EP0018602B1 - Gasifying oil burner - Google Patents

Gasifying oil burner Download PDF

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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
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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
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EP80102222A
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German (de)
French (fr)
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EP0018602A3 (en
EP0018602A2 (en
Inventor
Winfried Prof.-Dr.-Ing. Buschulte
Friedhelm Dageförde
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Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
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Priority to AT80102222T priority Critical patent/ATE3462T1/en
Publication of EP0018602A2 publication Critical patent/EP0018602A2/en
Publication of EP0018602A3 publication Critical patent/EP0018602A3/en
Application granted granted Critical
Publication of EP0018602B1 publication Critical patent/EP0018602B1/en
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    • 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.

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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)
  • 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)
  • Protection Of Pipes Against Damage, Friction, And Corrosion (AREA)
  • Nonmetallic Welding Materials (AREA)
  • Organic Insulating Materials (AREA)

Abstract

An oil burner including an oil atomizing nozzle to be mounted upstream of a transverse wall in a cylindrical flame tube and to discharge oil through an aperture in the wall through which air also passes into a cylindrical mixing tube positioned co-axially within the flame tube and open at its downstream end. The flame tube has a length at least twice its diameter and a diameter between 2.0 and 2.5 times the diameter of the mixing tube. At least one passage adjacent the transverse wall communicates between the interior of the flame tube and the interior of the mixing tube to recirculate combustion gases from the downstream end of the mixing tube to the upstream end thereof. The peripheral wall of the mixing tube adjacent its downstream end is perforated.

Description

Die Erfindung betrifft einen Vergasungsölbrenner nach dem Oberbegriff des Patentanspruches 1.The invention relates to a gasification oil burner according to the preamble of claim 1.

Vergasungsölbrenner dieser Art (DE-A-2 700 671, FR-A-2 377 002) haben den Vorteil, dass mit ihnen eine russfreie stöchiometrische Verbrennung realisierbar ist und dass die Verbrennung in dem zum Brenner gehörenden Flammrohr stattfindet und damit weitgehend unabhängig ist von der Form und den Abmessungen des Brennraumes des Heizkessels. Die Praxis hat gezeigt, dass derartige Brenner zu einer mehr oder weniger starken Geräuschemission neigen, die insbesondere in Hausheizungsanlagen als störend empfunden werden kann.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.

Bekannt ist ein Vergasungsölbrenner mit russfreier stöchiometrischer Verbrennung mit einem der Zufuhr von Verbrennungsluft dienenden Brennergehäuse mit einer koaxial in diesem angeordneten Ölzerstäuberdüse und einem sich koaxial hierzu erstreckenden Verdampferrohr, das sich frei in den Brennraum des Heizkessels erstreckt. Das Verdampferrohr ist hierbei auf seinem Umfang mit Durchbohrungen versehen, durch die von aussen aus dem Brennraum des Kessels heisse Brenngase in das Verdampferrohr eingesaugt werden sollen. Am offenen Ende des Verdampferrohres ist im Abstand von diesem Ende über Stege eine mit Durchbohrungen versehene Stauscheibe angeordnet, an der das aus dem Verdampferrohr austretende ÖI-Luft-Gemisch mit einer Flamme im Brennraum des Heizkessels ausbrennt. Das Verdampferrohr ist hierbei abhängig vom Brennraum des Kessels und diesem entsprechend zu wählen. Ein derartiger Brenner soll sich durch einen geräuscharmen Betrieb auszeichnen (DE-A-2 712 856).Known is 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. At the open end of the evaporator tube, 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).

Aufgabe der Erfindung ist es, Ölbrenner der gattungsgemässen Art so auszubilden, dass eine wesentliche Verringerung der Geräuschemission erreicht wird.The object of the invention is to design oil burners of the generic type such that a substantial reduction in noise emissions is achieved.

Diese Aufgabe wird gemäss der Erfindung dadurch gelöst, dass das Mischrohr wenigstens über einen an das stromabwärtige Ende angrenzenden Bereich gelocht ausgebildet ist.This object is achieved according to the invention in that the mixing tube is perforated at least over an area adjacent to the downstream end.

Zweckmässige Ausgestaltungen des Mischrohres zur Verminderung der Geräuschemission sind in den Unteransprüchen 2 bis 7 herausgestellt.Appropriate configurations of the mixing tube for reducing the noise emission are set out in subclaims 2 to 7.

Eine andere Möglichkeit, die Geräuschemission zu verringern, besteht darin, den Blendendurchlass aufzuteilen, und zwar in eine Mittelöffnung und eine Mehrzahl weiterer Luftdurchlassöffnungen, die um die Mittelöffnung herum innerhalb einer durch die Projektion des lichten Querschnittes des Mischrohres umschriebenen Fläche angeordnet sind.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.

Die erfindungsgemässe Gestaltung des Mischrohres und die Aufteilung des Blendendurchlasses in eine Mehrzahl von Luftdurchiassöffnungen führen jeweils allein zu einer Verringerung der Geräuschemission. Die gemeinsame Verwendung führt jedoch zu einer kumulativen Wirkung und zu einer stärkeren Verminderung der Geräuschemission als jede der beiden Massnahmen für sich alleine.The inventive design of the mixing tube and the division of the orifice passage into a plurality of air passage openings each alone lead to a reduction in noise emissions. However, the joint use leads to a cumulative effect and a greater reduction in noise emissions than either of the two measures alone.

Die Erfindung ist in der Zeichnung beispielsweise veranschaulicht und im nachstehenden im einzelnen anhand der Zeichnung beschrieben.

  • Fig. 1 zeigt schematisch im Längsschnitt einen Vergasungsölbrenner gemäss der Erfindung in einer ersten Ausführungsform.
  • Fig. 2 zeigt eine ähnliche Darstellung und zeigt zwei weitere Ausführungsformen der Erfindung.
  • Fig. 3 und 4 zeigen Schnitte längs der Linie 111 in Fig. 1 und geben verschiedene Ausführungsmöglichkeiten der erfindungsgemässen Aufteilung des Blendendurchlasses in mehrere Durchlassöffnungen wieder.
The invention is illustrated in the drawing, for example, and described in detail below with reference to the drawing.
  • Fig. 1 shows schematically in longitudinal section a gasification oil burner according to the invention in a first embodiment.
  • Fig. 2 shows a similar representation and shows two further embodiments of the invention.
  • FIGS. 3 and 4 show sections along the line 111 in FIG. 1 and show various possible embodiments of the division of the diaphragm passage according to the invention into several passage openings.

Der dargestellte Brenner 2 weist eine Kammer 4 auf, in der in üblicher Weise auf einem Düsenstock 8 eine Druckzerstäuberdüse 6 gehaltert ist. Das Öl wird von einer Ölpumpe 10 gefördert, die von einem Elektromotor 12 angetrieben wird, der gleichzeitig in üblicher Weise einen Gebläserotor 14 antreibt. Die Pumpe 10 fördert über ein einstellbares Drosselventil 16 und ein elektromagnetisch betätigtes Absperrventil 18 das Öl in den die Zerstäuberdüse 6 tragenden Düsenstock 8. Das Gebläse 14 fördert die Verbrennungsluft über einen Luftkanal 20 in das Gehäuse 4, und zwar über ein Drosselventil 22 mit einer Luftklappe 24, die über einen Motor 26 verstellbar ist. Mit einer auf dem Düsenstock 8 angeordneten Halterung 28 wird ein Zündelektrodenpaar 30 gehaltert, das mit einem Zündtransformator 32 in Verbindung steht.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.

In einem Abstand L3 vor der Mündung der Zerstäuberdüse 6 ist eine als Blende ausgebildete Wand 34 mit einem Blendendurchlass 36 angeordnet. Der Blendendurchlass 36 liegt koaxial mit der Achse der Düse. Stromabwärts vom Blendendurchlass 36 ist ein Mischrohr 38 angeordnet, das über Haltestege 40 an der Blendenwand 34 befestigt ist. Das Mischrohr 38 liegt koaxial in einem Flammrohr 42, dessen stromaufwärtiges Ende dichtend mit der Blendenwandung 34 verbunden ist. Das stromaufwärtige Ende 41 des Mischrohres 38 liegt von der Blendenwandung 34 in einem Abstand L4. Dadurch wird zwischen dem stromaufwärtigen Mischrohrende 41 und der Blendenwand 34 ein radialer Durchlass 35 gebildet, über den aus dem stromabwärts des Mischrohres liegenden Flammenraum Verbrennungsgase rezirkulieren können.At a distance L 3 in front of the mouth of the atomizer nozzle 6, 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. As a result, 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.

Der Durchmesser D2 des Flammrohres entspricht im wesentlichen dem 2 bis 2,5fachen des Durchmessers D, des Mischrohres 38. Die Länge L2 des Flammrohres entspricht wenigstens dem 2,5fachen Durchmesser D2 des Flammrohres. Diese Länge ist erforderlich, damit sich die Flamme, die sich stromabwärts des Mischrohres bildet, mit Sicherheit gegen die innere Flammrohrwandung anlegt und auf diese Weise das Flammrohr an seinem offenen Ende mit Sicherheit durch die Flammenfront abschliesst. Dies ist die Voraussetzung für eine sichere Rezirkulation eines Teiles des Gases über den äusseren Umfang des Mischrohres zurück. Die Rezirkulation wird weiter dadurch erzielt, dass die durch den Blendendurchlass 36 einströmende Luft über den radialen Durchlass 35 einen Unterdruck erzeugt, durch den Rezirkulationsgas angesaugt wird. Um die Rezirkulation nicht zu beeinträchtigen, ist es erforderlich, dass der Strahlquerschnitt der durch den Blendendurchlass strömenden Verbrennungsluft kleiner ist als der Durchmesser D, des Mischrohres 38. Diese Bedingung wird eingehalten, wenn der Durchmesser D3 des Blendendurchlasses gleich oder kleiner dem Durchmesser D, des Mischrohres ist. Durch die Blende wird eine Einschnürung des Luftstromes hinter dem Blendendurchlass erzielt, so dass auch bei annähernd gleichen Durchmessern von Blendendurchlass und Mischrohr noch sichergestellt ist, dass der Querschnitt des Luftstrahls im Bereich des radialen Durchlasses 35 kleiner bleibt als der Mischrohrdurchmesser D,.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. In order not to impair the recirculation, it is necessary that 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,.

Der beschriebene Brenner ist weiter mit einer lonisationssonde 44 versehen, die in das Flammrohr bis in den Flammenbereich vorsteht und die in üblicher Weise an ein Steuergerät 46 angeschlossen ist, über das bei Verlöschen der Flamme die Ölzufuhr durch Schliessen des Ventils 18 und Abschalten des Motors 12 unterbrochen wird.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.

Bei der in Fig. 1 dargestellten ersten Ausführungsform ist das Mischrohr 38 in einem an das stromabwärtige Ende 39 angrenzenden Bereich 37 gelocht ausgebildet. Dieser gelochte Bereich erstreckt sich über den grössten Teil der Länge L:, des Mischrohres. Lediglich ein begrenzter Abschnitt mit einer Länge Lo, die kleiner ist als zwei Drittel des Mischrohrdurchmessers D" ist vollwandig ausgebildet. Grundsätzlich ist es möglich, das Mischrohr auch über seine ganze Länge gelocht auszubilden. Versuche haben jedoch gezeigt, dass sich dann in dem an den radialen Durchlass angrenzenden Bereich mit der Zeit Russ absetzt. Dieser Russniederschlag kann dadurch vermieden werden, dass über den erwähnten Bereich das Mischrohr vollwandig ausgebildet ist.In the first embodiment shown in FIG. 1, 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. In principle, it is possible to design the mixing tube to be perforated over its entire length. However, tests have shown that the the area adjacent to the radial passage settles with soot over time This soot deposit can be avoided if the mixing tube has a solid wall over the area mentioned.

Bei einem Mischrohr, das in bekannter Weise über seine ganze Länge vollwandig ausgebildet ist, ergeben sich optimale Verbrennungsbedingungen, wenn die Gesamtlänge L, + L, etwa dem 1,4-2,5fachen des Durchmessers entspricht. Auch eine Gesamtlänge L, + L, entsprechend dem einfachen Durchmesser kann noch befriedigende Ergebnisse liefern. Bei einem in erfindungsgemässer Weise gelocht ausgebildeten Mischrohr ist es zweckmässig, die Länge etwas grösser zu wählen, wobei die Länge L, etwa 60-80% grösser sein sollte als bei einem ungelochten Mischrohr.In the case of a mixing tube which has a full-walled design over its entire length, optimal combustion conditions result if the total length L, + L corresponds approximately to 1.4-2.5 times the diameter. A total length L, + L, corresponding to the simple diameter, can still give satisfactory results. In the case of a mixing tube which is perforated in accordance with the invention, it is expedient to choose a length which is somewhat longer, the length L being approximately 60-80% greater than in the case of an unperforated mixing tube.

Gute Ergebnisse wurden erzielt bei einem Lochdurchmesser von 2 mm mit einem Lochabstand von 4 mm bei einem Mischrohrdurchmesser D, von 35 mm. Der Lochflächenanteil sollte so gewählt werden, dass quer zur Achse wirksame Gasschwingungen sich durch die Rohrwandung entspannen können, das Rohr jedoch im wesentlichen für den sich in axialer Richtung ausbreitenden Strahl wie eine geschlossene Wand wirkt. Dies ist erreichbar mit einem Lochanteil in dem gelochten Bereich zwischen 20 und 50%. Der Lochflächenanteil wird zusätzlich dadurch begrenzt, dass das Rohr eine bestimmte Strahlungsfläche behalten muss, um die gewünschte Vergasung des Öles vor Eintritt in die Flammzone zu gewährleisten.Good results were achieved with a hole diameter of 2 mm with a hole spacing of 4 mm with a mixing tube diameter D of 35 mm. 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.

Bei den beiden Ausführungsformen nach Fig. 2 ist das Mischrohr 138 jeweils an seinem stromaufwärtigen Ende bis an die Blendenwandung 34 geführt. An die Blendenwandung angronzond ist das Rohr über die Länge L4 gelocht, wobei die Löcher den radialen Durchlass bilden, durch den die Rezirkulationsgase angesaugt werden.In the two embodiments according to FIG. 2, 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.

Bei der Ausführungsform in Fig. 2 unten ist das Mischrohr 138 über seine ganze Länge zylindrisch ausgebildet. In dem Ausführungsbeispiel oberhalb der Mittellinie ist das stromaufwärtige Ende 139 des Mischrohres 138 zur Blendenwandung 34 hin konisch erweitert mit einem Konuswinket, der hier mit 90° gewählt ist. Das Mischrohrende divergiert also in Richtung auf die Blendenwandung 34. Der Lochquerschnitt im Bereich des radialen Durchlasses, angrenzend an die Blendenwandung 34, wird so gewählt, dass eine hinreichende Heissgasmenge rezirkuliert wird.In the embodiment in FIG. 2 below, the mixing tube 138 is cylindrical over its entire length. In the exemplary embodiment above the center line, 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.

In Fig. 1 und 2 ist im Bereich des stromabwärtigen Endes 39 des Mischrohres das Flammrohr 42 mit einer Mehrzahl von Löchern und Durchbrüchen 43 versehen.. Diese Löcher tragen gleichfalls zu einer verminderten Geräuscherzeugung bei. Zweckmässig sind bei einem Flammrohrdurchmesser von 75 mm 6 bis 8 Löcher über den Umfang verteilt bei einem Lochdurchmesser von 8-10 mm.1 and 2, in the region of the downstream end 39 of the mixing tube, the flame tube 42 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.

Mit der erfindungsgemässen Ausbildung des Ölbrenners kommt es zu einer wesentlichen Reduzierung von Geräuschen mit Frequenzen unter 500 Hz, die als besonders störend empfunden werden. Mit der erfindungsgemässen Ausbildung des Mischrohres mit gelochten Abschnitten war es möglich, den Geräuschpegel gegenüber der Ausführung bei Verwendung eines vollwandigen Mischrohres um ca. 3,5 dBA im Rauchgasrohr hinter dem Kesselaustritt und um ca. 4 dBA im Heizraum 1 m vor dem Brenner und in 1 m Höhe über dem Fussboden bei Verwendung des gelochten Mischrohres zu senken.With the design of the oil burner according to the invention, there is a substantial reduction in noise with frequencies below 500 Hz, which are perceived as particularly annoying. With the inventive design of the mixing tube with perforated sections, it was possible to reduce the noise level compared to the version when using a full-walled mixing tube by approx. 3.5 dBA in the flue gas pipe behind the boiler outlet and by approx. 4 dBA in the boiler room 1 m in front of the burner and in Lower 1 m above the floor when using the perforated mixing tube.

Eine Geräuschminderung kann weiter dadurch erzielt werden, dass der Blendendurchlass 36 in eine Mehrzahl von Durchlassöffnungen unterteilt wird. Eine solche Unterteilung führt zu einer Vergrösserung der Oberfläche des durch die Blendenöffnung hindurchtretenden Luftstrahles und damit zu einem günstigeren Schwingungsverhalten der Verbrennungsluft. Eine Ausführungsform ist in Fig. 3 dargestellt. Der Blendendurchlass weist hier eine zentrale Öffnung 136 auf, durch die die Düse das ÖI hindurchfördert. Um die zentrale Öffnung 136 herum ist eine Mehrzahl weiterer Luftdurchlassöffnungen 137 angeordnet, und zwar so, dass sie innerhalb einer durch die Projektion des lichten Querschnittes des Mischrohres 38 umschriebenen Fläche liegen. Bei der Ausführungsform nach Fig. 3 sind die weiteren Luftdurchlassöffnungen 137 rechts mit kreisförmigem Querschnitt dargestellt, wobei die Mittelpunkte auf einem gemeinsamen Kreis liegen. In Fig. 3 links sind die weiteren Luftdurchlassöffnungen 137 mit einem in radialer Richtung gestreckten Querschnitt ausgebildet. Dieser Querschnitt kann beispielsweise Tropfenform haben oder auch annähernd Trapezform. Durch eine solche Querschnittsform ist auf der begrenzten Fläche ein höherer Gesamtdurchlassquerschnitt erreichbar bzw. eine günstigere Anordnung eines vorgegebenen Querschnitts.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. 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. In the embodiment according to FIG. 3, the further air passage openings 137 are shown on the right with a circular cross section, the center points lying on a common circle. 3, 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.

Bei der Ausführungsform nach Fig. sind die aussen liegenden weiteren Durchlassöffnungen 137 wiederum mit kreisförmigem Querschnitt ausgebildet, wobei die Öffnungen mit ihren Mittelpunkten jeweils alternierend auf zwei Kreisen mit unterschiedlichem Durchmesser angeordnet sind.In the embodiment according to FIG. 1, 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.

Auch die beschriebene Aufteilung des Blendendurchlasses in eine Mehrzahl von Durchlassöffnungen führt für sich zu Geräuschminderung. Mit der Mehrlochblende allein war es möglich, den Geräuschpegel gegenüber der Ausführung mit vollwandigem Mischrohr und Einlochblende um ca. 4,5 dBA im Rauchgasrohr hinter dem Kesselaustritt und um ca. 3 dBA im Heizraum 1 m vor dem Brenner und in 1 m Höhe über dem Fussboden bei Verwendung der Mehrlochblende zu senken.The described division of the aperture passage into a plurality of passage openings also leads to noise reduction in itself. With the multi-hole orifice alone, it was possible to reduce the noise level by approx.4.5 dBA in the flue gas pipe behind the boiler outlet and by approx. 3 dBA in the boiler room 1 m in front of the burner and at a height of 1 m compared to the version with a full-walled mixing tube and single-hole orifice Lower the floor when using the multi-hole panel.

Versuche haben jedoch gezeigt, dass beide Massnahmen kumulativ wirken und damit durch die gleichzeitige Verwendung der beschriebenen Ausbildung des Blendendurchlasses und des Mischrohres besonders gute Ergebnisse erzielbar sind. So wurden mit dieser erfindungsgemässen Kombination Geräuschpegeisenkungen von ca. 6 dBA im Rauchgasrohr hinter dem Kesselaustritt und um ca. 5 dBA im Heizraum 1 m vor dem Brenner und in 1 m Höhe über dem Fussboden gemessen.However, tests have shown that both measures have a cumulative effect and that particularly good results can be achieved by simultaneously using the described design of the aperture passage and the mixing tube. With this combination according to the invention, noise reductions of approximately 6 dBA in the flue gas pipe behind the boiler outlet and by approximately 5 dBA in the boiler room were measured 1 m in front of the burner and at a height of 1 m above the floor.

Claims (9)

1. An oil burner (2) comprising an oil atomizing device (6), an air supply duct (4) surrounding said oil atomizing device, an orifice plate (34) positioned downstream of the outlet of the oil atomizing device, said orifice plate having therein an orifice (36), a mixing tube positioned downstream from and co-axially with said orifice in said wall, a radial passage (35) at the upstream end of the mixing tube adjacent to said orifice plate, a substantially cylindrical flame tube (42), the upstream end of which is seaiingly connected to the end wall of the air supply duct (4) supporting said orifice plate and in which said mixing tube is positioned substantially co-axially, said flame tube (42) having a diamter (D2), which is substantially 2,0 to 2.5 times the diameter (D,) of said mixing tube, and having a length (L2) which is at least 2.5 times the diameter (D2) of said flame tube, characterized in that at least a portion of said mixing tube (38, 138) adjacent the downstream end (39) is perforated.
2. An oil burner according to Claim 1, characterized in that adjacent to the passage (35) between mixing tube and orifice plate (34) the mixing tube (38) has an unperforated portion of a length (L0) which is less than two thirds of the diameter (D,) of the mixing tube, and the portion extending downstream from the end of said unperforated portion is perforated.
3. An oil burner according to Claim 1 or 2, characterized in that the mixing tube (138) extends to said orifice plate (34) and is perforated in the area of the radial passage (35).
4. An oil burner according to Claim 3, characterized in that the perforated portion (L.) of said mixing tube (138) adjacent the orifice plate (34) is conical and divergent in direction towards said orifice plate.
5. An oil burner according to Claim 4, characterized in that the conical portion (135) is formed with a cone angle of approximately 90°.
6. An oil burner according to one of the preceding claims, characterized in that the sum of the area of the perforations in the downstream perforated portion (37) of the mixing tube (38, 138) is between 20 and 50% of the surface area of the tube in this area.
7. An oil burner according to one of the preceding claims, characterized in that the diameter of the perforations in the downstream perforated portion (37) of the mixing tube (38, 138) is between 4 and 10% of the diameter (D,) of said mixing tube.
8. An oil burner (2) comprising an oil atomizing device (6), an air supply duct (4) surrounding said oil atomizing device, an orifice plate (34) positioned downstream of the outlet of the oil atomizing device, said orifice plate having therein an orifice (36), a mixing tube positioned downstream from and co-axially with said orifice in said wall, a radial passage (35) at the upstream end of the mixing tube adjacent to said orifice plate, a substantially cylindrical flame tube (42), the upstream end of which is sealingly connected to the end wall of the air supply duct (4) supporting said orifice plate and in which said mixing tube is positioned substantially co-axially, said flame tube (42) having a diameter (Dz), which is substantially 2.0 to 2.5 times the diameter (D,) of said mixing tube, and having a length (L,), which is at least 2.5 times the diameter (Dz) of said flame tube, characterized in that the orifice of the orifice plate has a ceniral opening (136) and arranged in a circle around said central opening a plurality of further air openings (137) positioned on an area within the projection of the internal cross-section of the mixing tube (38).
9. An oil burner according to one of Claims 1 to 7, characterized in that the diameter (D3) of the orifice in the orifice plate is equal to or less than the diameter (D,) of the mixing tube.
EP80102222A 1979-05-08 1980-04-25 Gasifying oil burner Expired EP0018602B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT80102222T ATE3462T1 (en) 1979-05-08 1980-04-25 GASING OIL BURNER.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2918416A DE2918416C2 (en) 1979-05-08 1979-05-08 Gasification oil burner
DE2918416 1979-05-08

Publications (3)

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

Family

ID=6070161

Family Applications (1)

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EP80102222A Expired EP0018602B1 (en) 1979-05-08 1980-04-25 Gasifying oil burner

Country Status (15)

Country Link
US (1) US4318688A (en)
EP (1) EP0018602B1 (en)
JP (1) JPS55150412A (en)
AT (1) ATE3462T1 (en)
AU (1) AU526030B2 (en)
CA (1) CA1147252A (en)
DD (1) DD150642A5 (en)
DE (1) DE2918416C2 (en)
DK (1) DK156919C (en)
ES (1) ES491252A0 (en)
FI (1) FI66979C (en)
GR (1) GR68000B (en)
IE (1) IE49595B1 (en)
NO (1) NO156185C (en)
YU (1) YU41711B (en)

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Also Published As

Publication number Publication date
DD150642A5 (en) 1981-09-09
DK181780A (en) 1980-11-09
JPS6152364B2 (en) 1986-11-13
DK156919B (en) 1989-10-16
US4318688A (en) 1982-03-09
DE2918416A1 (en) 1980-11-13
JPS55150412A (en) 1980-11-22
ES8101244A1 (en) 1980-12-01
GR68000B (en) 1981-10-26
YU41711B (en) 1987-12-31
IE800946L (en) 1980-11-08
ES491252A0 (en) 1980-12-01
EP0018602A3 (en) 1981-01-14
IE49595B1 (en) 1985-10-30
YU119880A (en) 1983-04-30
FI66979B (en) 1984-08-31
NO156185C (en) 1987-08-05
ATE3462T1 (en) 1983-06-15
NO156185B (en) 1987-04-27
FI801401A (en) 1980-11-09
DK156919C (en) 1990-03-12
DE2918416C2 (en) 1985-05-15
AU526030B2 (en) 1982-12-16
EP0018602A2 (en) 1980-11-12
AU5786080A (en) 1980-11-13
NO801347L (en) 1980-11-10
CA1147252A (en) 1983-05-31
FI66979C (en) 1984-12-10

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