EP0007424A1 - Brûleur pour combustion de carburants liquides - Google Patents

Brûleur pour combustion de carburants liquides Download PDF

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Publication number
EP0007424A1
EP0007424A1 EP19790101956 EP79101956A EP0007424A1 EP 0007424 A1 EP0007424 A1 EP 0007424A1 EP 19790101956 EP19790101956 EP 19790101956 EP 79101956 A EP79101956 A EP 79101956A EP 0007424 A1 EP0007424 A1 EP 0007424A1
Authority
EP
European Patent Office
Prior art keywords
arrangement according
chamber
burner arrangement
fuel
air
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.)
Granted
Application number
EP19790101956
Other languages
German (de)
English (en)
Other versions
EP0007424B1 (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 method for operating a burner in the field of stoichiometric combustion, in which liquid fuel and combustion air are brought together in a substantially constant ratio in a mixing and atomizing chamber, a vacuum being able to be produced there due to the air guidance and metering, with the help of which fuel is sucked into said chamber.
  • the invention further relates to a burner arrangement for performing the method.
  • a burner construction is known (Niepenberg, Industrie- ⁇ lfeuerungen, Verlag Gustav Kopf & Co., Stuttgart, 2nd edition; 1973), in which a two-stage air supply to the oil is used.
  • the oil gets into the central air flow at a point with negative pressure by using an injector construction, so it is sucked in through the air.
  • the amount of oil drawn in can be varied at the same time with the amount of air supplied.
  • the ratio of oil to air can also be kept constant over a certain burner control range.
  • a negative pressure is generated by the air duct, in the area of which the sucked-in fuel is let in.
  • the fuel must be introduced via an injector design. Due to the high air speed in the area The combustion path extends relatively long at the nozzle mouth, while in many cases the flame should be relatively short.
  • Cyclone is to be understood here to mean an air movement that is circular, with a slight air compression towards the edge of the mixing chamber due to the centrifugal forces. This air flow surprisingly results in a negative pressure inside the cyclone, which can be used to suck in the fuel. The burner therefore does not require a fuel pump. All that is required is that the fuel is introduced in the area of the cyclone's axis, since experience has shown that the negative pressure reaches its maximum value here.
  • the fuel introduced which can preferably be supplied in a compact jet, but can also be atomized slightly, is immediately torn apart by the turbulence within the air movement and divided into very fine particles and burned soot-free at the appropriate temperature conditions. It is advantageous if the fuel is supplied essentially as a compact jet with a jet diameter of 0.5 to 2.0 mm.
  • the negative pressure that can be generated in the mixing and atomizing chamber in the area of the nozzle inlet is between - 0.03 and - 0.15 bar.
  • Standard combustion in the sense of the invention is understood to mean one in which neither soot (measured according to BACHARRACH: soot number 0) nor a significant proportion of oxygen in the combustion gases occurs (oxygen content in the order of 0.01 to 0.1%).
  • the combustion process can also be carried out under or above stoichiometry without soot formation.
  • heating oils can be heating oils EL, L or S.
  • the corresponding viscosity values are defined in accordance with DIN. In the case of oils, the viscosity drops sharply with heating, so that u. U. from a heavy heating oil can be heated by heating with viscosity properties of a medium-heavy heating oil.
  • other substances such as alcohols, low-boiling aliphatics or aromatics are also suitable for combustion.
  • 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.
  • Another important advantage is that the fuel particles are completely homogeneously mixed with the air and thus a very short burnout time is achieved.
  • the method according to the invention further enables combustion to be carried out stoichiometrically over wide load ranges.
  • the control of the power can be carried out simply by changing the amount of combustion air supplied by controlling the drive line of the associated fan. The method can therefore be based on a very simple control option.
  • the burner arrangement for carrying out the method has an inlet opening, which is followed by a mixing and atomizing chamber enclosed by a jacket, into which the fuel jet passes. It also has at least one opening through which the combustion air can be fed to the mixing and atomizing chamber.
  • the burner arrangement according to the invention differs from the prior art in that the opening or openings for supplying the combustion air are incorporated into the jacket of the mixing and atomizing chamber and permit air guidance in which a cyclone is formed within the mixing and atomizing chamber and that the inlet opening for the fuel is arranged centrally on the end face of the chamber.
  • the air flow for generating a cyclone is made possible by the fact that the supply openings are cut obliquely, so that a supply air flow occurs tangentially to an imaginary circle within the mixing chamber and rotates the contents of the mixing chamber.
  • the inlet opening for the fuel is arranged "centrally"; This choice of words also means that it is possible to deviate from the exact central 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 able to maintain the highest possible flow rate.
  • the jacket of the mixing and atomizing chamber preferably has a cylindrical inner wall, in which individual bores or slots are provided as openings distributed over the circumference and length, with three to twenty, preferably twelve bores or slots being distributed over the circumference of the jacket in a rotationally symmetrical arrangement .
  • the mixing and atomizing chamber either opens directly into the room to be heated in a boiler or into a room surrounded by a burner jacket Room. In both cases it has proven to be advantageous if the clear width of the mixing and atomizing chamber from the fuel nozzles or from the fuel nozzle to the transition into the combustion chamber is of the same cross-section. Since the fuel is not atomized, but is preferably fed in in a compact jet, it is not under too high a pressure. It can be switched on and off in a simple manner by means of an electrically operated valve needle that closes and opens the inlet opening.
  • the burner arrangement described is primarily suitable for being used for household burners which have only low fuel oil consumption.
  • so-called mini-burners are required for single-family houses, which have an oil consumption of the order of 1-3 kg of oil per hour.
  • a burner based on the principle of master registration must be built that works.
  • the burner system becomes more expensive, the operation more complicated and in particular, it is more difficult to re-ignite after a failed attempt to start if a burner is provided with such an arrangement for regulating the starting air.
  • Another disadvantage is that a failed start attempt, if this is not due to a lack of fuel, also releases a large amount of soot and cracked products that can heavily contaminate the combustion chamber.
  • This object is achieved in that in the area of the MZK there is a heatable incandescent body in the flow of the unburned fuel-air mixture.
  • incandescent body which is preferably designed as a wire coil or ignition coil
  • the mixture can sweep past such a body, the combustion reaction starting immediately when fuel is added to the air. Misfires are practically not observed at all.
  • incandescent bodies are particularly well suited as igniters since they emit a large amount of heat to the fuel-air mixture in a relatively small area can be transmitted locally so that combustion is reliably initiated.
  • the MZK is preferably designed so that it has the same cross-section from start to finish.
  • One forehead side is delimited by the end wall, in which the inlet or openings for the fuel jet are also located.
  • the opening of the MZK is partially framed by the incandescent body.
  • the incandescent body is generally attached in such a way that it is penetrated as intensely as possible by the mixture jet emerging turbulently from the MZK without being completely in the core or in the axis of this jet. It is advantageous to mount it adjacent to the opening edge of the MZK, since it is known that tear-off vortices form at the edge. If the edge is rounded off so that the path of the flow is carried out from the axial direction due to the Coanda effect, this flow formation can also be easily adapted to the attachment of the filament. With such a rounded edge, a flame cone is formed with an opening angle between 90 and 180 °. It is proposed that in this case the incandescent body nestles against the end wall or is fitted into a groove.
  • the incandescent body or the ignition coil is located in the relatively cool area of the burner arrangement that is in operation between the MZK and the flame front. This ensures that the mixture coming out of the MZK comes into good contact with the incandescent body located at the opening. After initiating the ignition process and switching off the heating current, the incandescent body lies then practically outside the flame front and is only moderately heated so that it has a long service life.
  • the incandescent body is preferably made of ceramic or a low-ignition alloy, so that it cannot or hardly can be scaled.
  • the shape of the filament can be very different. It should be able to be warmed up quickly and have a good heat-emitting surface. Ceramic, cone-shaped incandescent bodies with an internal heating coil, electrically heated tapes or filaments or even platelets can be used. Strangely enough, a relatively small area is sufficient if it can be kept at a temperature of approximately 800 ° C. continuously during the ignition process.
  • the heating can of course also be done by induction, HF heating or related processes.
  • this object can be achieved in that flow-directing elements flow into the jacket tube be installed, which cause a circulating circulation of the burning mixture flow directed from the axis.
  • the fan pressure can thus be significantly reduced, which in addition to the energy consumption also significantly reduces the noise pollution caused by the airflow noise.
  • Such a large reduction in effort through relatively simple installations is not to be expected for the present case. Rather, from a plausibility assessment, it can only be expected that the main energy of the air flow will be used to generate the cyclone and to overcome the air friction in the supply lines and in the openings that lead to the MZK.
  • Another effect that is achieved is that larger oil droplets, which we more in the outer region of the swirling Strombe- due to centrifugal force are un g g, can be recycled again and thus travel a longer distance, so that they fully can evaporate more and more.
  • 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 so as to be adjustable relative to the end wall of the combustion chamber, with the adjustment also being able to change the light way of the intake 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 operation of the burner described shows the phenomenon that a relatively large amount of heat is transferred to the surroundings of the MZK through the jacket tube. Obviously due to this heating, the fuel flow through the inlet opening can decrease after prolonged operation, so that the performance of the burner arrangement drops.
  • the oxygen content can also drop from initially 1% to 5%, for example.
  • the fuel usually heating oil EL with a viscosity of approximately 5 cSt at 20 ° C.
  • the fuel is fed from a storage container 31 to the actual burner via a line 32.
  • a float regulator 33 is located between the storage container and the burner installed, which ensures a constant pressure between the burner fuel inlet and the level of the float regulator 33. 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 housing 54.
  • the armature runs out on the side facing away from the coil 56 into a valve needle 60, which opens and closes a further bore 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 bore 30.
  • the soft iron core 55 moves in one of these bores in the interior of the armature housing 54; the other is the mixing and atomizing chamber 43 (MZK).
  • 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. This can be heated either via a separate circuit or via heat exchange with the central boiler exchanger. Of course, such additional heating can also be omitted if appropriate operating conditions are present.
  • Air is brought in via an air line via an annular air duct 36 with connecting piece 37 machined into the end wall 51.
  • the channel owns and a weighted valve 38 which prevents air from entering the combustion chamber through the conduit and cooling it when the burner assembly is turned off.
  • the supply air line also 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 air channels 44, which are incorporated into the jacket of this chamber for supplying the combustion air to the mixing and atomizing chamber 43. They allow an air supply in which a vortex-shaped air movement (cyclone) is formed within the chamber 43. To do this in the chamber. forming cyclone is the inlet opening for the fuel, d. H. the bore 30, arranged centrally on the end face of the chamber.
  • a vortex-shaped air movement cyclone
  • the casing of the chamber 43 has a cylindrical inner wall, a total of 12 rotationally symmetrically distributed air channels (bores) 44 being present.
  • the air channels 44 lie so that the air is guided into the mixing chamber at an angle of 10 to 60 ° in deviation from the normal direction.
  • the air is accordingly blown tangentially to the periphery of a circle imagined within the mixing chamber 43, as can be seen from FIG. 3.
  • the mixing chamber 43 is preferably designed in such a way that it has the same cross-section from the nozzle 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 boiler; the boiler wall surfaces can be cooled. However, it is often useful to provide a cooling jacket in which the boiler water to be heated is preheated. It is also preferably provided that a burner jacket 63 is arranged on the inside of the end wall, which has a substantially larger diameter than the diameter of the mixing and atomizing chamber and concentrically surrounds its opening.
  • the burner jacket 63 can, for example, have a cylindrical shape or a frustoconical opening or taper. Other shapes are also possible.
  • the strong vortex movement (cyclone), which is caused within the mixing chamber by blowing in the combustion and atomizing air, therefore continues in the direction of the burner jacket 63 and ensures the establishment of a stable, concentrated flame.
  • the fuel jet 45 (see FIG. 3) does not emerge from the outlet opening 30 in droplet form, ie sprayed out, but initially in a compact jet with a diameter of 1 mm, for example. With such an arrangement, the oil consumption is below 75% full load is driven, about 3 to 4 kg of oil per hour. Due to the turbulence and centrifugal forces that act within the cyclone, the jet inside and outside the mixing chamber is fully captured, divided into fine droplets and then burned in the area of the burner jacket. 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 device 47 known per se is provided, which generates a high-voltage ignition spark between two electrodes.
  • the electrode necks are passed through a corresponding bore within the end wall 51.
  • a flame detector 46 is provided for monitoring the flame, via which a switch-off can take place if the flame is absent.
  • the bore 30, through which the oil flows has a diameter of 1-2 mm (depending on the embodiment, this value may also be exceeded or fallen short of), minor contaminations usually contained in the fuel do not lead to a blockage of the inlet opening, so that the vulnerability is significantly reduced.
  • Test runs have shown that with a diameter of the bore 30 between 1 and 2 mm and a pressure of the atomizing air of 0.03 and 0.15 bar before the entry into the air channels within the mixing chamber 43, a vacuum can be generated which is sufficient, the fuel - Heating oil EL - without sucking in additional pumps within line 32 and generating a compact jet of sufficient throughput (ie 2-3 kg of oil per hour).
  • the Brenneran has another control option order in that the float regulator 33 can be adjusted differently so that the fuel supply can be regulated.
  • the diameter of the air channels 44 and 49 and the diameter of the bore 30 must be coordinated.
  • twelve air channels 44 each with a diameter of 3 mm, in front of which an air pressure of between 0.03 and 0.3 bar is present, are compatible with a diameter of the bore 30 of 1 mm in diameter, 2-3 kg of oil per Flow in hour (depending on the vacuum) at medium power.
  • the pressure difference caused by the level difference between float regulator and fuel inlet corresponds to a fuel column between 0 and 30 mm.
  • the burner output can be regulated by adjusting the air supply through the compressor 40, as a result of which the negative pressure in the mixing chamber is variably set and the fuel supply through line 32 and bore 30 is thus controlled. Numerous levels are possible between the full load and zero levels.
  • the bores 44 and 49 can also be opened and closed in a controllable manner by means of slides, diaphragms and the like.
  • the burner is simply switched off by closing the bore 30 by the needle 60. It No complicated extinguishing and leakage regulations, as with atomizing nozzles, are required.
  • Figures 2, 3 show individual parts of the magnetic control in a somewhat enlarged form.
  • the following dimensions are selected, for example: diameter of the chamber 43: 15 mm, diameter of the feed channels 44: 3 mm, diameter of the fuel inlet 30: 1 mm, length of the chamber: 11 mm.
  • the ratio of length to diameter of chamber 43 should be about 0.5: 1 to 1: 0.5.
  • these dimensional examples are to be considered without restriction. They only serve to substantiate the economic use of the invention.
  • the fuel line 32 ends in an inner line 34, which is connected to a closable further bore 30 '.
  • the closure bore 30 ' can be opened and closed using the controllable valve needle 60.
  • the further details of the locking mechanism are similar to that of Fig. 1 and need not be discussed here.
  • the liquid fuel enters the mixing and atomization chamber 43 from the inlet opening 30, which chamber is surrounded by a cylindrical jacket, in which two rings of air channels 44, 44 ′ end one behind the other in the axial direction.
  • the channels are preferably about 3 and 8 mm away from the outlet opening of the bore 30, measured from a projection of the center of the bores 44, 44 ′ onto the axis of the chamber 43.
  • an ignition coil 70 is provided in the burner according to FIGS. 4 and 5, 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 is arranged in such a way that it is penetrated by the jet of the unburned mixture as it flows out of the chamber 43 and ignites it at an intrinsic temperature of approximately 700-900 ° C.
  • the ignition coil 70 is supplied with the energy for the annealing process via electrical leads 71.
  • the filament is preferably wound in the form of a helix or screw; however, other configurations are also conceivable, for example a zigzag bend or a flat glow band. Surprisingly, it has been shown that the use of the filament enables the driver to run with a very lean, practically stoichiometric fuel-air mixture right from the start. It is therefore not necessary to first reduce the amount of air by means of a movable flap and then to increase it again after the ignition.
  • the coil is switched off again. It is arranged in such a way that it lies in the area between opening plane 73 and flame front, that is to say in a relatively cool area, which considerably increases its service life.
  • the distance from the edge of the MZK is approximately between 5 and 40 mm.
  • the distance from the opening plane 73 or end wall 51 is approximately between 5 and 30 mm.
  • an ionization sensor 74 is provided, with which it is continuously monitored whether combustion takes place within the burner jacket or not.
  • FIG. 5 shows a view into the cut burner jacket 63.
  • the ignition coil 70 is arranged with the axis of the mixing and atomizing chamber lying horizontally in such a way that it is attached below the opening of the chamber 43 and is only a relatively short distance from the opening of the chamber 43 in the form of an arc segment.
  • the ignition body or the ignition coil can also assume a different position, since it is absolutely not necessary to arrange the incandescent body below the MZK.
  • the coil fulfills the requirement that the vortices emerging from the chamber 43 penetrate as large a space as possible, which is occupied by the coil 70, and thus initiate the ignition safely and reliably.
  • the edge 75 of the MZK is rounded outwards so that the path of the flow is partially pulled out of the axis direction due to the Coanda effect. In this way, a very widely spread flame cone can be generated, the opening angle of which is between 90 and 180 °.
  • the incandescent body in particular an ignition coil, should conform to the end wall 51 or be fitted into a groove.
  • FIGS. 6 and 7 A further exemplary embodiment of a burner arrangement is shown in FIGS. 6 and 7.
  • the fuel usually heating oil EL with a viscosity of about 5 cSt at 20 ° C, is supplied from the reservoir 31 via line 3 & the actual burner. Further details have already been described.
  • the casing tube 63 according to FIGS. 6 and 7 is provided in its last third with three times four slots 80, which extend in the circumferential direction lie and overlap slightly each.
  • the slots have a width of approximately 1 mm and each have a length of slightly less than a quarter of the circumferential length of the casing tube 63.
  • beads 81 are pressed into the casing tube, which increase the strength.
  • the slots can also be shifted more towards the center of the casing tube - seen in the axial direction.
  • the flow of hot combustion gases and flame shape are preferably taken into account so that the slots are in front of the hot gas impact area, as seen from the mixing and atomizing chamber.
  • a Z is ündspirale provided which is penetrated by the jet of uncombusted effluent mixture as it flows out of the chamber 43, and this at a natural temperature of 700 - 900 ° C ignites. It has been shown that the use of a glow wire makes it possible to run a very lean, practically stoichiometric fuel-air mixture right from the start.
  • FIG. 1 A further embodiment variant is provided in FIG.
  • a cylindrical guide sleeve 76 is provided inside and concentric to the burner jacket 63, which is fastened to the end wall 73 via supports 77.
  • the fuel-air mixture escaping in vortices is partially drawn behind the guide sleeve into the intermediate space 78 between the sleeve and the burner jacket 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 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 fan can surprisingly be significantly reduced. Measurements have shown that the air pressure requirement can be reduced to 50% of the air pressure without the same flame quality flow-conducting elements is possible.
  • the material of the guide elements or the guide sleeve is preferably a ceramic, highly heat-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 burner jacket of the burner projects beyond the guide sleeve and has a constriction 83 in the protruding area 82.
  • This constriction in the form of a truncated cone, can, for example, reduce 5-20% of the largest diameter, so that accordingly only 95-80% of the original diameter - in certain cases also. 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)
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
DE19782828319 DE2828319C2 (de) 1978-06-28 1978-06-28 Brenner für flüssigen Brennstoff mit einer zylindrischen Wirbelkammer
DE2828319 1978-06-28
DE19792912101 DE2912101A1 (de) 1979-03-27 1979-03-27 Pumpenlose brenneranordnung mit nachgeschaltetem mantelrohr
DE2912101 1979-03-27
DE19792912083 DE2912083A1 (de) 1979-03-27 1979-03-27 Brenneranordnung mit mantelrohr
DE2912083 1979-03-27
DE19792912102 DE2912102C2 (de) 1979-03-27 1979-03-27 Brenner für flüssigen Brennstoff
DE2912102 1979-03-27

Publications (2)

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

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EP19790101956 Expired EP0007424B1 (fr) 1978-06-28 1979-06-15 Brûleur pour combustion de carburants liquides

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0109585A1 (fr) * 1982-11-11 1984-05-30 DEUTSCHE FORSCHUNGSANSTALT FÜR LUFT- UND RAUMFAHRT e.V. Brûleur à mazout à vaporisation avec un dispositif de pulvérisation de mazout
WO2011091872A3 (fr) * 2010-01-28 2013-04-11 Bundesanstalt für Materialforschung und -Prüfung (BAM) Brûleur pour combustibles péroxy et four doté d'un tel brûleur
CN107228361A (zh) * 2017-07-06 2017-10-03 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

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1133491B (de) * 1959-06-15 1962-07-19 Robert Von Linde Dipl Ing Niederdruck-Zerstaeubungsbrenner
DE1157333B (de) * 1951-07-10 1963-11-14 Lummus Co Verbrennungsvorrichtung fuer fluessige Brennstoffe
DE1242784B (de) * 1960-11-18 1967-06-22 Gulf Oil Deutschland G M B H Zerstaeuberbrenner fuer fluessige Brennstoffe mit Brennstoffzerstaeubung und -ansaugung durch Verbrennungsluft
AT255625B (de) * 1962-11-23 1967-07-10 Otto Goldmann Ölvergasungsbrenner
US3363661A (en) * 1965-12-07 1968-01-16 Fletcher Co H E Apparatus for producing a flame jet by combusting counter flow reactants
US3432246A (en) * 1966-03-05 1969-03-11 Danfoss As Electrical flame ignition and supervising apparatus
DE2261596A1 (de) * 1971-12-15 1973-06-28 Phillips Petroleum Co Brennkammer und verfahren zum verbrennen eines brennstoffes in dieser brennkammer
DE2517756A1 (de) * 1975-04-22 1976-11-04 Christian Coulon Verfahren und einrichtung zum zerstaeuben und verbrennen von fluessigen brennstoffen

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US3363661A (en) * 1965-12-07 1968-01-16 Fletcher Co H E Apparatus for producing a flame jet by combusting counter flow reactants
US3432246A (en) * 1966-03-05 1969-03-11 Danfoss As Electrical flame ignition and supervising apparatus
DE2261596A1 (de) * 1971-12-15 1973-06-28 Phillips Petroleum Co Brennkammer und verfahren zum verbrennen eines brennstoffes in dieser brennkammer
DE2517756A1 (de) * 1975-04-22 1976-11-04 Christian Coulon Verfahren und einrichtung zum zerstaeuben und verbrennen von fluessigen brennstoffen

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0109585A1 (fr) * 1982-11-11 1984-05-30 DEUTSCHE FORSCHUNGSANSTALT FÜR LUFT- UND RAUMFAHRT e.V. Brûleur à mazout à vaporisation avec un dispositif de pulvérisation de mazout
WO2011091872A3 (fr) * 2010-01-28 2013-04-11 Bundesanstalt für Materialforschung und -Prüfung (BAM) Brûleur pour combustibles péroxy et four doté d'un tel brûleur
CN107228361A (zh) * 2017-07-06 2017-10-03 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
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

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SU1058521A3 (ru) 1983-11-30

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