EP0794383A2 - Buse de pulvérisation par pression - Google Patents

Buse de pulvérisation par pression Download PDF

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Publication number
EP0794383A2
EP0794383A2 EP97810083A EP97810083A EP0794383A2 EP 0794383 A2 EP0794383 A2 EP 0794383A2 EP 97810083 A EP97810083 A EP 97810083A EP 97810083 A EP97810083 A EP 97810083A EP 0794383 A2 EP0794383 A2 EP 0794383A2
Authority
EP
European Patent Office
Prior art keywords
swirl
liquid
nozzle
tube
chamber
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
EP97810083A
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German (de)
English (en)
Other versions
EP0794383A3 (fr
EP0794383B1 (fr
Inventor
Klaus Dr. Döbbeling
Peter Dr. Jansohn
Hans Peter Knöpfel
Christian Dr. Steinbach
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General Electric Switzerland GmbH
Original Assignee
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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Filing date
Publication date
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Publication of EP0794383A2 publication Critical patent/EP0794383A2/fr
Publication of EP0794383A3 publication Critical patent/EP0794383A3/fr
Application granted granted Critical
Publication of EP0794383B1 publication Critical patent/EP0794383B1/fr
Anticipated expiration legal-status Critical
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3478—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet the liquid flowing at least two different courses before reaching the swirl chamber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3421—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber
    • B05B1/3431—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves
    • B05B1/3442—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves the interface being a cone having the same axis as the outlet
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
    • B05B7/02—Spray pistols; Apparatus for discharge
    • B05B7/04—Spray pistols; Apparatus for discharge with arrangements for mixing liquids or other fluent materials before discharge
    • B05B7/0408—Spray pistols; Apparatus for discharge with arrangements for mixing liquids or other fluent materials before discharge with arrangements for mixing two or more liquids
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B7/00—Spraying apparatus for discharge of liquids or other fluent materials from two or more sources, e.g. of liquid and air, of powder and gas
    • B05B7/02—Spray pistols; Apparatus for discharge
    • B05B7/10—Spray pistols; Apparatus for discharge producing a swirling discharge
    • 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
    • F23C7/002—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning 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
    • F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space
    • F23D11/26—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space with provision for varying the rate at which the fuel is sprayed
    • 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
    • F23D11/38—Nozzles; Cleaning devices therefor
    • F23D11/383—Nozzles; Cleaning devices therefor with swirl means
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3421—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber
    • B05B1/3431—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves
    • B05B1/3447—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels being formed at the interface of cooperating elements, e.g. by means of grooves the interface being a cylinder having the same axis as the outlet
    • 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 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/07002—Premix burners with air inlet slots obtained between offset curved wall surfaces, e.g. double cone burners

Definitions

  • the invention relates to the field of combustion technology. It relates to a pressure atomizing nozzle, comprising a nozzle body, in which a turbulence or swirl chamber is formed, which is connected to an outside space via a nozzle bore and has at least one supply channel for the liquid to be atomized, through which said liquid can be supplied under pressure, and a method of operating this pressure atomizing nozzle.
  • Atomizer burners are known in which the oil which is burned is finely divided mechanically. It is broken down into fine droplets of approximately 10 to 400 ⁇ m in diameter (oil mist), which evaporate and burn in the flame when mixed with the combustion air.
  • pressure atomizers see Lueger - Lexikon dertechnik, Manual Verlags-Anstalt Stuttgart, 1965, Volume 7, p.600
  • the oil is supplied to an atomizer nozzle under high pressure by an oil pump.
  • the oil enters a swirl chamber via essentially tangential slots and leaves the nozzle via a nozzle bore. It is thereby achieved that the oil particles receive two components of motion, an axial and a radial.
  • the oil film emerging from the nozzle bore as a rotating hollow cylinder widens into a hollow cone due to the centrifugal force whose edges start to vibrate unstably and tear into small oil droplets.
  • the atomized oil forms a cone with a more or less large opening angle.
  • Swirl nozzles pressure atomizers
  • air-assisted atomizers of the known types with a pressure of up to approx. 100 bar are hardly suitable for this because they do not allow a small angle of propagation, the atomization quality is restricted and the impulse of the drop spray is low.
  • This consists of a nozzle body, in which a turbulence chamber is formed, which is connected to an outside space via at least one nozzle bore, and which has at least one supply channel for the liquid to be atomized, which can be supplied under pressure. It is characterized in that the cross-sectional area of the feed channel opening into the turbulence chamber is larger by a factor of 2 to 10 than the cross-sectional area of the nozzle bore.
  • This arrangement makes it possible to generate a high level of turbulence in the turbulence chamber, which does not subside on the way to the point of exit from the nozzle.
  • the fluid jet is caused to decay rapidly by the turbulence generated in front of the nozzle bore in the outside space, that is to say after leaving the nozzle bore, resulting in low angles of propagation of 20 ° and less.
  • the droplet size is also very small.
  • the aim is to generate a drop spray over the entire load range of the gas turbine (approx. 10% to 120% fuel mass flow based on nominal load conditions), which enables stable, low-pollution combustion in a given air flow field .
  • the fuel admission pressure drops due to the falling total fuel mass flow.
  • the energy required for atomization for pressure atomizers is over given the fuel admission pressure, so that the atomization quality worsens in this load range and the penetration depth of the fuel spray into the air flow becomes smaller due to the low fuel admission pressure.
  • the invention tries to avoid all of these disadvantages. It is based on the task of developing a pressure atomizing nozzle which has a simple construction, requires only a small installation space and enables a spray angle of the liquid to be atomized which is adapted to the respective operating conditions.
  • a sufficiently large nozzle admission pressure should be generated even with small fuel mass flows (approx. 25% based on nominal load conditions), while the nozzle with a large fuel mass flow (approx. 100-120% based on nominal load conditions) should not generate an excessively high nozzle admission pressure should need.
  • the drop spray produced in this way is intended to enable low-pollutant and stable combustion over the entire load range of the gas turbine.
  • a pressure atomizing nozzle comprising a nozzle body, in which a turbulence and / or swirl chamber is formed, which is connected to an outside space via a nozzle bore and has at least one first feed channel for the liquid to be atomized, through which said liquid is submerged Pressure can be supplied, in that at least one further supply channel for part of the liquid to be atomized or for a second liquid to be atomized opens into the chamber, through which said part of the liquid or the second liquid can be supplied under pressure and with swirl .
  • this two-stage pressure atomizing nozzle enables adaptation of the pot spray (atomization quality, drop size, spray angle) to the respective load conditions. Furthermore, the nozzle is characterized by a simple design that takes up little space.
  • the main atomizer stage thus consists of a swirl-free, turbulence-assisted pressure atomizer nozzle which, at high nozzle admission pressures, for example 100 bar, delivers very fine atomization with extremely small spray angles.
  • the rotating movement creates a hollow cone flow at the nozzle hole, so that the liquid only exits the nozzle as a film from a certain mass fraction that is supplied by the swirl stage. If the mass fraction of the swirl stage is increased with falling total liquid mass flow, the liquid admission pressure can be kept at a high level, so that fine atomization can be maintained even with a low mass flow.
  • the liquid spray cone angle is larger at low load, this compensates for the lower penetration depth of the liquid spray into the air flow. Since a very small spray cone angle is desired at full load and overload, the liquid mass flow to be atomized flowing through the swirl channels is reduced or completely switched off in these cases.
  • the liquid to be atomized can be fed into the chamber via the first feed channel (s) with swirling action.
  • the pressure atomizer nozzle is operated at full and overload operation via a main pressure swirl stage with a low swirl, by swirling the entire liquid to be atomized via at least one first supply channel to the swirl chamber, where a swirled flow is generated which then passes through the nozzle bore into the outside space , and in partial and low-load operation it is additionally operated via a further pressure swirl stage with a larger swirl, in that part of the liquid to be atomized or a second liquid to be atomized is more swirled through the at least one further supply channel and there is a strongly swirled flow is generated, which then passes through the nozzle bore into the outside space, the proportion of the more swirled liquid supplied via the further swirl stage being increased as the total liquid mass flow decreases, this can be done e way an excellent adaptation of the atomization to the respective load range.
  • the nozzle according to the invention is advantageously used in a premix burner of the double-cone design or in a four-slot burner, part of the combustion air (approx. 3 to 7%) being conducted in the jacket flow around the nozzle in the vicinity of the nozzle. This avoids local detachment and recirculation areas. The recirculation zone is prevented from moving into the interior of the burner.
  • FIGS. 1 to 3 show a first exemplary embodiment of the invention, FIG. 1 showing the pressure atomizing nozzle in a partial longitudinal section and FIGS. 2 and 3 showing two cross sections in different planes.
  • the pressure atomizing nozzle comprises a nozzle body 30, consisting of a first tube 31, which is closed at its end seen in the direction of flow by a conical cover 32. In the middle of the cover 32 there is a nozzle bore 33, the longitudinal axis of which is designated by 34.
  • a second tube 35 which has a smaller outside diameter than the inside diameter of the first tube 31, is inserted into the tube 31 and extends as far as the cover 32 and rests thereon.
  • the annular space 36 between the two tubes 31 and 35 serves to supply the or a part of the liquid 37 to be atomized.
  • the end of the tube 35 resting on the cover 32 is provided with four tangentially arranged slots 38 which connect the annular space 36 to produce a chamber 39 which serves as a swirl chamber for the liquid 37 to be atomized flowing through the slots 38.
  • the chamber 39 is delimited by the inner walls of the cover 32 and the second tube 35, and by a filler 40 which is inserted in the interior of the second tube 35 and fastened therein. This filler 40 is spaced from the top edge of the slots 38, however, it can also be at the same height in another embodiment variant.
  • the pressure atomizing nozzle according to the invention thus has two stages - a turbulence generator stage (see FIG. 2) and a pressure swirl stage (see FIG. 3).
  • the pressure atomizing nozzle can also be provided with more or fewer slots 38 or feed channels 41.
  • the feed channel 41 can extend over the entire circumference of the filler 40, so that an annular gap results as a feed channel into the turbulence chamber 39. A different distribution of the channels over the circumference is also possible.
  • FIGS. 4 to 6 show a further exemplary embodiment of the invention, FIG. 4 showing the pressure atomizing nozzle according to the invention in a partial longitudinal section and FIGS. 5 and 6 showing two cross sections in different planes.
  • the structure of the nozzle differs from the exemplary embodiment described above only in that a swirl main stage is present in the nozzle instead of the turbulence generator stage.
  • the supply channels 41a in contrast to the supply channels 41 in FIG. 1, are not arranged axially aligned in the filler 40, but are positioned tangentially, so that the liquid 37 to be atomized swirls in both via the channels 38 and via the channels 41a the chamber 39 arrives. It is important that the liquid 37 to be atomized receives only a small swirl, which leads to a narrow spray cone angle ⁇ , when it has flowed through the channels 41a, while the swirl of the liquid 37 is greater after flowing through the channels 38 and thus a larger one Spray cone angle ⁇ is achievable.
  • the pressure atomizing nozzle comprises a nozzle body 30, consisting of a first tube 31, which is closed at its end seen in the direction of flow by a conical cover 32. In turn, the nozzle bore 33 is arranged in the cover 32.
  • a second tube 35 is inserted, which has a smaller outside diameter than the inside diameter of the first tube 31, so that an annular channel 36 is formed between the tubes 31 and 35, which according to FIG. 7 has a different height due to different inserts can have.
  • This ring channel 36 serves as a feed line for a swirl stage.
  • the second tube 35 is delimited by a filler 40 of larger diameter, which encloses the chamber 39 with the cover 32 of the first tube 31.
  • At least one tangential swirl channel 38 for connecting the ring channel 36 to the chamber 39 is arranged in the filler 40.
  • 6 channels 38 are advantageous.
  • at least one feed channel 41 is also arranged axially parallel as a turbulence channel for the liquid to be atomized, the feed channel / feed channels 41 opening into the swirl channel / swirl channels 38.
  • channels 38 and 41 are arranged so that, for example, the swirl channels 38 into the Open channels 41, so that the liquid to be atomized only enters the chamber 39 via the channels 41.
  • Fig. 8 shows a schematic representation of a possible liquid supply system to the pressure atomizing nozzle.
  • the liquid to be atomized in this case liquid fuel (oil) 12
  • a return valve 49 is used to set the pump admission pressure.
  • a shut-off valve 50 is arranged in the fuel line between the pump 42 and the pressure vessel 43.
  • Two lines 44, 45 extend from the pressure vessel 43, the line 44 feeding the annular space 36 (and thus the swirl atomizer stage) and the line 45 being connected to the feed channels 41 (turbulence generator stage) or 41a (swirl atomizer stage).
  • a control valve 46 and 47 is arranged in each of the lines 44 and 45, which allow the respective amount of liquid supplied to be regulated.
  • one of the two valves 46, 47 can also be completely closed, so that in this case only one of the two atomizing stages of the nozzle is in operation. Smooth switching is possible between the two stages.
  • several burners for example a gas turbine combustion chamber, are to be supplied with fuel via this fuel supply system.
  • the circuit shown has the advantage that only the two valves 46, 47, i.e. only one control valve per stage.
  • FIG. 9 Another embodiment variant analogous to FIG. 8 is shown in FIG. 9.
  • the pressure atomizing nozzle is fed with water 51 via a feed line 44 and with oil 12 via a feed line 45.
  • a pump 42 is arranged in each of the lines 44 and 45 and a shut-off valve 50 is arranged downstream, with which the lines 44 and 45 can optionally be closed.
  • the amount of the liquids 12, 51 to be atomized is regulated by means of the control valves 46, 47. If, as indicated in FIG. 9, several burners, for example a gas turbine combustion chamber, are supplied with liquid fuel 12 or water 51 via this liquid supply system, then the nozzle can be operated at the start or at partial load by only atomizing oil 12 finely via the main swirl stage .
  • the swirl stage can be designed for maximum pressure at maximum fuel mass flow ⁇ BS .
  • water 51 is then supplied via line 44.
  • Water 51 and oil 12 mix in chamber 39 and form an emulsion which is atomized when it emerges from the nozzle. This leads to a reduction in NOx emissions.
  • FIG. 10 shows the distribution of the fuel mass flow in BS as a function of the radius R of the spray in a pressure atomizer nozzle according to the embodiment variant shown in FIG. 1 at a certain distance from the nozzle. If only the turbulence-generating stage is operated, a very narrow spray cone angle ⁇ is achieved. If, on the other hand, only the swirl generator stage is operated, this has an effect in a larger spray cone angle ⁇ . With the combined operation of both stages, the mass distribution between the two stages can be varied continuously.
  • FIG. 11 shows the distribution of the fuel mass flow in BS as a function of the radius R of the spray in a pressure atomizer nozzle according to the embodiment variant shown in FIG. 4 at a certain distance from the nozzle.
  • the pressure atomizing nozzle according to the invention can, for example, be installed in a gas turbine burner and operated as follows:
  • a pressure atomizer nozzle is to be used in an embodiment variant according to FIG. 1. Since a very narrow spray cone angle ⁇ is desired for full load and overload, only the turbulence-assisted atomizer stage is used. For this purpose, the entire fuel mass flow to be atomized is supplied without swirl to the turbulence chamber 39 via at least one feed channel 41 (four feed channels 41 according to FIG. 1), a highly turbulent flow being generated there, which then passes through the nozzle bore 33 into the burner.
  • This main stage delivers a very fine atomization with an extremely narrow spray cone angle ⁇ (approx. 20 °) at nozzle admission pressures of approx. 100 bar.
  • this turbulence-assisted pressure atomizer stage is combined with a swirl stage for the generation of small drops at low throughputs.
  • part of the fuel to be atomized is swirled into the chamber 30 via at least one further feed channel 38 (four feed channels 38 according to FIG. 1), so that the turbulence chamber 30 is additionally used as a swirl chamber.
  • the rotating movement creates a hollow cone flow at the nozzle bore 33. From a certain mass fraction that is passed through the swirl stage, the fuel only emerges as a film from the nozzle.
  • the fuel admission pressure can be kept at a high level (> 10 bar) and fine atomization can be maintained even with a low mass flow.
  • the spray cone angle becomes low load ⁇ enlarged. Since the depth of penetration of the fuel spray into the air flow is lower at low load than at full load, this is compensated for by the larger spray cone angle ⁇ .
  • a very narrow spray cone angle ⁇ is desirable for full load and overload. For this purpose, the fuel mass flow flowing through the swirl channels 38 must be switched off completely, so that the behavior of a pure turbulence-assisted pressure atomizer nozzle is achieved.
  • a pressure atomizer nozzle according to FIG. 4 is used, then during full and overload operation of the gas turbine, the entire fuel to be atomized is fed to the swirl chamber 39 with a small swirl via at least one first feed channel 41a (four feed channels 41a according to FIG. 4), one swirling there Flow is generated, which then passes through the nozzle bore 33 into the outside space. Due to the low swirl, a narrow spray cone angle ⁇ is achieved, which leads to fine atomization of the fuel at high pressures. In partial and low-load operation, part of the fuel to be atomized is additionally swirled to the chamber 39 via the at least one further feed channel 38 (four feed channels 38 according to FIG. 4).
  • the pressure atomizing nozzle according to the invention can be installed, for example, in a premix burner of the double-cone type, the basic structure of which is described in EP 0 321 809 B1.
  • the two partial cone bodies 1, 2 are arranged radially offset from one another with respect to their longitudinal symmetry axes 1b, 2b. This creates tangential air inlet slots 19, 20 on both sides of the partial cone bodies 1, 2 in the opposite inflow arrangement, through which the combustion air 15 flows into the interior 14 of the burner, ie into the cone cavity formed by the two partial cone bodies 1, 2.
  • the partial cone bodies 1, 2 expand in a straight line in the direction of flow, ie they have a constant angle ⁇ with the burner axis 5.
  • the two partial cone bodies 1, 2 each have a cylindrical starting part 1a, 2a, which also run offset.
  • the pressure atomizing nozzle 3 according to the invention, which is arranged approximately in the narrowest cross section of the conical interior 14 of the burner.
  • the burner can also be designed without a cylindrical initial part, that is to say purely conical.
  • the liquid fuel 12 is atomized by means of the nozzle 3 in the manner described above. Different spray cone angles ⁇ result depending on the respective operating conditions.
  • the fuel spray 4 is enclosed in the interior 14 of the burner by the combustion air stream 15 flowing tangentially into the burner through the air inlet slots 19, 20; the mixture is ignited only at the outlet of the burner, the flame being stabilized in the region of the burner mouth by a backflow zone 6.
  • the two partial cone bodies 1, 2 each have a fuel feed line 8, 9 along the air inlet slots 19, 20, which are provided on the long side with openings 17 through which a further fuel 13 (gaseous or liquid) can flow.
  • This fuel 13 is mixed with the combustion air 15 flowing through the tangential air inlet slots 19, 20 into the interior of the burner, which is represented by the arrows 16. Mixed operation of the burner via the nozzle 3 and the fuel feeds 8, 9 is possible.
  • a front plate 10 is arranged with openings 11, through which dilution air or cooling air can be supplied to the combustion chamber 22 if necessary. In addition, this air supply ensures that flame stabilization takes place at the burner outlet. There is a stable flame front 7 with a backflow zone 6.
  • guide plates 21a, 21b can be seen from FIGS. 13 to 15. These can be opened or closed, for example, about a pivot point 23, so that the original gap size of the tangential air inlet slots 19, 20 is thereby changed. Of course, the burner can also be operated without these baffles 21a, 21b.
  • a burner can also be operated with the method just described, consisting essentially of a swirl generator 100 for a combustion air stream 15 and of means for injecting a fuel, in which a mixing section 220 is arranged downstream of the swirl generator 100 and this has transition channels 201 running in the flow direction within a first section part 200 for transferring a flow formed in the swirl generator 100 into the flow cross section 18 downstream of the transition channels 201 of the mixing section 220, the means for injecting the fuel being a pressure atomizer nozzle according to the invention, which according to one of the The method described above is operated.
  • the swirl generator 100 is preferably a conical structure, which is acted upon tangentially several times (for example via four slots) by the combustion air flow 15 flowing in tangentially.
  • This combustion air flow 15 wraps around the fuel drop spray 4, which was previously formed by atomizing the liquid fuel 12 in the two-stage pressure atomizing nozzle 3.
  • the flow that is formed is seamlessly transferred to a transition piece 200, which is extended by a tube 18, using a transition geometry (transition channels 201) provided downstream of the swirl generator 100. Both parts form the mixing section 220, to which the actual combustion chamber (not shown here) is connected on the downstream side.
  • the mixing section allows the fuel to be premixed very well with the combustion air, enables low-loss flow control and prevents the flame from re-igniting from the combustion chamber due to the maximum axial speed on the axis. Since the axial speed drops towards the wall, bores 48 are provided in the wall of the tube, through which combustion air 15 flows, which causes an increase in speed along the wall. Only downstream of the mixing tube 220 does a central backflow zone 6, which has the properties of a flame holder, form. It is also advantageous here if 3 up to 7% of the combustion air flow 15 are guided as a jacket air flow 15a around the pressure atomizing nozzle. This in turn prevents separation and recirculation areas in the vicinity of the nozzle.

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  • 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)
  • Nozzles (AREA)
EP97810083A 1996-03-05 1997-02-20 Méthode d'exploitation d'une buse de pulvérisation par pression Expired - Lifetime EP0794383B1 (fr)

Applications Claiming Priority (2)

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DE19608349 1996-03-05
DE19608349A DE19608349A1 (de) 1996-03-05 1996-03-05 Druckzerstäuberdüse

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EP0794383A2 true EP0794383A2 (fr) 1997-09-10
EP0794383A3 EP0794383A3 (fr) 1998-04-01
EP0794383B1 EP0794383B1 (fr) 2002-11-06

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US (1) US5934555A (fr)
EP (1) EP0794383B1 (fr)
JP (1) JPH09327641A (fr)
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DE (2) DE19608349A1 (fr)

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EP0892212A3 (fr) * 1997-07-17 1999-02-10 Abb Research Ltd. Buse de pulvérisation par pression
EP0911583A1 (fr) * 1997-10-27 1999-04-28 Asea Brown Boveri AG Procédé de mise en oeuvre d'un brûleur à prémélange
EP0924461A1 (fr) 1997-12-22 1999-06-23 Abb Research Ltd. Buse de pulvérisation par pression à deux étages
EP0924460A1 (fr) 1997-12-22 1999-06-23 Abb Research Ltd. Buse de pulvérisation par pression à deux étages
WO1999047270A1 (fr) * 1998-03-18 1999-09-23 Slowik Guenter Procede permettant de modifier le mouvement de rotation d'un fluide dans la chambre de rotation d'un gicleur et generateur de rotation pour gicleurs
DE10008389A1 (de) * 2000-02-23 2001-08-30 Guenter Slowik Verfahren und Leitungssystem zur Beeinflussung des Tropfenspektrums von fluiden Stoffen bei deren Zerstäubung
US7972133B2 (en) 2006-03-27 2011-07-05 Alstom Technology Ltd. Burner for the operation of a heat generator and method of use
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EP0892212A3 (fr) * 1997-07-17 1999-02-10 Abb Research Ltd. Buse de pulvérisation par pression
EP0911583A1 (fr) * 1997-10-27 1999-04-28 Asea Brown Boveri AG Procédé de mise en oeuvre d'un brûleur à prémélange
US6270338B1 (en) 1997-10-27 2001-08-07 Asea Brown Boveri Ag Method for operating a premix burner
EP0924461A1 (fr) 1997-12-22 1999-06-23 Abb Research Ltd. Buse de pulvérisation par pression à deux étages
EP0924460A1 (fr) 1997-12-22 1999-06-23 Abb Research Ltd. Buse de pulvérisation par pression à deux étages
US6036479A (en) * 1997-12-22 2000-03-14 Abb Research Ltd. Two-stage pressure atomizer nozzle
WO1999047270A1 (fr) * 1998-03-18 1999-09-23 Slowik Guenter Procede permettant de modifier le mouvement de rotation d'un fluide dans la chambre de rotation d'un gicleur et generateur de rotation pour gicleurs
US6517012B1 (en) 1998-03-18 2003-02-11 Slowik Guenter Method for varying the swirling movement of a fluid in the swirl chamber of a nozzle, and a nozzle system
DE10008389A1 (de) * 2000-02-23 2001-08-30 Guenter Slowik Verfahren und Leitungssystem zur Beeinflussung des Tropfenspektrums von fluiden Stoffen bei deren Zerstäubung
US7972133B2 (en) 2006-03-27 2011-07-05 Alstom Technology Ltd. Burner for the operation of a heat generator and method of use
CN102580867A (zh) * 2012-02-10 2012-07-18 烟台润达垃圾处理环保股份有限公司 一种液体高速雾化机
RU2493521C1 (ru) * 2012-04-10 2013-09-20 Олег Савельевич Кочетов Система кочетова оборотного водоснабжения
RU2493520C1 (ru) * 2012-04-10 2013-09-20 Олег Савельевич Кочетов Система оборотного водоснабжения
RU2482925C1 (ru) * 2012-04-19 2013-05-27 Олег Савельевич Кочетов Центробежная вихревая форсунка кочетова
RU2486964C1 (ru) * 2012-04-19 2013-07-10 Олег Савельевич Кочетов Центробежная вихревая форсунка
RU2500482C1 (ru) * 2012-08-16 2013-12-10 Олег Савельевич Кочетов Широкофакельная центробежная форсунка
RU2550838C1 (ru) * 2013-11-06 2015-05-20 Олег Савельевич Кочетов Форсунка вихревая кочетова
RU2550839C1 (ru) * 2013-11-06 2015-05-20 Олег Савельевич Кочетов Форсунка кочетова
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Also Published As

Publication number Publication date
EP0794383A3 (fr) 1998-04-01
DE19608349A1 (de) 1997-09-11
JPH09327641A (ja) 1997-12-22
CN1164442A (zh) 1997-11-12
EP0794383B1 (fr) 2002-11-06
DE59708638D1 (de) 2002-12-12
US5934555A (en) 1999-08-10

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