EP0007424B1 - Brûleur pour combustion de carburants liquides - Google Patents

Brûleur pour combustion de carburants liquides Download PDF

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Publication number
EP0007424B1
EP0007424B1 EP19790101956 EP79101956A EP0007424B1 EP 0007424 B1 EP0007424 B1 EP 0007424B1 EP 19790101956 EP19790101956 EP 19790101956 EP 79101956 A EP79101956 A EP 79101956A EP 0007424 B1 EP0007424 B1 EP 0007424B1
Authority
EP
European Patent Office
Prior art keywords
chamber
combustion
fuel
air
vortex
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP19790101956
Other languages
German (de)
English (en)
Other versions
EP0007424A1 (fr
Inventor
Johannes Wilhelmus Graat
Hans Theodoor Remie
A.M. Verhagen
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.)
Smit Ovens Nijmegen BV
Original Assignee
Smit Ovens Nijmegen BV
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
Priority claimed from DE19782828319 external-priority patent/DE2828319C2/de
Priority claimed from DE19792912101 external-priority patent/DE2912101A1/de
Priority claimed from DE19792912083 external-priority patent/DE2912083A1/de
Priority claimed from DE19792912102 external-priority patent/DE2912102C2/de
Application filed by Smit Ovens Nijmegen BV filed Critical Smit Ovens Nijmegen BV
Priority to AT79101956T priority Critical patent/ATE1870T1/de
Publication of EP0007424A1 publication Critical patent/EP0007424A1/fr
Application granted granted Critical
Publication of EP0007424B1 publication Critical patent/EP0007424B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
    • F23D11/101—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet
    • F23D11/105—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet at least one of the fluids being submitted to a swirling motion
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23Q—IGNITION; EXTINGUISHING-DEVICES
    • F23Q7/00—Incandescent ignition; Igniters using electrically-produced heat, e.g. lighters for cigarettes; Electrically-heated glowing plugs
    • F23Q7/06—Incandescent ignition; Igniters using electrically-produced heat, e.g. lighters for cigarettes; Electrically-heated glowing plugs structurally associated with fluid-fuel burners
    • F23Q7/08—Incandescent ignition; Igniters using electrically-produced heat, e.g. lighters for cigarettes; Electrically-heated glowing plugs structurally associated with fluid-fuel burners for evaporating and igniting liquid fuel, e.g. in hurricane lanterns

Definitions

  • the invention relates to a burner arrangement for the combustion of liquid fuels, with a cylindrical swirl chamber which is closed on one side by a rear wall and opens on the other side in a combustion chamber, with an opening or openings for supplying the combustion air in the jacket of the swirl chamber , wherein the combustion air is introduced through the openings and generates a vortex sinking flow, and with a cylindrical jacket tube downstream of the vortex chamber, which surrounds the chamber concentrically and is open to the furnace side.
  • a vortex sinking flow is to be understood as an air movement which is circular, with a slight air compression towards the edge of the vortex chamber due to the centrifugal forces. This air flow creates a negative pressure inside the vortex that can be used to suck in the fuel.
  • the burner arrangement therefore does not require a fuel pump. All that is required to convey the fuel is that it is introduced in the region of the axis of the swirl sinking flow, since experience has shown that the negative pressure reaches its maximum value here.
  • the introduced fuel which is fed in a compact jet, is immediately torn apart by the turbulence within the air movement and divided into the finest particles and burned soot-free at the appropriate temperature conditions.
  • the beam diameter is between 0.5-2.0 mm, for example.
  • the negative pressure of the introduction that can be generated in the swirl chamber is between - 0.03 and - 0.15 bar.
  • DE-B 1 157 333 discloses a burner arrangement of the type mentioned at the outset for the combustion of liquid fuels.
  • a fuel atomizer nozzle is located near the mouth of the swirl chamber. The vortex flow is first generated in the vortex chamber; the fuel is only absorbed when it exits the swirl chamber.
  • a device in which, in a burner arrangement of the type mentioned at the outset, the inlet opening for the fuel is arranged centrally on the rear wall of the swirl chamber, the fuel leaving the inlet opening as a compact jet, and in which a concentrically located guide sleeve is installed, which is provided on its side in the region of the swirl chamber with peripherally distributed suction openings.
  • the burner arrangement according to the invention has the advantage that disruptive elements within the swirl chamber can be eliminated. As a result, the air pressure and thus the required power of the fan for the combustion air can be significantly reduced. Another advantage is that part of the fuel that flows out of the opening looks for a creepage path along the walls of the swirl chamber. These not inconsiderable portions of the fuel are torn apart by the air flow at the edge of the swirl chamber, with further energy utilization taking place.
  • the built-in guide sleeve causes forced recirculation of part of the burning mixture.
  • a large part of the energy to be used in the fans is obviously not used at all to maintain the circulation and breakdown of the oil droplets, but rather to counteract the build-up in the casing. This wastes considerable energy uselessly.
  • the air pressure to be used can be considerably reduced.
  • the reduced fan power also reduces the noise pollution caused by the airflow noise.
  • Another effect that is achieved is that larger oil droplets, which are due to the centrifugal force more in the outer region of the swirling current movement, are returned again and thus travel a longer distance so that they can evaporate more completely.
  • a device is known from DE-B 2517756, in which In the area of the inlet opening for the fuel, a strong swirl and thus a vortex sinking flow is generated, with the aid of which the fuel can be sucked in.
  • This arrangement lacks a closed vortex chamber, which is simultaneously a mixing and atomizing chamber, but in which no combustion takes place.
  • the principle of the mixing and atomizing chamber only makes it possible to combine the suction process with a mixing and atomizing process, whereby at the same time the ratio between fuel and combustion air, which is also the atomizing medium, can be set in the range of the stoichiometric ratio.
  • the guide sleeve In order to be able to adapt the guide sleeve to different burner conditions, heat demand numbers and the like, it is arranged adjustably across the end wall of the combustion chamber, with the adjustment also being able to change the clear width of the suction openings. This can be done structurally simply by the guide sleeve being slidably attached to several supports.
  • An increase in the circulation effect can furthermore be brought about by the fact that the casing tube of the burner projects beyond the guide sleeve and has a constriction in the protruding area.
  • the entire combustion air is preferably also used as an atomizing medium in order to use its energy content as completely as possible. This also means that only a relatively low air pressure has to be maintained for the incoming combustion air.
  • the fuel particles are mixed with the air completely homogeneously and thus achieve a very short burnout time. Combustion can be carried out stoichiometrically over wide load ranges. The power can be controlled simply by changing the amount of combustion air supplied by controlling the drive power of the associated fan. A very simple controller can thus be assigned to the combustion device.
  • the air flow for generating a vortex sinking flow is made possible by the fact that the feed openings to the vortex chamber are cut obliquely, so that a supply air flow occurs tangentially to an imaginary circle within the vortex chamber and rotates the contents of the vortex chamber.
  • air baffles or impact bodies which produce the same effect.
  • the inlet opening for the fuel is arranged "centrally"; this choice of words also means that it is possible to deviate from the exact center position or that several openings have to be provided. It is essential that the fuel is supplied in the region of the strongest negative pressure in order to be as precise as possible to be able to maintain high flow rates.
  • the burner arrangement described is primarily suitable for being used for household burners which have only low fuel oil consumption.
  • so-called micro burners are required for single-family houses, which have an oil consumption in the range of 1-3 kg of oil per hour.
  • the fuel usually heating oil
  • the fuel is fed from a storage container 31 to the actual burner via a line 32.
  • a float regulator 33 is installed between the storage container and the burner, which ensures that the pressure between the burner fuel inlet and the level of the float regulator 33 is always the same. This ensures the proportionality between the negative pressure and the amount of fuel in the unit of time.
  • the line 32 ends in a bore 34 which ends in an armature housing 54.
  • a soft iron anchor 55 is movably mounted in the armature housing and can be pulled into the armature housing 54 against the force of a spring 57 by the coil 56.
  • the armature 55 has a collar 58 which limits the movement of the armature into the armature housing 54.
  • the armature runs on the side facing away from the coil 56 into a valve needle 60 which opens and closes a further bore, the inlet opening 30.
  • the armature-coil arrangement is contained in a housing bush 61, which is screwed to a cylindrical housing 35, which has two different-sized cylindrical bores from the two base sides of the cylinder, which are connected to one another via the inlet opening 30.
  • the soft iron anchor 55 moves in one of these bores in the interior of the armature housing 54; the other is the swirl chamber 43.
  • the housing 35 is embedded in an end wall 51 which is part of the burner housing.
  • a tank heater 50 is installed in the reservoir 31.
  • Air is brought in via an air line 41 via an annular air duct 36 with connecting piece 37 machined into the end wall 51.
  • the air line 41 also has a weight-loaded valve 38, with the help of which air is prevented from entering the combustion chamber through the swirl chamber 43 and cooling it down when the burner arrangement is switched off.
  • the air line 41 has a control valve 39, via which the air drawn in by an air compressor 40 is pressed into the air duct 36 at a pressure of approximately between 0.03 and 0.3 bar.
  • the air channel 36 ends in the openings 44, 44 ', which are incorporated into the jacket of this chamber for supplying the combustion air to the swirl chamber 43. They allow an air supply in which a vortex sinking flow (cyclone) is formed within the vortex chamber 43.
  • the inlet opening 30 for the fuel is arranged centrally on the front side of the chamber 43 in relation to this swirling iron flow forming in the chamber.
  • the jacket of the swirl chamber 43 has a cylindrical inner wall, a total of twelve rotationally symmetrically distributed openings (bores) 44 (or 44 ') being present.
  • the average distance between the opening openings is approximately 5 mm from the inlet opening 30, measured from a projection of the center of the openings 44 onto the axis of the swirl chamber 43.
  • the openings 44, 44 ' lie such that the air is guided into the swirl chamber 43 at an angle of 10-60 ° in deviation from the normal direction.
  • the air is accordingly blown tangentially to the periphery of a circle imagined within the swirl chamber 43.
  • the vortex chamber 43 is preferably designed such that it is of the same cross-section from the inlet opening 30 to the mouth.
  • the end wall 51 forms the end of a conventional boiler, which is equipped with the usual exchanger tubes (not shown) and side walls 52. Due to the good atomization, mixing and gasification and subsequent combustion with a short flame, there is no need to install a brick lining in the Hetzkessei; the Kesseiwand vom can be cooled. However, it is often useful to provide a cooling jacket in which the boiler water to be heated is preheated.
  • a jacket tube 63 is arranged, which has a much larger diameter than the diameter of the swirl chamber 43 and concentrically surrounds its opening.
  • the casing tube 63 can, for example, have a cylindrical shape or be designed to open or taper in the manner of a truncated cone. Other shapes are also possible.
  • the strong swirling iron flow which is caused within the swirl chamber 43 by the blowing in of the combustion and atomizing air, therefore continues in the direction of the casing tube 63 and ensures the establishment of a stable, concentrated flame.
  • the fuel jet does not exit droplet 30, i.e. sprays out, but in a compact jet with e.g. 1 mm diameter.
  • the oil consumption is in such an arrangement, which is operated under 75% full load, about 3-4 kg of oil per hour. Due to the turbulence and centrifugal forces that act within the vortex sinking flow, the jet inside and outside the vortex chamber 43 is fully captured and divided into fine droplets and then burned in the area of the casing tube 63. It should be noted that the droplet size is reduced to such an extent that a soot-free, essentially blue-flame combustion takes place.
  • an ignition coil 70 is provided in the burner arrangement according to FIGS. 1 and 2, which consists of an approximately 1 mm thick wire made of a heat-resistant, low-scaling chromium-nickel alloy.
  • the filament of the ignition coil 70 is disposed such that it is penetrated by the jet of uncombusted effluent Gem i- ULTRASONIC when flowing out of the swirl chamber 43, and this ignited at a natural temperature of about 700-900 ° C.
  • the ignition coil 70 is supplied with the energy for the annealing process via electrical leads.
  • a flame detector 46 is provided for monitoring the flame, via which a switch-off can take place if the flame is absent.
  • the inlet opening 30, through which the oil flows in has a diameter of 1-2 mm (depending on the embodiment, these values may also be exceeded and undershot), slight contaminations usually contained in the fuel do not lead to a blockage of the inlet opening, so that the Susceptibility to operation is low.
  • Test runs have shown that with a diameter of the inlet opening 30 between 1 and 2 mm and a pressure of the combustion air of 0.03 and 0.15 bar before the entry into the air channels within the swirl chamber 43, a vacuum can be generated which is sufficient for Suck fuel without additional pumps within line 32 and produce a compact jet of sufficient throughput (ie 2-3 kg of oil per hour).
  • Another control option is provided by the burner arrangement in that the float regulator 33 can be set differently so that the fuel supply can be regulated.
  • the diameter of the openings 44 and 44 'and the diameter of the inlet opening 30 must be coordinated.
  • twelve air channels 44 each with a 3 mm diameter Knives with an air pressure of between 0.03 and 0.3 bar are compatible with a diameter of the inlet opening 30 of 1 mm, whereby 2-3 kg of oil per hour (depending on the negative pressure) flow in at medium power.
  • the pressure difference caused by the level difference of the float regulator inlet opening corresponds to a fuel column between 0 and 30 mm.
  • the burner output can be regulated by adjusting the air supply through the air compressor 40, as a result of which the negative pressure in the swirl chamber 43 is variably set and the fuel supply through line 32 and inlet opening 30 is thus controlled. Numerous levels are possible between the full load and zero levels.
  • the openings 44 and 44 ' can also be opened and closed in a controllable manner by means of slides, screens and the like.
  • the burner is simply switched off by closing the inlet opening 30 by the needle 60. Accordingly, no complicated extinguishing and leakage regulations, as with atomizing nozzles, are required.
  • FIGS. 1 and 2 show embodiments in which a cylindrical guide sleeve 76 is provided within the jacket tube and concentric to the jacket tube 63 and is fastened to the end wall 51 via supports 77.
  • the fuel-air mixture emerging in vortices is partially drawn behind the guide sleeve into the intermediate space 78 between the sleeve and the casing tube 63 and drawn back into the mixture flow near the axis via peripherally distributed suction openings 79.
  • the direction of flow is indicated by the arrows.
  • the guide sleeve 76 is made of heat-resistant material. It can also have elongated holes for adjusting the sleeve in the axial direction, so that the sleeve can be fixed in different positions with respect to corresponding carriers, thereby specifying different clear widths of the suction openings 79.
  • the operating air pressure of the air compressor 40 can be significantly reduced. Measurements have shown that the air pressure requirement can be reduced to 50% of the air pressure with the same flame quality, which is possible without a guide sleeve.
  • the material of the guide sleeve 76 is preferably a ceramic, high-temperature-resistant, sintered or pressed fiber material made of Si-Al or Zr-carbides, as are known for example under the names REFRAX (manufacturer Carborundum) or FIBERFAX.
  • the jacket tube 63 of the burner extends beyond the guide sleeve 76 and has a constriction 83 in the protruding area 80.
  • This constriction in the form of a truncated cone, can, for example, reduce 5-20% of the largest diameter. so that only 95-80% of the original diameter - in certain cases even less - are available.

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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)

Claims (4)

1. Brûleur pour la combustion de combustibles liquides, avec une chambre à turbulence cylindrique (43) qui est fermée d'un côté par une paroi de fond et dont l'autre côté débouche dans une chambre de combustion, avec une ouverture ou des ouvertures (44, 44') pour l'introduction de l'air de combustion dans le corps de la chambre à turbulence (43), l'air de combustion étant introduit par les ouvertures (44, 44') et donnant naissance à un courant tourbillonnaire en dépression, et avec une chemise tubulaire cylindrique (63) qui est disposée à la suite de la chambre à turbulence (43) et s'ouvre du côté du foyer, caractérisé en ce que l'ouverture d'admission (30) du combustible est disposée -centralement par rapport à la paroi de fond de la chambre à turbulence (43), le combustible quittant l'ouverture d'admission (30) en un jet compact et en ce qu'un manchon de guidage (76) est incorporé dans la chemise tubulaire (63), ledit manchon comprenant des ouvertures d'aspiration (79) distribuées périphériquement du côté de ce manchon voisin de la chambre à turbulence.
2. Brûleur selon la revendication 1, caractérisé en ce que le manchon de guidage (76) est réglable axialement par rapport à la chemise tubulaire (63), le diamètre intérieur des ouvertures d'aspiration (79) étant simultanément réglé.
3. Brûleur selon la revendication 1, caractérisé en ce que la chemise tubulaire (63) s'étend au-delà dudit manchon de guidage (76) et comporte un rétrécissement (83) dans sa partie dépassante.
4. Brûleur selon la revendication 1, caractérisé en ce que la chemise de guidage (76) est réalisée par compression d'un matériau-fibre céramique réfractaire.
EP19790101956 1978-06-28 1979-06-15 Brûleur pour combustion de carburants liquides Expired EP0007424B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT79101956T ATE1870T1 (de) 1978-06-28 1979-06-15 Brenneranordnung zur verbrennung fluessiger brennstoffe.

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE2828319 1978-06-28
DE19782828319 DE2828319C2 (de) 1978-06-28 1978-06-28 Brenner für flüssigen Brennstoff mit einer zylindrischen Wirbelkammer
DE19792912101 DE2912101A1 (de) 1979-03-27 1979-03-27 Pumpenlose brenneranordnung mit nachgeschaltetem mantelrohr
DE19792912083 DE2912083A1 (de) 1979-03-27 1979-03-27 Brenneranordnung mit mantelrohr
DE2912083 1979-03-27
DE2912102 1979-03-27
DE2912101 1979-03-27
DE19792912102 DE2912102C2 (de) 1979-03-27 1979-03-27 Brenner für flüssigen Brennstoff

Publications (2)

Publication Number Publication Date
EP0007424A1 EP0007424A1 (fr) 1980-02-06
EP0007424B1 true EP0007424B1 (fr) 1982-11-24

Family

ID=27432319

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19790101956 Expired EP0007424B1 (fr) 1978-06-28 1979-06-15 Brûleur pour combustion de carburants liquides

Country Status (2)

Country Link
EP (1) EP0007424B1 (fr)
SU (1) SU1058521A3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3241730A1 (de) * 1982-11-11 1984-05-17 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5300 Bonn Vergasungsoelbrenner mit einer oelzerstaeubungsvorrichtung
DE102010000248A1 (de) * 2010-01-28 2011-08-18 Bundesanstalt für Materialforschung und -prüfung (BAM), 12205 Brenner für Peroxy-Brennstoffe und Ofen mit einem solchen Brenner
CN107228361B (zh) * 2017-07-06 2024-03-22 浙江明新能源科技有限公司 燃烧器辅助预热机构及燃烧装置

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1157333B (de) * 1951-07-10 1963-11-14 Lummus Co Verbrennungsvorrichtung fuer fluessige Brennstoffe
DE1133491B (de) * 1959-06-15 1962-07-19 Robert Von Linde Dipl Ing Niederdruck-Zerstaeubungsbrenner
NL261543A (fr) * 1960-11-18
DE1254279B (de) * 1962-11-23 1967-11-16 Erhard Schwarze OElbrenner
US3363661A (en) * 1965-12-07 1968-01-16 Fletcher Co H E Apparatus for producing a flame jet by combusting counter flow reactants
DE1526214B1 (de) * 1966-03-05 1970-05-27 Danfoss As Elektrische Zuend- und UEberwachungsvorrichtung fuer Flammen
US3826077A (en) * 1971-12-15 1974-07-30 Phillips Petroleum Co Method of introducing three streams of air into a combustor with selective heating
DE2517756A1 (de) * 1975-04-22 1976-11-04 Christian Coulon Verfahren und einrichtung zum zerstaeuben und verbrennen von fluessigen brennstoffen

Also Published As

Publication number Publication date
SU1058521A3 (ru) 1983-11-30
EP0007424A1 (fr) 1980-02-06

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