 6 Combustion chamber 12 forms a stabilizing vortex. At this point, the mixture is ignited by the ignition electrodes 16.
  • the electrical preheating is switched off and the perforated base 6 receives the temperature required for evaporation via the heat conduction of the pipe section 9, which is located in the region of the vortex of flame formed on the turbulator.
  • the pipe section 9 and the perforated base 6 must be made of a good heat-conducting material. Aluminum and copper or their alloys are suitable for this.
  • the flame tube 15 is shrunk. Since the flame tube glows downstream at the free end, a sufficient amount of heat is introduced into the tube section 9 and thus into the perforated base 6. The flame tube 15 also prevents the parts made of highly conductive material from cooling the flame too much at this point, as a result of which unnecessary CO would otherwise be generated.
  • the flow path of the mixture through the perforated plate 6, the bores 7 and the flame turbulator 14 is represented by arrows. The flame monitoring is not shown here, it can be carried out in the usual way for blue burners.
  • drawing no. 2 a somewhat different configuration is shown. Similar parts are designated by the same reference numerals as in drawing no. 1.
  • the atomizer nozzle is arranged coaxially in the burner tube 2, which is closed downstream by the orifice 21 with the air nozzle 20. If the cross section of the oil evaporator is small, as in the example shown, an orifice with an air nozzle is also sufficient, since in this case the fuel does not have to be distributed in such a wide jet. Downstream of the air nozzle 20 is the mixing chamber 4 of the oil evaporator 5, which is designed here as a tube. The bores 7 are arranged radially in the tubular jacket of the oil evaporator 5. The tubular heater 10 is shown here as a cylindrical heating cartridge. The thermal sensor 13 is also located in the jacket of the oil evaporator 5.
  • the flame tube 15 is formed at its upstream end as a flange 17, which is connected in a heat-conducting manner to the thicker part 18 of the oil evaporator 5, which is also upstream. If from the holes 7 of the oil evaporator 5 a finished, hot oil vapor-air mixture emerges, it is ignited by the ignition electrodes 16. Since the bottom and part of the oil evaporator 5 lie in the area of the flame represented by arrows, a large part of the heat of vaporization required for the fuel is distributed in the oil evaporator. The flame tube 15 becomes glowing at its downstream end during operation and conducts the heat via the flange 17 to the oil evaporator 5. The burner can be operated in the form shown, but the flame produces some noise. In the drawing 3, the same burner principle is shown with an additional, radial flame turbulator 14, which is pushed onto the downstream part of the oil evaporator 5.
  • This flame turbulator reduces the speed of the mixture emerging from the bores 7 of the oil evaporator and at the same time generates a stabilizing vortex, which also favors heat conduction into the oil evaporator.
  • the drawing 3 shows a radial section through the bores 7 of the oil evaporator 5 and the entire flame tube 15.
  • the nozzle 1 can be seen from the front, the wall of the oil evaporator 5 with the bores 7.
  • the flame turbulator 14 has a shape which is similar to the wheel of a radial fan. The mixture emerges in the space between the blades of the flame turbulator 14 and forms a stabilizing vortex in the annular space 19, which is delimited radially by the flame tube 15.
  • the two ignition electrodes 16 are also visible in the front view.
  • an axially arranged flame turbulator as shown in drawing 1, can also be used, which is pushed downstream of the bores 7 over the oil evaporator 5.
  • the ignition electrodes 16 can be guided through the wings of the axial flame turbulator 14.
  • a glow element made of metal or ceramic can also be arranged, which distributes the mixture emerging from the bores of the oil evaporator (5) over the entire cross section, the outflow rate being reduced so far that the flame can hold onto the surface .
  • An infrared heater is created in this way.
  • the heat for evaporating fuel is both from the Part of the oil evaporator 5 passed upstream, as well as from the flame tube 15, which is connected to the oil evaporator 5 in a heat-conducting manner via the flange 17.
  • the burner with a radial flame can also be operated without the flame tube 15. In this case, additional heat-conducting elements must be attached to the oil evaporator.
  • the oil evaporator 5 is shielded by the insulation 24 in its upstream part.
  • the nozzle 1 is again arranged in the burner tube 2.
  • the oil evaporator 5 is formed by the perforated base 6 with the holes 7, in which the tubular heater 10 is cast.
  • the flame turbulator 14 is located downstream.
  • the bolt 22 projects centrally into the flame and conducts heat into the perforated base 6.
  • several small bolts can also be distributed over the flame turbulator.
  • This version has the lowest thermal inertia, since only a small amount of material has to be heated to start the burner. After ignition, the bolt 22 ensures that sufficient heat is conducted to the perforated base 6 so that the evaporation functions even when the preheating is switched off.
  • Heat is also conducted to the perforated base 6 via the flame tube 15, which is connected to the perforated base 6 via the flange 17.
  • the preheating at the start can also be carried out using heated air.
  • the heat required for the fuel evaporator is supplied through heat pipes. In this way, the energy from the combustion process can be extracted at a particularly favorable point, since heat conduction is not a problem over long distances.
  • Staged combustion can also be implemented.
  • the first stage burns with a lack of air, so that larger amounts of CO are generated.
  • the second stage the remaining air is mixed in so that the combustion can take place with the optimal amount of air.
  • exhaust gases can also be added to the combustion air in the known manner.
  • multi-stage or modulating burners can also be built with the known means.
  • the prechamber of an internal combustion engine can be constructed analogously, but the functional sequence is somewhat different.
  • the prechamber is arranged centrally in the cylinder head.
  • the inlet and outlet valves are outside the prechamber.
  • the intake combustion air is displaced into the prechamber.
  • fuel is injected into the prechamber, and the mixture flowing out of the prechamber is also ignited outside.
  • a short flame now emerges from the antechamber, which forms between the chamber and the piston. No soot is produced in this way, even when using diesel oil.
  • the compression temperature must be kept lower so that no auto-ignition occurs within the prechamber.
  • the holes 7 shown in the drawings have a diameter of 1.5-2.0 mm. It has been found that this reliably prevents the flame from striking back in the evaporator. These diameters also allow moderate mixture speeds of around 1 - 3 m / s to be operated, so that the pressure of the normal fans is sufficient for oil burners. It is also important that the material of the oil evaporator 5 also consists of a good heat-conductive material for this reason, because this also makes it more difficult for the flame to bounce back through the bores (7). The stated values were determined for a fuel throughput of 0.3-1.0 l / h. It would be possible to choose even smaller cross-sections, but this increases the risk of clogging and the required air pressure increases disproportionately.
  • the security against a backlash of the flame is severely impaired if the outflow speed is not increased enormously, which becomes problematic in the case of small oil burners because of the required fan pressure. Larger holes also increase the likelihood that unevaporated fuel will leave the evaporator.
  • the holes 7 do not necessarily have to have a circular shape, it is also possible to choose slot-shaped openings which can be designed as gills. The stated dimensions for the diameter in this case relate to the slot width.

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

Abstract

L'invention concerne un brûleur de prémélange pour combustibles liquides, comportant un tube de brûleur (2), un système de distribution de combustible, de préférence une buse d'atomisation (1), un agitateur d'air (3), un préchauffage (10) et les électrodes d'amorçage (16). En aval de la buse d'atomisation (1) est disposé coaxialement un évaporateur d'huile (5) présentant, radialement dans son enveloppe ou bien axialement dans son fond (6), des orifices de sortie (7) dont les diamètres sont inférieurs à 5 mm. En aval de ces orifices de sortie (7) font saillie dans la chambre de combustion (12) l'évaporateur d'huile (5) lui-même ou bien des parties thermoconductrices (9, 22) reliées à ce dernier, ou bien un tube de flammes (15) est relié de manière thermoconductrice avec l'évaporateur d'huile (5).
PCT/DE1999/001420 1998-05-14 1999-05-11 Bruleur de premelange pour combustibles liquides Ceased WO1999060306A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE1998121672 DE19821672A1 (de) 1998-05-14 1998-05-14 Vormischbrenner für flüssige Brennstoffe
DE19821672.6 1998-05-14

Publications (1)

Publication Number Publication Date
WO1999060306A1 true WO1999060306A1 (fr) 1999-11-25

Family

ID=7867783

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE1999/001420 Ceased WO1999060306A1 (fr) 1998-05-14 1999-05-11 Bruleur de premelange pour combustibles liquides

Country Status (2)

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DE (1) DE19821672A1 (fr)
WO (1) WO1999060306A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10157856A1 (de) * 2001-11-26 2003-07-17 Rolls Royce Deutschland Magervormischbrenner für eine Gasturbine mit Zündhilfe
DE10246696A1 (de) * 2002-10-07 2004-04-15 Robert Bosch Gmbh Zerstäubungsanordnung
DE102014103817B4 (de) 2014-03-20 2018-07-19 Webasto SE Verdampferbrenner für ein mobiles, mit flüssigem Brennstoff betriebenes Heizgerät
DE102014103813A1 (de) 2014-03-20 2015-09-24 Webasto SE Verdampferbrenneranordnung für ein mobiles, mit flüssigem Brennstoff betriebenes Heizgerät
DE102014103812A1 (de) * 2014-03-20 2015-09-24 Webasto SE Verdampferbrenner für ein mobiles, mit flüssigem Brennstoff betriebenes Heizgerät
DE102014103815B4 (de) 2014-03-20 2018-07-19 Webasto SE Verdampferbrenner
DE102015112932A1 (de) * 2015-08-06 2017-02-09 Eberspächer Climate Control Systems GmbH & Co. KG Mischanordnung

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1265906B (de) 1960-05-14 1968-04-11 Willi Broedlin Brenner fuer fluessige Brennstoffe, insbesondere Heizoel
DE2356769A1 (de) 1973-11-14 1975-06-05 Schladitz Hutzenlaub Gbr Brenner fuer fluessige brennstoffe
DE2649669A1 (de) 1976-10-29 1978-05-03 Messerschmitt Boelkow Blohm Brenner fuer fluessige brennstoffe, insbesondere oele
EP0166329A2 (fr) * 1984-06-25 1986-01-02 AG Verfahrenstechnik für Heizung VTH Brûleur, en particulier brûleur pour l'incinération de combustibles liquides à l'état gazeux
WO1988003249A1 (fr) * 1986-10-27 1988-05-05 Olymp-Werk A. Schwarz Gesellschaft M.B.H. Bruleur pour la combustion de combustible liquide
EP0283435A1 (fr) 1987-03-13 1988-09-21 Füllemann Patent Ag Brûleur
EP0405481A1 (fr) 1989-06-29 1991-01-02 Sintermetallwerk Krebsöge Gmbh Dispositif pour pulvériser un fluide
US5154597A (en) * 1987-03-13 1992-10-13 Vth Ag Verfahrenstechnik Fur Heizung Burner for combustion of gasified liquid fuels
DE4305468A1 (de) 1993-02-23 1994-09-08 Herbert Prof Dr Ing Heitland Arbeitsverfahren für einen Zweitakt-Verbrennungsmotor und Zweitakt-Verbrennungsmotoren zur Durchführung dieses Arbeitsverfahrens
DE4401799C1 (de) 1994-01-22 1995-06-14 Webasto Thermosysteme Gmbh Verdampfungsbrenner für ein Heizgerät
DE19606560A1 (de) * 1996-02-22 1997-09-04 Stephan Herrmann Vorverdampfender und vormischender Brenner für flüssige Brennstoffe
WO1997049952A1 (fr) * 1996-06-25 1997-12-31 Koehne Heinrich Procede et structure d'un bruleur pour la combustion superficielle pour combustibles liquides

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1265906B (de) 1960-05-14 1968-04-11 Willi Broedlin Brenner fuer fluessige Brennstoffe, insbesondere Heizoel
DE2356769A1 (de) 1973-11-14 1975-06-05 Schladitz Hutzenlaub Gbr Brenner fuer fluessige brennstoffe
DE2649669A1 (de) 1976-10-29 1978-05-03 Messerschmitt Boelkow Blohm Brenner fuer fluessige brennstoffe, insbesondere oele
EP0166329A2 (fr) * 1984-06-25 1986-01-02 AG Verfahrenstechnik für Heizung VTH Brûleur, en particulier brûleur pour l'incinération de combustibles liquides à l'état gazeux
WO1988003249A1 (fr) * 1986-10-27 1988-05-05 Olymp-Werk A. Schwarz Gesellschaft M.B.H. Bruleur pour la combustion de combustible liquide
EP0283435A1 (fr) 1987-03-13 1988-09-21 Füllemann Patent Ag Brûleur
US5154597A (en) * 1987-03-13 1992-10-13 Vth Ag Verfahrenstechnik Fur Heizung Burner for combustion of gasified liquid fuels
EP0405481A1 (fr) 1989-06-29 1991-01-02 Sintermetallwerk Krebsöge Gmbh Dispositif pour pulvériser un fluide
DE4305468A1 (de) 1993-02-23 1994-09-08 Herbert Prof Dr Ing Heitland Arbeitsverfahren für einen Zweitakt-Verbrennungsmotor und Zweitakt-Verbrennungsmotoren zur Durchführung dieses Arbeitsverfahrens
DE4401799C1 (de) 1994-01-22 1995-06-14 Webasto Thermosysteme Gmbh Verdampfungsbrenner für ein Heizgerät
DE19606560A1 (de) * 1996-02-22 1997-09-04 Stephan Herrmann Vorverdampfender und vormischender Brenner für flüssige Brennstoffe
WO1997049952A1 (fr) * 1996-06-25 1997-12-31 Koehne Heinrich Procede et structure d'un bruleur pour la combustion superficielle pour combustibles liquides

Also Published As

Publication number Publication date
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