EP0579008A2 - Ölbrenner - Google Patents

Ölbrenner Download PDF

Info

Publication number
EP0579008A2
EP0579008A2 EP93110067A EP93110067A EP0579008A2 EP 0579008 A2 EP0579008 A2 EP 0579008A2 EP 93110067 A EP93110067 A EP 93110067A EP 93110067 A EP93110067 A EP 93110067A EP 0579008 A2 EP0579008 A2 EP 0579008A2
Authority
EP
European Patent Office
Prior art keywords
oil
nozzle
atomizing
gas
swirl
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.)
Withdrawn
Application number
EP93110067A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0579008A3 (enrdf_load_stackoverflow
Inventor
Hans-Benno Dr. Ricke
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.)
KRAFT-INDUSTRIEWARMETECHNIK DR RICKE GmbH
Original Assignee
KRAFT-INDUSTRIEWARMETECHNIK DR RICKE GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by KRAFT-INDUSTRIEWARMETECHNIK DR RICKE GmbH filed Critical KRAFT-INDUSTRIEWARMETECHNIK DR RICKE GmbH
Publication of EP0579008A2 publication Critical patent/EP0579008A2/de
Publication of EP0579008A3 publication Critical patent/EP0579008A3/xx
Withdrawn legal-status Critical Current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
    • F23D11/408—Flow influencing devices in the air tube
    • 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
    • F23D11/007—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 F23D11/10 and F23D11/24

Definitions

  • the invention relates to an oil burner with an oil nozzle which can be supplied with oil by means of an oil supply line and from which an oil jet can be emitted, an atomizing gas nozzle which is arranged downstream of the oil nozzle and can be supplied with compressed atomizing gas by means of a gas supply line and in which an opening direction is provided Widening nozzle space is formed, in which the oil jet and the atomizing gas can be mixed and the resulting oil / atomizing gas flow can be subjected to a swirl, and a burner tube which coaxially surrounds the oil nozzle and the atomizing gas nozzle, with its downstream end section over the outlet surface of the nozzle space of the atomizing gas nozzle protrudes and through which the mixed and swirled oil / atomizer gas stream emerging from the atomizer gas nozzle can be charged with combustion air.
  • soot and / or coke deposits cannot be excluded, by which the Operation of a furnace or furnace is subject to sensitive interference.
  • the flame propagation and thus the heat transfer properties of the oil burner can be influenced in an undesirable manner, local overheating of individual components of the oil burner can occur, the flame tube and the combustion chamber or the burner block being particularly worth mentioning, the ignitability and the flame monitoring can be impaired, contamination of the goods to be heated can occur in a directly fired furnace, drying or heat treatment system, or the trains of a boiler system can become blocked.
  • Such soot and / or coke deposits can also lead to considerable impairments on flat flame burners, since in such flat flame burners the flame temperature can be cooled down by exhaust gas recirculation to such an extent that after-burning solid particles no longer occur.
  • the invention has for its object to provide an oil burner, the flame free of unburned carbon particles is.
  • the oil to be burned is finely atomized and partially evaporated by a compressed atomizing gas, so that the flame of the burner is colored blue-violet from its root like a gas flame.
  • Such a flame is free of unburned carbon particles, it is clean, ie it does not cause soot or coke deposits on the oil burner or in the furnace, nor does it carry such carbon particles into the environment.
  • the oil Due to the nozzle design of the oil burner according to the invention, the oil is first atomized and then finely divided by an axially rotating atomizing gas stream and deflected in a primarily radial outflow direction, the opening angle of the outflow being between 90 and 180 degrees.
  • the opening angle is normally less than 90 degrees
  • the result of the oil burner according to the invention is considerably larger Opening angle.
  • the oil / atomizing gas stream is pulled apart to a larger outflow cross-section, while in the area of the main flow or central axis of the oil jet emitted from the oil nozzle, a zone of static negative pressure is created downstream of the nozzle area of the oil burner, into which gas flows upstream in the direction of the nozzle area of the oil burner the environment is returned. If this recirculated gas is already heated as a combustion product, it transfers part of its sensible heat to the outflowing oil / atomizer gas stream, as a result of which the oil droplets evaporate and, after mixing the oil / atomizer gas stream with the combustion air stream, which contains about 95% of the air volume required for stoichiometric combustion, burn without soot.
  • Such an exemplary embodiment has proven to be particularly advantageous for the expedient operation of the oil burner according to the invention, in which the sum of the outlet surface cross sections of the gas emission channels is approximately 0.7 times the narrowest flow cross-sectional area of the nozzle space of the atomizer gas nozzle.
  • a more intense swirling of the oil / atomizer gas flow can be achieved if the oil jet is already swirled in the oil nozzle.
  • the oil burner according to the invention is to be designed as a flat flame burner, it is advantageous if the swirl caused in the oil nozzle is in the same direction as the swirl caused in the atomizer gas nozzle.
  • the oil burner can be used advantageously, in particular, as a flat flame burner if the swirl caused by the swirl disk is in the same direction as the swirl caused in the atomizer gas nozzle.
  • a flat flame burner both the oil jet and the atomizing gas jets and the combustion air flow should be subjected to a swirl in the same direction.
  • the swirl caused by the swirl disk should be opposite to the swirl caused in the atomizing gas nozzle, which in turn should possibly be opposite to the swirl acting on the oil jet in the oil nozzle.
  • the combination of the oil / atomizer gas stream with the combustion air stream can be improved if a separating disk, which coaxially surrounds the atomizer nozzle and by means of which is available for the combustion air stream, is arranged downstream of the swirl disk and upstream of a mixing section in which the combustion air stream meets the oil / atomizer gas stream standing flow cross section is reduced.
  • the diameter of the nozzle space of the atomizing nozzle can increase linearly or progressively downstream of its narrowest flow cross-sectional area.
  • a linear or a progressive enlargement of the diameter of the nozzle space can be expedient.
  • the atomizer nozzle can advantageously be designed as a separate component and can be pressed by means of the oil nozzle under spring tension against a seat provided for it on a burner head of the oil burner.
  • oil is emitted from an oil nozzle 2 and mixed with an atomizing gas in an atomizing nozzle 3 and swirled by atomizing gas jets before the mixed and swirled oil / atomizing gas stream 4 is combined with a combustion air stream 5.
  • the oil nozzle 2 is supplied with an adjustable oil flow 7 via an oil supply line 6, in which valves (not shown) are provided and which is connected to an oil pump (also not shown).
  • the oil nozzle 2 is used for metering an oil jet 8 and is also designed in a manner known per se so that the oil jet 8 leaving it is subjected to a swirl directed around its main flow axis 9.
  • the atomizing nozzle 3 is arranged behind the oil nozzle 2.
  • the atomizer nozzle 3 forms a trumpet-like widening nozzle chamber 10, into which the swirled oil jet 8 is injected.
  • gas emission channels 11 are formed, approximately in the radial direction of the atomizing nozzle 3.
  • the gas emission channels 11, of which six are provided in the embodiment shown are arranged at the same circumferential distance from one another around the central axis of the nozzle chamber 10 or the main flow axis 9 of the oil jet 8.
  • longitudinal axes 12 of the gas emission channels 11 do not intersect the central axis or main flow axis 9 running perpendicular to them, but are arranged at a distance 13 parallel to the radii intersecting the central axis or the main flow axis 9.
  • the atomizing nozzle 3 is connected to a compressed gas source (not shown in detail) via a gas supply line 14 running coaxially to the oil supply line 6 in the oil burner area.
  • a compressed gas source e.g. Air, oxygen or water vapor are used.
  • the atomizing gas stream 15 is divided into the gas emission channels 11, from which it strikes the oil jet 8 at a high speed quasi tangentially or secant and accordingly applies a swirl to it, which is opposite to the original swirl of the oil jet 8 predetermined by the oil nozzle 2. This results in the well-mixed oil / atomizer gas flow 4 leaving the nozzle chamber 10 of the atomizer nozzle 3 through its outlet surface 16 approximately radially to the central axis of the nozzle chamber 10.
  • the sum of the exit surface cross sections of the six gas emission channels 11 in the illustrated embodiment is approximately 0.7 times the narrowest flow cross section area 17 of the nozzle chamber 10 of the atomizer nozzle 3.
  • the oil / atomizing gas stream 4 leaving the nozzle chamber 10 essentially in the radial direction is then combined with the combustion air stream 5, which is fed through a burner tube 18 arranged in the oil burner area coaxially to the gas supply line 14 from an air source, not shown.
  • the combustion air stream 5 passes through an annular swirl disk 20, seated between the gas supply line 14 and the burner chamber 18 and through which swirl channels 19 pass, in which it is subjected to a swirl that corresponds to that of the nozzle chamber 10 of the atomizer nozzle 3 in the radial direction leaving oil / atomizer gas flow 4 is opposite.
  • the swirled combustion air flow 5 is reduced by a separating disc 22, which reduces the flow cross section of the burner pipe 18 available for the combustion air flow 5 to a comparatively small outer ring cross section, jammed.
  • the combustion process now takes place in the part of the burner tube 18 projecting beyond the atomizer nozzle 3 and in a part of a flame tube 23 projecting beyond the relevant end of the burner tube 18.
  • both volatile and high-boiling oils can be burned in a large output range, even at furnace chamber temperatures> 1300 degrees Celsius.
  • the compressed atomizing gas e.g. air, oxygen or water vapor
  • the compressed atomizing gas jets envelop the oil jet 8 emerging from the oil nozzle 2 under pressure, push it through and accelerate it, break up the oil droplets more finely by means of shear forces and swirl the oil mist formed about the main flow axis 9 of the oil jet 8.
  • the mixed oil flows / Atomizer gas flow 4 along the outwardly curved envelope surface of the nozzle chamber 10 of the atomizer nozzle 3 and leaves it in a primarily radial direction, ie, perpendicular to the main flow axis 9 of the oil jet 8 emerging from the oil nozzle 2 with the formation of an axially close, rotationally symmetrical space 24 of static negative pressure.
  • the oil / atomizing gas stream 4 flowing radially outward through the space 25 mixes in the annularly shaped mixing section 21 with the combustion air stream 5 flowing in from the annular space 26. Part of this becomes static in the space 24 near the axis, forming a toroid as a burning, highly heated mixture Sucked back vacuum, where it mixes with the radially flowing oil / atomizer gas flow 4 in the space 25, transfers some of its sensible heat to it and thus contributes to the evaporation of the oil mist.
  • the flame front returns to the nozzle chamber 10, which progressively widens in the downstream direction, inside the atomizer nozzle 3, as a result of which the compact mixture forming the oil / atomizer gas stream 4 in the region of the envelope surface of the nozzle chamber 10 is heated up.
  • the oil / air mixture completely burns out in a relatively small combustion chamber volume, with the development of high temperatures down to the regions of the room 24 static negative pressure or the nozzle chamber 10 near the oil nozzle.
  • the burn-out in a small combustion chamber volume allows the use of the oil burner 1 described above for high-speed burners and especially for flat-flame burners, for which gas burners have previously been used primarily, in those furnace systems in which, for procedural reasons, the flame is guided along the inner furnace wall or ceiling.
  • FIGS. 2 and 3 show the nozzle design of the oil burner 1 shown in FIG. 1 in detail.
  • the sum of the outlet surface cross sections of the gas emission channels 11 is smaller than the narrowest flow cross section area 17 of the nozzle chamber 10 of the atomizer nozzle 3. Since the flow cross section of the nozzle chamber 10 increases downstream, any residual pressure of the atomizer gas jets which is still present has a swirl-enhancing effect when it leaves the gas emission channels 11.
  • the oil / atomizing gas stream 4 lies securely on the outer envelope surface of the nozzle chamber 10 and leaves the nozzle chamber 10 at an opening angle which is predetermined by the angle Beta of the outflow tangent 28. With this nozzle design, this angle beta is largely constant over a wide range of throughput and gas pressure variations.
  • FIG. 1 shows the nozzle design of the oil burner 1 shown in FIG. 1 in detail.
  • the sum of the outlet surface cross sections of the gas emission channels 11 is smaller than the narrowest flow cross section area 17 of the nozzle chamber 10 of the atomizer nozzle 3. Since the
  • the opening angle alpha of the outflowing oil / atomizer gas flow 4 remains constant with increasing pressure, determined by the outlet angle of the envelope surface of the nozzle chamber 10 or the angle Beta of the outlet tangent 28.
  • the downstream of the atomizer nozzle 3 The current flow profile becomes sharper with increasing pre-pressure of the atomizing gas, the individual jets of the incoming atomizing gas begin to emerge, the hollow cap in front of the mouth of the atomizing nozzle 3 becomes more pronounced.
  • an atomizer nozzle 3 with the cross section shown in FIG. 4 shows a different behavior at different admission pressures of the atomizer gas.
  • the gas-emitting channels 11 open into a pre-swirling chamber 29, the outlet surface of which forms the narrowest flow cross-sectional area 17 of the nozzle chamber 10, which is continuously expanded linearly downstream.
  • the outflowing oil / atomizer gas flow 4 is always at the outer admission pressure of the atomizer gas on the outer envelope surface of the nozzle space 10 on and leaves the atomizer nozzle 3 with an opening angle that is the same as that of the atomizer nozzle 3.
  • the flow of the mixture can change into a purely radial flow with an opening angle> 180 degrees, which does not change its contour with increasing admission pressure of the atomizing gas until it changes into an axially directed flow from a certain admission gas pressure , whereby the opening angle that is set becomes smaller with increasing admission pressure of the atomizing gas. If the admission pressure of the atomizing gas is then reduced, the flow changes back into a radially directed flow, but at a significantly lower admission pressure of the atomizing gas than when the radial flow is changed into an axial flow.
  • This hysteresis is shown in the diagram according to FIG. 6 for two different atomizing nozzles 3.
  • the changeover point from radial to axial is influenced by the opposite or the same direction of the swirl direction of the oil and the atomizing gas, but not the changeover point from axial to radial flow.
  • the ratio is ⁇ 0.5, a stable radial outflow is also not to be expected, because then the influence of the oil jet from the oil nozzle 2 on the flow contour of the oil / atomizer gas flow 4 decreases. This is because the oil jet 8 expands the jet of the oil / atomizing gas stream 4. If the narrowest flow cross-sectional area 17 of the nozzle chamber 10 is too large, the mixing process between the oil jet 8 and the atomizing gas is impaired. The exchange of impulses and transmission of shear forces are then reduced. In order to generate an at least partially blue-violet flame pattern, it is necessary to feed in larger quantities of atomizing gas.
  • An atomizer nozzle 3 according to FIG. 4 with a radial outflow is particularly suitable for use in flat-flame burners. It provides complete burnout in the smallest possible space.
  • the flame shape is optimal when the oil jet 8, the atomizing gas jets and the combustion air stream 5 are twisted in the same direction.
  • An atomizer nozzle 3 according to FIG. 3 is optimal if the oil jet 8, the atomizer gas jets and the combustion air stream 5 are to be varied continuously over a wide performance range.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)
EP93110067A 1992-07-11 1993-06-24 Ölbrenner Withdrawn EP0579008A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19924222839 DE4222839A1 (de) 1992-07-11 1992-07-11 Ölbrenner
DE4222839 1992-07-11

Publications (2)

Publication Number Publication Date
EP0579008A2 true EP0579008A2 (de) 1994-01-19
EP0579008A3 EP0579008A3 (enrdf_load_stackoverflow) 1994-02-23

Family

ID=6462989

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93110067A Withdrawn EP0579008A2 (de) 1992-07-11 1993-06-24 Ölbrenner

Country Status (3)

Country Link
EP (1) EP0579008A2 (enrdf_load_stackoverflow)
CN (1) CN1085643A (enrdf_load_stackoverflow)
DE (1) DE4222839A1 (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT408796B (de) * 1999-04-29 2002-03-25 Dumag Ohg Brenner
EP1705424A1 (en) * 2005-03-04 2006-09-27 Riello S.p.a. Liquid-fuel burner combustion head
WO2019017176A1 (ja) * 2017-07-21 2019-01-24 スプレーイングシステムスジャパン合同会社 二流体ノズル

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10005256B4 (de) * 2000-02-05 2010-04-29 Elster Gmbh Brenner für gasförmige oder flüssige Brennstoffe
CN114992632B (zh) * 2022-06-22 2024-07-30 西北工业大学 一种基于球头管路的可拆装多功能燃油喷嘴

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2303104A (en) * 1940-03-15 1942-11-24 Harold G Abbey Wide range oil burner
DE962391C (de) * 1953-12-08 1957-04-18 Daimler Benz Ag Einrichtung zur Zerstaeubung und Mischung von Brennstoff mit Druckluft an Brennkammern, insbesondere fuer Brennkraftturbinen
FR1350802A (fr) * 1962-12-18 1964-01-31 Hersan Et Cie Perfectionnements aux brûleurs à combustibles liquides à pulvérisation mécanique
DE2447151C3 (de) * 1974-10-03 1979-04-19 Smit Nijmegen B.V., Nijmegen (Niederlande) Brenner zur Verbrennung von flüssigem Brennstoff
US3979069A (en) * 1974-10-11 1976-09-07 Luigi Garofalo Air-atomizing fuel nozzle
GB1565844A (en) * 1976-08-05 1980-04-23 Coulon C Method and apparatus for burning liquid fuels
US4335804A (en) * 1979-07-30 1982-06-22 Bardin Viktor P Vortex-type oil mist generator
DE3544420A1 (de) * 1985-12-16 1987-07-30 Hench Hans Vorrichtung zur erzeugung von aerosolen
DE3709667A1 (de) * 1987-03-24 1988-10-13 Theophil Bauer Duese zum verspruehen zweier medien

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT408796B (de) * 1999-04-29 2002-03-25 Dumag Ohg Brenner
EP1705424A1 (en) * 2005-03-04 2006-09-27 Riello S.p.a. Liquid-fuel burner combustion head
WO2019017176A1 (ja) * 2017-07-21 2019-01-24 スプレーイングシステムスジャパン合同会社 二流体ノズル
JP2019018183A (ja) * 2017-07-21 2019-02-07 スプレーイングシステムスジャパン合同会社 二流体ノズル

Also Published As

Publication number Publication date
DE4222839A1 (de) 1994-01-13
CN1085643A (zh) 1994-04-20
EP0579008A3 (enrdf_load_stackoverflow) 1994-02-23

Similar Documents

Publication Publication Date Title
DE3306483C2 (enrdf_load_stackoverflow)
DE69210715T2 (de) Brenner mit geringer NOx-Produktion
EP0598189B1 (de) Zerstäuber für einen Ölbrenner
DE4326802A1 (de) Brennstofflanze für flüssige und/oder gasförmige Brennstoffe sowie Verfahren zu deren Betrieb
DE69101389T2 (de) Brenner für festen und flüssigen oder gasförmigen Brennstoff.
DE2700671C2 (de) Blaubrennender Ölbrenner
DE876495C (de) Brennkammer fuer Gasturbinen
DE2953648C2 (de) Flüssigbrennstoffbrenner
EP0710799A2 (de) Verfahren zur thermischen Oxidation von flüssigen Abfallstoffen
EP0189390B1 (de) Zerstäubungsdüse für flüssigen Brennstoff
EP0101462B1 (de) Brenner für staubförmige, gasförmige und/oder flüssige brennstoffe
CH626151A5 (enrdf_load_stackoverflow)
EP0645583A1 (de) Gasbrenner
EP0579008A2 (de) Ölbrenner
EP1752633B1 (de) Vorrichtung zur Heißgaserzeugung im Abgasstrang eines Verbrennungsmotors
EP0585442B1 (de) Ablagerungsfreier brenner
DE19537636A1 (de) Verfahren zum Betrieb einer Kraftwerksanlage
DE4422535A1 (de) Verfahren zum Betrieb einer Feuerungsanlage
EP0072950A2 (de) Verfahren zur Verdampfung und Verbrennung flüssiger Brennstoffe sowie Brenner hierzu
DE19542644B4 (de) Vormischverbrennung
WO2010097197A2 (de) Brenner für eine thermische nachverbrennungsvorrichtung
DE19531387C2 (de) Verfahren zum Verbrennen insbesondere flüssiger Brennstoffe und Brenner zur Durchführung des Verfahrens
DE3341305A1 (de) Vergasungsoelbrenner
DE4327497A1 (de) Zerstäuberdüse für einen Brenner sowie Brenner
DE68909851T2 (de) Verbrennungsvorrichtung.

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

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE ES FR GB IT NL

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE ES FR GB IT NL

17P Request for examination filed

Effective date: 19940729

17Q First examination report despatched

Effective date: 19960109

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

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 19960521