CN101981379A - burner scaling - Google Patents
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- CN101981379A CN101981379A CN2009801112622A CN200980111262A CN101981379A CN 101981379 A CN101981379 A CN 101981379A CN 2009801112622 A CN2009801112622 A CN 2009801112622A CN 200980111262 A CN200980111262 A CN 200980111262A CN 101981379 A CN101981379 A CN 101981379A
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- 239000000446 fuel Substances 0.000 claims abstract description 90
- 239000000203 mixture Substances 0.000 claims abstract description 23
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
- F23R3/286—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply having fuel-air premixing devices
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
- F23R3/28—Continuous combustion chambers using liquid or gaseous fuel characterised by the fuel supply
- F23R3/34—Feeding into different combustion zones
- F23R3/346—Feeding into different combustion zones for staged combustion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
- F23R2900/00016—Retrofitting in general, e.g. to respect new regulations on pollution
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
- F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
- F23R2900/00—Special features of, or arrangements for continuous combustion chambers; Combustion processes therefor
- F23R2900/00017—Assembling combustion chamber liners or subparts
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Gas Burners (AREA)
Abstract
The invention relates to a method for upscaling the size of a burner (1) of a gas turbine engine comprising a burner housing (2), in which burner (1) at an upstream end a mixture of fuel (14) and air (12) is provided from a premixing channel (10) for sustaining a main flame (7) at a downstream end of the burner (1), wherein the premixing channel (10) is defined at its exit (8) by a circular inner wall formed by an inner quarl section (4a) and a circular outer wall formed by an outer quarl section (4b). According to the invention the burner (1) can be increased in size by adding a quarl section (4c) outside and circumferenting said quarl section (4b) and forming an annular space between the added quarl section (4c) and the existing outer quarl section (4b) and by adding a premixing channel (11) defined at its exit (9) by a circular inner wall formed by said previously outmost quarl section (4b) and a circular outer wall formed by the added quarl section (4c), wherein said quarl sections (4a, 4b, 4c) are defining a combustion room for housing said main flame (7), wherein an outer quarl section (4c, 4b) has a greater diameter than a neighboring inner quarl section (4b, 4a) and extends a greater distance downstream than the neighboring inner quarl section (4b, 4a).
Description
Technical field
The present invention relates to preferably be used in the combustion road (quarl) of the burner in the gas-turbine unit, relate more specifically to be suitable for making the combustion road in the stable burner of engine combustion, and further relate to guiding combustion chamber (pilot combustor) and provide combustion product so that main lean premixed combustion stablized burner.
Background technology
Gas-turbine unit is used in the various application that comprise generating, military commercial aviation, pipeline transportation and sea-freight.In the gas-turbine unit with the work of LPP pattern, fuel and air are provided for the combustion chamber, and mix the back by flame ignition at this, thereby take fire.Except that the suitable mixing of the thermal efficiency, fuel and air, the control of subject matter relevant with the combustion process of gas-turbine unit and flame stabilization, pulsation and noise elimination and pollutant effulent is relevant, particularly with nitrogen oxide (NO
x), CO, UHC, cigarette be relevant with particle emission.
The industrial combustion gas turbogenerator is to reduce flame temperature by adding the air more air more required than combustion process itself when working with the LPP pattern.The unnecessary air that does not react must be heated in combustion process, and consequently the flame temperature of combustion process is lowered (being lower than stoichiometric point (or claiming stoichiometric point)), is reduced to 1800K from about 2300K, even lower.Requiring to reduce flame temperature is in order significantly to reduce NO
xEmission.Be proved to be to reduce NO
xThe successful method of emission is to make combustion process oil-poor (lean), makes divalence nitrogen-atoms and oxygen atom (N thereby make the temperature of flame be reduced to be lower than
2And O
2) separate and recombine into NO and NO
2Temperature.The swirl stabilized combustion circulation is commonly used in the industrial combustion gas turbogenerator, so that around center line, produce the adverse current (recirculating zone that eddy flow causes by passing through of pointing out above, Swirl Induced Recirculating Zone), thus adverse current is returned heat and free radical in the unburned fuel that enters and the AIR MIXTURES makes flameholding.Need begin (making fuel-pyrolysis, the branching process of beginning chain lock) with the heat and the free radical of fuel that reacts before and air and keep the fresh unreacted fuel and the smooth combustion of air mixture.The combustion product that smooth combustion in the gas-turbine unit requires the circulating combustion process to produce transports go back to the upstream with the process of taking fire.Flame front is stabilized in the shear layer of the recirculating zone that eddy flow causes.In shear layer, " the local turbulence flame speed of air/fuel mixture " must be higher than " local air/fuel mixture speed ", thereby makes flame front/combustion process to be stabilized.
Lean premixed burning is as follows not as the combustion stablized immanent cause of diffusion flame:
1. flame temperature being reduced to the required air capacity of 1700-1800K from 2300K approximately is the twice of stoichiometric(al) combustion required air quantity.Overall like this fuel/air mixture than (Φ) very near (about 0.5 or be lower than 0.5; Φ 〉=0.5) or the fuel/air mixture ratio when being similar to premixed flame and oil-poor extinguishing occurring.Under these conditions, flame part in a periodic manner extinguishes, and restrikes again.
2. during near oil-poor extinction limit, the flame speed of oil-poor local premixed flame is very responsive for the equivalent proportion fluctuation.The fluctuation of flame speed can cause the space wave/motion of flame front (recirculating zone that eddy flow causes).The more unsettled flame front that is easy to move of premixed flame causes periodic rate of heat release, and this can cause the development of flame movement, unsettled hydrodynamic process and thermodynamics-acoustic instability again.
3. the equivalent proportion fluctuation may be that unsettled heat is discharged and the unsettled pressure vibration the most common joining mechanism that is coupled.
4. in order to make sufficient combustion oil-poor, in order significantly to reduce NO
xDischarging, the nearly all air that uses in the engine all must be by injector and fuel premixed.Therefore, the possibility that should respond of all the fuel streams in the burner, and that point that requires to take fire is fixed.
5. when the required heat that reacts is the stability limit factor, the very little erratical fluctuations of fuel/air mixture equivalent proportion (may being caused that perhaps being flowed by the air by burner/injector causes by the vibration of fuel) can make the flame part extinguish, restrike.
6. the another very important reason of premixed flame stability reduction is that the sharp gradient that fuel and air mix can be eliminated from combustion process.This makes pre-mixed flow be enough to aitiogenic in temperature all is combustible Anywhere.When flame can be easier to occur in a plurality of positions, can become unstable more.The unique method that makes premixed flame be stabilized in the fixed position mixes the thermograde (when temperature is too low, flame can not occur) that is produced based on unburned premixed fuel and air with the hot product of burning.This makes the thermal gradient that generation, radiation, diffusion and convection current produced of heat become a kind of method that makes premixed flame stable.The radiation heating of fluid can not produce steep gradient; Therefore, stability is produced, is spread by heat certainly and is by convection into pre-reaction zone and causes.Diffusion only can produce precipitous gradient in laminar flow, and can not produce in turbulent flow, only makes convection current and energy produce the required sharp gradient of flame stabilization, and this is actually thermal gradient and free radiation gradient.Thermal gradient and free radiation gradient are by same mechanism generation, diffusion and the convection current by the backflow combustion product in the recirculating zone that causes at eddy flow.
7. in pre-mixed flow and diffuse flow, cause that the rapid expanding of separation and eddy flow reflux to be used to usually in the fuel of pre-reaction and air, produce thermal gradient and free radical.
A target of the present invention is to propose a kind of approach that the size of burner is carried out convergent-divergent.
Summary of the invention
Disclosed by the invention is a kind of partly-premixed low emission combustor of oil-poor-rich oil that is used for gas turbine combustion chamber, and it all provides stable igniting and combustion process under all engine load conditions.This burner is according to following principle work, that is: the free radical " supply " from the floss hole of guiding combustion chamber (pilot combustor) with heat and high concentration burns thereby keep the fast and stable of leading lean premixed flame to the main flame that burns in lean premixed air/fuel swirl.Guiding combustion chamber supply heat, and the free radical of high concentration directly added to the shear layer of the recirculating zone that preceding stationary point and main cyclone cause, main lean premixed stream mixes at this with the combustion gas product of guiding the heat that the combustion chamber provides.This allows the more oil-poor mixing of main premix air/fuel swirl flow combustion and lower temperature, and not so it can not be in swirl stabilized backflow from keeping under the operating mode of burner.
According to a first aspect of the invention, this paper has proposed the method for a kind of amplification that feature characterized by independent claims 1 (or claiming to increase) burner dimensions.
According to a second aspect of the invention, this paper has proposed a kind of burner of the method up-sizing according to the independent solution claim.
Others of the present invention embody in the dependent claims.
Burner adopts:
Produce-be imparted to the eddy flow of the air/fuel in the fuel stream, swirling number S by radial swirler
nBe that (it is greater than critical value S more than 0.7
n=0.6);
Near the d/d active matter in preceding stationary point-non-equilibrium free radical,
Burner geometry with specific type of a plurality of combustion duct devices, and
Fuel in the burner and inside air classification make the combustion process under all combustion gas turbine operating modes stable.
In brief, under all engine load conditions, disclosed burner all provides stable ignition and combustion process.Some key characters relevant with burner of the present invention are:
The geometrical orientation of burner element;
Fuel and air capacity at the burner internal classification;
The minimum of the required active matter-Ji that under different engines/burner operating mode, produces;
The fuel attribute;
Fuel and Air mixing under working conditions of different engines;
The eddy flow level of giving (imparted level of swirl);
A plurality of (minimum is a double burning way) combustion road layout.
In order to reach alap emission level, target of the present invention is the mixing attribute that has unanimity in the outlet of lean premixed passage.The disclosure covers following situation: have two different combustion zones in burner, in these two combustion zones, fuel is burning simultaneously always.Two combustion zones all are swirl stabilized, fuel and air before combustion process by premixed.The all burned main combustion process of fuel above 90% is oil-poor.Supportive combustion process occurs in little inside, guiding combustion chamber, wherein has 1% total fuel flow to be consumed at most, and this process can be oil-poor, stoichiometric (or claim stoichiometric) and (equivalent proportion Φ=1.4 or higher) of rich oil.
An important difference between the burner that provides in disclosed burner and the prior art document is: because the present invention uses from the combustion zone of guiding combustion chamber the free base flow that do not put out along the center line downstream guiding of guiding combustion chamber, so do not need bluff in the guiding combustion chamber, described free radical stream is released by the outlet of standard-sized sheet zone in the guiding combustion chamber of the larynx shape portion of guiding combustion chamber.
Supportive combustion process in the little guiding combustion chamber can be oil-poor, stoichiometric or rich oil, and can both provide the main cause of stable ignition and combustion process relevant with efficiency of combustion under all engine load conditions.Because high surface area causes guiding the fray-out of flame on the chamber wall, so the combustion process efficient that occurs in the small combustion chamber guide is low.No matter be the situation of oil-poor, stoichiometric or rich oil, inefficient combustion process can produce a large amount of active matters---free radical, need these active matters to improve the stability of main oil-poor flame, and they are useful (notes: the flame that occurs in the oil-poor air/fuel mixture of premix are known as oil-poor flame in this article) for the successful work of the design/invention of this burner.
The shear layer of keeping (but misfire, reason is that little guiding combustion chamber can be used as torch igniter) main recirculating zone under oil-poor the extinguishing that is lower than main oil-poor flame (Lean Blow Off the is called for short LBO) limit (roughly be T＞1350K,
) burning may be very the difficulty.Engine in this burner design, uses/provides " classification (staging) " of additional small combustion chamber guide when being lower than the LBO submaximal work of main oil-poor flame.The air (being undertaken by cooling off in conjunction with bump and convection current) that is used for cooling off little guiding combustion chamber inwall accounts for about 5-8% of the total air that flows through burner, its before the arrival cyclone with the fuel premixed.Big relatively fuel quantity can be joined in the little guiding combustion chamber cooling air, this correspondence is the equivalent proportion of rich oil very
Eddy flow cooling air, fuel and the hot combustion product of guiding the combustion chamber from childhood can keep very effectively main oil-poor flame be lower than, be in, burning during greater than the LBO limit.Combustion process is very stable, effectively, and its reason is with premixed hot combustion product of fuel and very hot cooling air (greater than 750 ℃) hot and active matter (free radical) to be offered the preceding stationary point of main flame recirculating zone.In this combustion process, with premixed the little guiding combustion chamber that combines of the very hot cooling air (greater than 750 ℃) of fuel served as flameless burner, herein, reactant (oxygen and fuel) and combustion product premixed, and produce dispersed flame in the preceding stationary point of the recirculating zone that eddy flow causes.
In order to make disclosed burner energy operate as normal stable operation among the application, eddy flow level that requirement is given and swirling number (formula 1) (are not less than 0.6 greater than critical value, be not more than 0.8), disintegrate at this critical value place vortex---the recirculating zone can form, and can be fixedly located in many combustions road layout.Preceding stationary point P should be positioned at the combustion road, and is in the exit of guiding combustion chamber.The main cause of this requirement is:
If the eddy flow level of giving is low and swirling number that produced is lower than 0.6, then for the geometry of most of burner, can forms weak recirculating zone, thereby unsettled burning occur.
Need the strong inverse flow district with heat and free radical from passing the upstream back towards the flame front direction burnt fuel and the air before.Need certain strong inverse flow district that the shear layer zone is provided, in this shear layer zone, turbulent flame speed can " be mated " or is in direct ratio with the fuel/air mixture of part, and can set up stable flame.The flame front of setting up in the shear layer of main recirculating zone must be stable, and flame front periodic motion can not occur or move.The swirling number of giving can be high, but should not be higher than 0.8, and reason is, if be 0.8 or be higher than 0.8, the fuel that surpasses total fuel flow 80% so fails to be convened for lack of a quorum to reflux and goes back.The further growth of swirling number can not make the amount of combustion product reflux increase again again, and the flame in the shear layer of recirculating zone can run into high turbulent flow and tension force, and this may cause fray-out of flame, part to extinguish and restrike.The disclosure covers following situation: the rotational flow generator of any kind---radially, axial, axial-radially---can be used in this burner.In the disclosure, what illustrate is the radial swirler configuration.
Burner has utilized the aerodynamics stability of flame, and in many combustions road layout, flame is confined to the stable region---the recirculating zone.Many combustions road layout is a key character of burner design provided by the invention, and its reason is as follows.This combustion road (perhaps being called diffuser):
Provide the flame front (main recirculating zone) of flame stabilization (anchor), and do not needed flame stabilization on the surface of solids/bluff body, so just avoided high thermic load and the problem relevant with the burner mechanical integrity in the precalculated position, space;
Geometry (combustion road half-angle α and length L) is important for the size and the shape of the control recirculating zone related with swirling number.The length of recirculating zone is in direct ratio with 2-2.5 combustion road length doubly roughly;
The order of magnitude L/D=1 of optimum length L (D is the diameter of combustion road larynx shape portion).The minimum length in combustion road should be not littler than L/D=0.5, and be not more than L/D=2;
Best half-angle α should be less than 20 degree, and are not more than 25 degree, compare with the flame front that does not more limit to like this, and allowing had lower eddy flow before stability reduces; And
The transmission time of free radical reduces in the recirculating zone because the expansion of the hot gas that burning causes makes, and therefore most important task is exactly the size and the shape of control recirculating zone.
Description of drawings
Fig. 1 is the cross-sectional view of simplifying, and it schematically shows the burner in the shell of being encapsulated in of according to the present invention each side, but the detail how burner is configured in described enclosure is not shown among this figure.
Fig. 2 is the cross-sectional view of burner, and it schematically shows the section on the symmetry axis, and around rotary body of rotation formation of symmetry axis, it has shown the layout of burner.
Fig. 3 shows the diagram of flame with the flame stabilization limit of swirling number, the eddy flow level of giving and equivalent proportion variation.
Fig. 4 a shows the aerodynamic diagram near field, combustion chamber.
Fig. 4 b shows the aerodynamic diagram near field, combustion chamber.
Fig. 5 shows the diagram of turbulence intensity.
Fig. 6 shows the diagram that the relaxation time (relaxation time) changes with combustion pressure.
Fig. 7 illustrates the cartridge 15 of cyclone 3 porch with perspective view.
The specific embodiment
Hereinafter will a plurality of embodiment be described in further detail with reference to disclosed accompanying drawing.
In Fig. 1, with burner 1 burner is described with shell 2, shell 2 has encapsulated burner assembly.
For clarity sake, Fig. 2 shows the cross-sectional view of the burner on the rotation axes of symmetry.The major part of burner is radial swirler 3, a plurality of combustions road 4a, 4b, 4c and guiding combustion chamber 5.
Foregoing, burner 1 is according to following principle work, that is: with the free radical of heat and high concentration from the floss hole 6 " supply " of guiding combustion chamber 5 to the main flame 7 that lean premixed air/fuel swirl, burns, thereby keep the fast and stable burning of main lean premixed flame 7, wherein lean premixed air/fuel swirl comes from second outlet 9 of first outlet, the 8 and second lean premixed passage 11 of the first lean premixed path 10.The described first lean premixed path 10 is formed by the wall 4a and the 4b in a plurality of combustions road, and between between the two.The second lean premixed passage 11 is formed by the wall 4b and the 4c in many combustions road, and between between the two.The symmetrical wall 4c of outmost rotation in many combustions road is equipped with extension 4c1, so that the optimum length of many combustions road layout to be provided.The first lean premixed path 10 and the second lean premixed passage 11 are equipped with the cyclone wing, constitute cyclone 3, so that rotation is applied in the air/fuel mixture that passes passage.
When lean premixed air/fuel flows burning, produce main flame 7.Flame 7 (hereinafter also is abbreviated as RZ sometimes) in main recirculating zone 20 and forms the symmetrical shear layer 18 of conical rotation on every side.In this example combustion road 4c, flame 7 is enclosed in the inside of the extension 4c1 in outermost combustion road.
Guiding combustion chamber 5 supply heats, and the free radical of high concentration directly added to preceding stationary point P and introduce in the shear layer 18 of recirculating zone 20 of main cyclone, main lean premixed stream mixes with the hot gaseous product of guiding combustion chamber 5 and providing at this.
Guiding combustion chamber 5 is equipped with wall 21, and wall 21 surrounds and is used to guide between the burning of combustion zone 22.Air is supplied between burning by fuel channel 23 and air duct 24.Around the wall 21 of guiding combustion chamber 5, distribution plate 25 is arranged, porose on the plate face of distribution plate.Described distribution plate 25 keeps at a certain distance away with described wall 21, forms cooling space layer 25a.Cooling air 26 is inhaled into by cooling inlet 27, and comes the outside of described distribution plate 25, and when the time comes, cooling air 26 is distributed on the wall 21 of guiding combustion chamber, with the described wall 21 of effective cooling.Through after the described cooling, cool off air 26 and discharge by second cyclone 28 around the guiding combustion road 29 that is arranged on guiding combustion chamber 5.By giving fuel supplying in the pipe 30 that is arranged at cooling space layer 25a exterior circumferential, other fuel can be added in the oil-poor flame 7 of master of burning.Described then other fuel come out, and enter into second cyclone 28, and at this, positive at present hot cooling air 26 and the fuel that adds by pipe 30 are effectively mixed.
A large amount of relatively fuel can be joined in the 5 cooling air of little guiding combustion chamber, this correspondence the very equivalent proportion of rich oil
The combustion product of guiding eddy flow cooling air, fuel and the heat of combustion chamber from childhood can keep very effectively main oil-poor flame 7 be lower than, be in, greater than the burning under the LBO limiting case.Combustion process is highly stable, effective, and its reason is: the combustion product of heat and heat and active matter (free radical) are offered the preceding stationary point P of main flame recirculating zone 20 with the premixed very hot cooling air (greater than 750 ℃) of fuel.In this combustion process, with premixed the little guiding combustion chamber 5 that combines of the very hot cooling air (greater than 750 ℃) of fuel served as flameless burner, reactant (oxygen and fuel) is in this and combustion product premixed, and the preceding stationary point P in the recirculating zone 20 that eddy flow causes produces the flame that disperses.
In order to make among the application the operation of normally stably working of disclosed burner 1, eddy flow level that requirement is given and swirling number (formula 1) (are not less than 0.6 greater than critical value, be not more than 0.8, referring to Fig. 3), at described critical value place, vortex can be disintegrated---and recirculating zone 20 can form and can be fixedly located in many combustion road 4a, and 4b is in the 4c layout.Preceding stationary point P should be positioned at combustion road 4a, outlet 6 places of guiding combustion chamber 5 in the 4b, 4c.Some main causes of this requirement were partly mentioned at summary of the invention.Other reason is:
If swirling number is greater than 0.8, then eddy flow can extend to the outlet of combustion chamber, and this may cause steam turbine guide vane subsequently overheated.
Below provide the general introduction that the eddy flow level of giving and swirling number are required.Referring to Fig. 4 a and 4b.
The eddy flow level of giving (ratio between tangential moment and the axial moment) must be higher than critical level (0.4-0.6), thereby makes it possible to form stable centers recirculating zone 20.Critical swirling number S
NAlso the geometry with burner becomes, and this is its reason of changing between 0.4 and 0.6 just.If the swirling number of giving is smaller or equal to 0.4, perhaps in the scope of 0.4-0.6, then main recirculating zone 20 can not form, perhaps can periodically form, disappear down in low frequency (being lower than 150Hz), the aerodynamics that is produced may be very unsettled, can cause the combustion process of transition.
In the shear layer 18 of stable, constant recirculating zone 20, if any strong velocity gradient and turbulent flow level, then flame can be stablized under the following conditions:
The local speed (UF/A) of turbulent flame speed (ST)＞fuel/air mixture.
The backflow product is to be positioned at the thermal source of recirculating zone 20 and active matter (indicating by arrow 1a and 1b), at the mixing section downstream space of burner 1 with must be static on the time, with the fuel and air mixture of can pyrolytic coming in.If stable combustion process is not occupied an leading position, so calorifics-acoustic instability can appear.
The length of swirl stabilized flame is that weak point reaches 1/5th of jet flames, and has the obviously comparatively oil-poor blowing-out limit.
Premix or Turbulence Diffusion Combustion eddy flow provide a kind of effective fuel and air pre-mixing to close mode.
The intensity, swirling number and the feature recirculating zone speed URZ that carry the fuel/air mixture of the shear layer that enters recirculating zone 20 and recirculating zone secretly are proportional.
This feature recirculating zone speed URZ can be expressed as:
URZ＝UF/Af(MR，dF/A，cent/dF/A，SN)，
MR=rcent (UF/A, cent) 2/rF/A (UF/A) 2 wherein
(Driscoll1990 Whitelaw1991) shows in experiment
The exp-1/2 of RZ intensity=(MR) (dF/A/dF/A, cent) (URZ/UF/A) (b/dF/A),
And MR should＜1.
(dF/A/dF/A only is important for turbulent diffusion flame cent).
The size/length of recirculating zone is " fixing ", and is proportional with 2-2.5dF/A.
At S
NOn=0.8, no matter S
NHow high be increased to again, approximately being no more than 80% material mass can reflux.
Swim increase combustion road-dispersion wall burner larynx shape subordinate and improved backflow (Balchelor 67, and Hallet 87, and Lauckel 70, and Whitelow 90); Lauckel 70 shows that best geometric shape parameters is: α=20 °-25 °; L/dF/A, min=1 or higher.
This means dquarl/dF/A=2-3, but flame holding shows near 2 value, can reach the more oil-poor oil-poor blowing-out limit (Whitelaw 90).
Experiment and practical experience also show owing to there being the backfire risk, thereby for premixed flame, UF/A should be higher than 30-50m/s (Proctor 85).
If in combustion exit, road back side step (backfacing step) is set, then forms outside RZ.The length L ERZ of outside RZ is generally 2/3hERZ.
000
Active matter---free radical
In swirl stabilized combustion, combustion process is begun and reach stable by heat and free radical 31 are upstream sent back to flame front 7 from burnt fuel and air before.If combustion process is very oil-poor, as the situation in the oil-poor partly-premixed combustion system, will cause ignition temperature low so, the equilibrium level of free radical is also very low.Equally, under high-engine pressure, the very fast loose corresponding equilibrium level of temperature to (or weigh newly equilibrate to) and combustion product of the free radical that is produced by combustion process is referring to Fig. 6.This is owing to the loose speed to equilibrium state of this free radical is that increase along with pressure is exponentially and increases, and on the other hand, the equilibrium level of free radical is to be exponential reduction along with the reduction of temperature.Be used to make the level of free radical of burning beginning high more, combustion process will be quick more, stable more.Under elevated pressures, when the burner in the modern gas turbine engines is worked under oil-poor partly-premixed pattern, the relaxation time of free radical compare that free radical produces from it the shear layer 18 of main recirculating zone 20 that is back upstream short possibly towards required " transporting " time of the preceding stationary point P of flame front 7 and main recirculating zone 20 convection current downstream (representing with arrow 31).The result, when the stream of the free radical 31 of reverse flow is sent free radical 31 back to flame front 7 in the main by the time recirculating zone 20, and when free radical begin with the oil-poor fuel and air mixture of " fresh " premix that enters from first passage 10 and second channel 11 preceding stationary point P mix with light/when keeping combustion process, free radical 31 may reach low equilibrium level.
The present invention utilizes the high uneven level of free radical 32 that main poor oil firing 7 is stablized.In the present invention, the size of little guiding combustion chamber 5 is retained little, and most fuel combustion occurs in the lean premixed main chamber (7 and 18 place), rather than in little guiding combustion chamber 5.Little guiding combustion chamber 5 can be retained small size, and reason is that free radical 32 is d/d at the P place, preceding stationary point near main recirculating zone 20.This normally is fed to extra heat and free radical the most effectively position (7) of swirl stabilized combustion.Because the outlet 6 of little guiding combustion chamber 5 is positioned at the preceding stationary point P of main oil-poor backflow 20,, do not allow free radical 32 loose to low equilibrium level so extinguish and utilize the time scale between the free radical 32 very short.The preceding stationary point P of main oil-poor recirculating zone 20 is kept, and the outlet 6 in little guiding combustion chamber 5 is in and is stable on the aerodynamics in the combustion road (4a).In order to guarantee in the little guiding combustion chamber 5 with the distance of oil-poor, stoichiometry or fuel-rich combustion (zone 22) and the time is short as far as possible and directly, the position of the outlet of little guiding combustion chamber 5 is positioned in larynx shape portion 33 places of little guiding combustion chamber 5 on the center line.5 larynx shape portion 33 places, little guiding combustion chamber on center line, in combustion road 4a, free radical 32 mixes with product 31 from the abundant pre-warmed fuel and air mixture poor oil firing of pipe 30 and space 25a, mixes with premixed fuel 14 and air 12 in the shear layer 18 of oil-poor main recirculating zone 20 more subsequently.This high pressure gas-turbine unit for original the most serious intrinsic thermodynamics acoustic instability is very favorable.Equally, because free radical and the heat that produced by little guiding combustion chamber 5 is used effectively, so its size can be less, and do not need extinguishing process.Keep the little possibility of guiding combustion chamber 5 sizes to have beneficial effect for discharging.
Burner geometry with many combustions road layout
Described burner has utilized the aerodynamics stability of flame, and with the flame stabilization zone---recirculating zone 5 is defined in a plurality of combustions road layout (4a, 4b and 4c).The reason of a key character why many combustions road (term fires the road in this article sometimes as many combustions road sections more, and they define the complete combustion road of burner) layout becomes disclosed burner design is as follows.Combustion road (perhaps being called diffuser sometimes):
Flame front 7 is provided, and (it is fixed that main recirculating zone 20 is stayed) avoided high thermic load and the problem relevant with the burner mechanical integrity like this,
Geometry (combustion road half-angle α and length L) combines with swirling number, is important for size and the shape of controlling recirculating zone 20.The length of recirculating zone 20 is in direct ratio with 2-2.5 combustion road length L doubly roughly,
The order of magnitude L/D=1 of optimum length (D is the diameter of combustion road larynx shape portion).The minimum length in combustion road should be less than 0.5, and should be greater than 2 (list of references 1:The influence of Burner Geometry and Flow Rates on the Stability and Symmetry of Swirl-Stabilized Nonpremixed Flames; People such as V.Milosavljevic; Combustion and Flame 80, the 196-208 pages or leaves, 1990),
Best half-angle α (list of references 1) should be less than 20 degree, and are not more than 25 degree,
Compare with the flame front that does not more limit to, before stability reduces, lower swirling number can be arranged,
Owing to the expansion that burning causes, importantly control the size and the shape of recirculating zone, reduce the transmission time of free radical in the recirculating zone.
The convergent-divergent of burner
For different burner ratings, combustion road (perhaps diffuser) and the eddy flow of giving provide the possibility of the physical dimension ratio of the disclosed burner of convergent-divergent simply.
Scaled burner (example):
It is identical that swirling number in the path 10 should keep,
All other burner part should be identical; Fuel at the burner internal classification should keep identical or similar.
Amplify burner in proportion:
New third channel (this paper supposition is called 11b, and is unexposed) should be set at the outside, and around the second channel 11, new combustion road section 4d (only being illustrated among schematic combustion road accompanying drawing Fig. 8) is set at around the outside second channel 11; Form the outer wall of third channel thus; The shape of new combustion road section 4d should be similar with the shape of previous outmost combustion road section 4c.
Swirling number in the passage should be S
N, 10＞S
N, 11＞S
N, 11b, but should be greater than S
N=0.6, but be not more than 0.8
All other burner parts should be identical
The fuel of operation of combustors and burner internal classification should keep identical or similar.
Fuel staging and operation of combustors
When the same when being placed in the external reflux district (as shown in Fig. 4 b) in igniter 34 and the burner in prior art, enter this regional fuel/air mixture and must be made into rich oil usually, so that make enough heat of flame temperature, thereby keep this regional smooth combustion.Get enough rich oils, enough hot at main premixed fuel and air rheology, and have before the free radical of q.s, flame can not propagate into main recirculating zone usually.When flame in the time can not propagating into inner main recirculating zone after the igniting soon from the external reflux district, must when engine speed begins to increase, make flame with higher pressure propagation.Only after chamber pressure begins to rise, main flame begins can cause free radical quicker to low equilibrium level balance again from the propagation in external reflux district, this is a desired characteristics not, and for the situation of lighting flame in the preceding stationary point of main recirculating zone, it is reactive.Up to guide with bulk temperature (bulk temperature) when being elevated to certain level, just can light a fire in main recirculating zone, wherein at described certain level place, the equilibrium level that adds the product of free radical in free radical of carrying secretly in the main recirculating zone and premixed fuel and the air is enough to light main recirculating zone.The process that makes flame from external communication to main recirculating zone, a large amount of fuel does not burn and just leaves engine with unlit main premixed fuel and air mixture.If flame is to transfer to main recirculating zone before other burners in same engine in certain burner, will go wrong so, reason is because all fuel is all burned, thereby flame is stabilized in inner burner and can burns De Gengre.This causes burner different with temperature between the burner, and this may damage engine pack.
The present invention also allows to light the master at the P place, preceding stationary point of main recirculating zone 20 and burns 7.Most of gas-turbine units must use the position of external reflux district (referring to Fig. 4 b) as spark or torch igniter ignition engine.If smooth combustion can also occur, then can light a fire; Otherwise after igniting, can be blown out immediately.As in the present invention, inner or main recirculating zone 22 is more successful aspect the retention flame usually, and reason is that the gas 31 that refluxes is transported back, focuses on the zonule at the P place, preceding stationary point of main recirculating zone 20 from the heat of the combustion product of reflux gas 31.Combustion flame leading edge 7 is also outwards expanded with cone shape from stationary point P before this, as shown in Figure 2.The expand heat and the free radical 32 that make the upstream produce of the taper shape in downstream can be kept the burning in downstream, and flame front 7 is widened when mobile downstream.Compare with the swirl stabilized combustion of not firing, (4c) demonstrating the combustion road is how from essence the shape of flame being become more circular coneization and hemisphereization so not for 4a, 4b in combustion road shown in Figure 2.The flame front of circular coneization makes the point source of heat can effectively begin the burning in whole flow field more.
In the present invention, the combustion process in the burner 1 is classification.In the first order, promptly in the starter, by adding the fuel 23 that mixes with air 24, and utilize 34 burning mixts of igniter, the oil-poor flame 35 of generation in little guiding combustion chamber 5.After the igniting, the equivalent proportion of flame 35 is adjusted to oil-poor state (be lower than equivalent proportion 1, be approximately 0.8 equivalent proportion) or rich oil state (greater than equivalent proportion 1, equivalent proportion is approximately between 1.4 and 1.6) in the little guiding combustion chamber 5.The reason that equivalent proportion in the little guiding combustion chamber 5 is in the rich oil condition of scope between 1.4 and 1.6 is an emission level.The flame 35 in the little guiding combustion chamber 5 can be operated and keep to (equivalent proportion is 1) under the stoichiometry situation, but owing to may cause the higher thermic load of high emission level, wall 21, so do not advise doing like this.Operation is also kept flame 35 in the little guiding combustion chamber to be in benefit oil-poor or the rich oil condition is that the thermic load of the emission that produces and wall 21 is low.
At next stage, promptly in the second low load stage, fuel is added to cooling air 27 by pipe 30, and is endowed swirling motion in cyclone 28.Can effectively keep the burning of main oil-poor flame 7 when being lower than, being in or being higher than the LBO limit like this.The fuel quantity that can add the cooling air (through pre-warmed, temperature is much higher than 750 ℃) of heat to can be corresponding to equivalent proportion＞3.
At the next stage of operation of combustors, third part and full load level fuel 15a are added to air 12 gradually, and this is the main air flow that arrives main flame 7.
Claims (4)
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP08006666.5 | 2008-04-01 | ||
| EP08006666A EP2107311A1 (en) | 2008-04-01 | 2008-04-01 | Size scaling of a burner |
| PCT/EP2009/053555 WO2009121776A1 (en) | 2008-04-01 | 2009-03-26 | Size scaling of a burner |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN101981379A true CN101981379A (en) | 2011-02-23 |
| CN101981379B CN101981379B (en) | 2012-06-20 |
Family
ID=39810145
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009801112622A Expired - Fee Related CN101981379B (en) | 2008-04-01 | 2009-03-26 | Size scaling of a burner |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20110027728A1 (en) |
| EP (2) | EP2107311A1 (en) |
| CN (1) | CN101981379B (en) |
| ES (1) | ES2417158T3 (en) |
| RU (1) | RU2455570C1 (en) |
| WO (1) | WO2009121776A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105102894B (en) * | 2012-12-17 | 2017-07-11 | 安萨尔多能源公司 | Burner assembly, the combustion chamber including the burner assembly and the method for supplying fuel to the burner assembly |
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| US9366443B2 (en) * | 2013-01-11 | 2016-06-14 | Siemens Energy, Inc. | Lean-rich axial stage combustion in a can-annular gas turbine engine |
| US8794217B1 (en) | 2013-02-07 | 2014-08-05 | Thrival Tech, LLC | Coherent-structure fuel treatment systems and methods |
| JP6086860B2 (en) * | 2013-11-29 | 2017-03-01 | 三菱日立パワーシステムズ株式会社 | Nozzle, combustor, and gas turbine |
| US20150159877A1 (en) * | 2013-12-06 | 2015-06-11 | General Electric Company | Late lean injection manifold mixing system |
| US11156164B2 (en) | 2019-05-21 | 2021-10-26 | General Electric Company | System and method for high frequency accoustic dampers with caps |
| US11174792B2 (en) | 2019-05-21 | 2021-11-16 | General Electric Company | System and method for high frequency acoustic dampers with baffles |
| GB202013274D0 (en) * | 2020-08-25 | 2020-10-07 | Siemens Gas And Power Gmbh & Co Kg | Combuster for a gas turbine |
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-
2008
- 2008-04-01 EP EP08006666A patent/EP2107311A1/en not_active Withdrawn
-
2009
- 2009-03-26 ES ES09728642T patent/ES2417158T3/en active Active
- 2009-03-26 EP EP09728642.1A patent/EP2263044B1/en not_active Not-in-force
- 2009-03-26 CN CN2009801112622A patent/CN101981379B/en not_active Expired - Fee Related
- 2009-03-26 US US12/935,923 patent/US20110027728A1/en not_active Abandoned
- 2009-03-26 WO PCT/EP2009/053555 patent/WO2009121776A1/en active Application Filing
- 2009-03-26 RU RU2010144571/06A patent/RU2455570C1/en not_active IP Right Cessation
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105102894B (en) * | 2012-12-17 | 2017-07-11 | 安萨尔多能源公司 | Burner assembly, the combustion chamber including the burner assembly and the method for supplying fuel to the burner assembly |
Also Published As
| Publication number | Publication date |
|---|---|
| EP2263044B1 (en) | 2013-05-15 |
| EP2263044A1 (en) | 2010-12-22 |
| EP2107311A1 (en) | 2009-10-07 |
| US20110027728A1 (en) | 2011-02-03 |
| RU2455570C1 (en) | 2012-07-10 |
| RU2010144571A (en) | 2012-05-10 |
| CN101981379B (en) | 2012-06-20 |
| ES2417158T3 (en) | 2013-08-06 |
| WO2009121776A1 (en) | 2009-10-08 |
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