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
  • F23D11/001—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space spraying nozzle combined with forced draft fan in one unit
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
  • F23C7/00—Combustion apparatus characterised by arrangements for air supply
  • F23C7/02—Disposition of air supply not passing through burner
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
  • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
  • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
  • F23C9/006—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber the recirculation taking place in the combustion chamber
• • 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
  • F23D11/102—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 in an internal mixing chamber
  • F23D11/103—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 in an internal mixing chamber with means creating a swirl inside the mixing chamber
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
  • F23K5/00—Feeding or distributing other fuel to combustion apparatus
  • F23K5/02—Liquid fuel
  • F23K5/04—Feeding or distributing systems using pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23K—FEEDING FUEL TO COMBUSTION APPARATUS
  • F23K5/00—Feeding or distributing other fuel to combustion apparatus
  • F23K5/02—Liquid fuel
  • F23K5/14—Details thereof
  • F23K5/18—Cleaning or purging devices, e.g. filters

Definitions

• the present invention relates to a device for the evaporation of fuels, in which the air used for the evaporation simultaneously represents part of the combustion air, an ultra-fine particle size causing faster evaporation and thus better combustion and thus the undesired residues, especially the NOx, are limited, in order to support the reduction of the residues, add secondary combustion air, perpendicular to the flame axis, to this.
• the heating oils include Chlorine and sulfur, the higher the proportion of sulfur, the heavier the heating oil and can reach 3.5% by weight.
• the main problem with the current heating systems is the particle size of the atomized heating oil, which is 80% between 40 and 80 microns using an atomizing pressure of approx. 15 bar.
• a good combustion is particularly problematic in industrial oil burners because the droplet size of the heavy heating oils used in the known mechanical atomizing nozzles, even at high pressure, more than 20 bar, reach a particle size of at least 60 microns. In addition, very small nozzle openings are required, diameter approx. 0.15 mm, which easily clog and lead to breakdowns.
• the heavy heating oils In order to reduce the viscosity of the heavy heating oils, it is heated from 50 ° C. to 100 ° C., which affects the particle size, but not enough to bring about maximum combustion, quite apart from the fact that heating the heating oil consumes large amounts of energy.
• the present invention has for its object to evaporate and instead of atomize the fuel to use air necessary for evaporation as part of the combustion air.
• this object is achieved by a device for the evaporation of fuels and the supply of combustion air, as defined in claim 1.
• FIG. 1 shows a sectional view of a two-substance nozzle according to the invention
• FIG. 2 shows a sectional view along the sectional plane A - A of FIG. 1 of a nozzle core
• FIG. 3 shows a sectional view along the sectional plane A - A of FIG. 1 4 shows a sectional view of a nozzle sleeve according to FIG. 1
• FIG. 5 shows a sectional view of another embodiment of a two-component nozzle according to the invention
• FIG. 6 shows a sectional view along the sectional plane BB of FIG. 5 of the nozzle sleeve
• FIG. 7 shows a sectional view along 5 of the nozzle core
• FIG. 8 a schematic illustration of the functional principle of the device according to the invention
• FIG. 9 a plan view, partly in section of an extremely advantageous embodiment of the device according to the invention
• FIG. 10 a schematic Front view of the device according to FIG. 9, the distribution of the Secondary combustion air and any
• the device according to the invention is based on a device for atomizing liquids with the addition of compressed gas, which has a SAUTER-mean particle size of 21.08 microns with a pressure of only 1 bar.
• the particle size can be significantly reduced, so that one can speak of evaporation.
• This evaporation is the basis of the device according to the invention and ensures optimal combustion.
• nozzle sleeve 1 shows a nozzle sleeve 1, in which a nozzle core 2 is mounted, which has a mixing chamber 3, into which bores 4 lying parallel to the core axis and compressed air and via feed channels 5 and tangential channels 6 (see also Fig. 2) pressurized heating oil flows in, so that the heating oil and the compressed air can mix there.
• the nozzle sleeve 1 has an expansion chamber 7, a compression chamber 8 and a nozzle channel 9.
• the depth of the expansion chamber 7 and the compression chamber 8 determine the length of the nozzle channel 9, a short nozzle channel 9 giving off a wider cone than a long one .
• 4 also shows a conical nozzle channel 10 which emits an even wider cone than an equally long but cylindrical nozzle channel 9.
• the diameters of the nozzle channels 9 and 10 determine the amount of heating oil output per unit of time: at constant pressure, this is small with a small pressure Diameter, where but the diameters of the nozzle channels 9 and 10 are not less than 0.30 mm and, since they can be cleaned with the evaporation air, they remain constant throughout.
• the feed channels 5 of the nozzle core 2 open into the tangential channels 6, which open into the mixing chamber 3, so that a heating oil coming from the feed channels 5 and the tangential channels 6 is pushed into the mixing chamber 3 in such a way that it rotates along the wall thereof Movement is set into which the compressed air is pressed in vertically through the bore 4, after which it can relax after a first compression phase in the mixing chamber 3 in the expansion chamber 7, and then is compressed in the heating oil in the compression chamber 8 to become.
• FIG. 5 shows another embodiment of a nozzle unit, consisting of a nozzle sleeve 11 and a nozzle core 12, which is used especially for fuels, in which the nozzle unit has to be precisely adapted to the viscosity of the heating oil, such as, for example, with heavy heating oils.
• the nozzle unit of FIG. 1 had to be adapted to a viscosity of more than 10 centipoises, the changes would have to be made both to the feed channels 5, the tangential channels 6 and the mixing chamber 3 of the nozzle core 2, and to the expansion chamber 7 of the nozzle sleeve 1 done.
• the modifications are simpler in the embodiment according to FIG. 5.
• the feed channels 13 and the tangential channels 14 lie in the nozzle sleeve 11, the tangential channels 14 opening into the compression chamber 15, which has the nozzle channel 16.
• the air is guided through bores 18 into the mixing chamber 17, which is connected to the compression chamber 15. If you want to adapt this nozzle unit to a higher viscosity, it is sufficient to keep the mixing chamber 17 of the nozzle core 12 deeper and to enlarge the diameter of the bores.
• a cover 20 In the pressure vessel 19 there is a float 23 with a needle 24.
• the cover 20 is provided with a pressure relief valve 25 and an air outlet 26.
• a heating oil, not shown, is conveyed into the pressure container 19 by means of a pump 30, while the compressor 21 the pressure vessel 19 sets under air pressure, the level of the pressure being adjustable with the pressure relief valve 25.
• the nozzle sleeve 1 (11) with the nozzle core 2 (12) is located in a distributor block 31. This is supplied with compressed air via the air outlet 26 and a solenoid valve 32, the volume of which can be regulated with a needle valve.
• the heating oil under identical pressure as the air, is pressed into the distributor block 31 via the heating oil outlet 829 and a solenoid valve 34, the heating oil volume being adjustable by means of a needle valve 35.
• the distributor block 31 carries a combustion hollow cylinder 36 which is provided with a sieve 37 in the direction of escape of the nozzle axis and has side holes 38 which can be more or less closed with a slide 39. Secondary combustion air coming from a blower 40 can be blown through these side holes 38 into the hollow cylinder 36 and thus into the evaporated heating oil which has already been enriched with primary combustion air.
• the pressure relief valve 25 can consist of a membrane, which is raised by means of a magnetic core in an electrical coil under a preset current and allows excess pressure to escape, such an embodiment being provided with a potentiometer which controls the current of the coil , makes the setting of the pressure level much easier, since it only requires a change in the current in the coil in order to increase or decrease the resistance of the membrane to the pressure.
• a major advantage of this solution is that the amount of heating oil per unit time can be adjusted continuously by means of the pressure in the pressure vessel 19 without significantly changing the particle size.
• the particle size becomes smaller by approx. 0.5 micron at pressures between 1 and 4 bar, whereas the output quantity increases at these pressure values from 0.5 kg to approx. 1.1 kg / hour. Thanks to this possibility, the hourly consumption can be infinitely modulated to suit the weather conditions, for example by means of an external thermostat, so that the duration of combustion can be adjusted as required Increase in the amount of combustion per unit time can shorten, which is done automatically thanks to an electronic circuit.
• FIG. 9 shows, without taking any scale into account, an extremely advantageous embodiment of the device according to the invention.
• the main difference compared to the device in FIG. 8 is that the hollow cylinder 36 is replaced with, in this embodiment, nine tubes 41, the free ends 42 of which are closed.
• the tubes 41 have bores 43 and a blower 44 fills the tubes 41 with compressed air, which is blown through the bores 43 into a flame, not shown.
• a thread 45 with which the tubes 41 are screwed into a distributor plate 46 and blocked by means of nuts 47, it is possible to set the blowing direction of the bores 43 as desired, ie the air coming from the blower 44 can both be blown into the axis of the flame, as well as more or less tangential to it, in order to specifically control a swirl. You can also achieve a mixture of axis blowing direction and tangential blowing direction. Furthermore, the bores 43 of one tube 41 can be made offset to those of another tube 41.
• FIG. 9 shows two different possibilities.
• the housing 49 of the fan 44 has openings 50 which are shielded from the outside air by means of a sleeve 51.
• the fan sucks in exhaust gases via a double-walled hollow cylinder 52 and openings 50, which the fan 44, together with the outside air sucked in by it, who blows over the tubes 41 into the flame, not shown.
• the advantage is that the cold outside air coming from the blower 44 is heated in the tubes 41 and therefore the flame cannot cool down, so that insufficient combustion due to cooling of the flame and thus reducing the heat evaporation of the heating oil is avoided.
• the flame can be shortened so that the volume of the boiler can be kept small, which increases the efficiency of the heating, all the more so as the ultra-fine heating oil particles produced by the nozzle 1 according to the invention burn very quickly and do not have to be kept floating by means of an oversized volume of the secondary combustion air, as described.
• the diameter of the nozzle channels 9 and 16 is at least 0.4 mm, that is to say can practically never clog, if only because the nozzle 1 (11) is blown through before and after the combustion process.
• their cross sections are approximately 7 times larger than those of the mechanical atomizing nozzles, the hourly consumption quantity can be kept at 0.5 kg and, as described, can be increased continuously with only an increase in the air pressure in the pressure container 19 can be increased to 1.1kg.

Landscapes

• 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)
• Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)

Applications Claiming Priority (3)

Publications (2)

Family

ID=4188751

Family Applications (1)

Country Status (9)

Cited By (1)

Families Citing this family (5)

Family Cites Families (10)

• 1994
  • 1994-02-17 AT AT94905823T patent/ATE161939T1/de not_active IP Right Cessation
  • 1994-02-17 JP JP6518788A patent/JPH08506887A/ja active Pending
  • 1994-02-17 WO PCT/IB1994/000015 patent/WO1994019648A1/fr active IP Right Grant
  • 1994-02-17 AU AU59781/94A patent/AU5978194A/en not_active Abandoned
  • 1994-02-17 DE DE59404953T patent/DE59404953D1/de not_active Expired - Fee Related
  • 1994-02-17 EP EP94905823A patent/EP0683882B1/fr not_active Expired - Lifetime
  • 1994-02-17 HU HU9502439A patent/HUT74194A/hu unknown
  • 1994-02-17 CA CA002156248A patent/CA2156248A1/fr not_active Abandoned
  • 1994-02-17 US US08/507,254 patent/US5743726A/en not_active Expired - Fee Related

Non-Patent Citations (1)

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