WO2006090466A1 - 燃料噴射弁とこれを用いた燃焼器及びその燃料噴射方法 - Google Patents
燃料噴射弁とこれを用いた燃焼器及びその燃料噴射方法 Download PDFInfo
- Publication number
- WO2006090466A1 WO2006090466A1 PCT/JP2005/003105 JP2005003105W WO2006090466A1 WO 2006090466 A1 WO2006090466 A1 WO 2006090466A1 JP 2005003105 W JP2005003105 W JP 2005003105W WO 2006090466 A1 WO2006090466 A1 WO 2006090466A1
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- WIPO (PCT)
- Prior art keywords
- fuel
- injection valve
- air
- fuel injection
- combustion
- Prior art date
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
- F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
- F02C7/22—Fuel supply systems
- F02C7/232—Fuel valves; Draining valves or systems
-
- 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
- F23R3/02—Continuous combustion chambers using liquid or gaseous fuel characterised by the air-flow or gas-flow configuration
- F23R3/04—Air inlet arrangements
- F23R3/10—Air inlet arrangements for primary air
- F23R3/12—Air inlet arrangements for primary air inducing a vortex
-
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T50/00—Aeronautics or air transport
- Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
Definitions
- the present invention relates to a fuel injection valve used in a combustor such as a gas turbine, a combustor using the same, and a fuel injection method thereof.
- NOx nitrogen oxides
- the main cause of NOx is so-called thermal NOx, in which nitrogen in the air is oxidized by a high-temperature flame during combustion. To reduce this thermal NOx, the hot spot in the flame is reduced. It is effective to suppress the occurrence of high-temperature flame. Therefore, conventionally, a low NOx combustor using a premixed fuel injection valve as described below has been proposed (for example, see Patent Document 1).
- FIG. 1 is an overall configuration diagram of a low-NOx combustor for a gas turbine equipped with a conventional premixed fuel injection valve.
- the conventional low NOx combustor 50 includes a no-rotner burner 58 disposed in the central portion and a plurality of main burners 59 disposed around the center.
- 52 is a combustor liner
- 53 is a casing
- 54 is a spark plug (idaniter)
- air 56 flows between the casing 53 and the liner 52 to reach the burners 58 and 59.
- the other part flows into the liner 52 to form flames 57a and 57b, and the generated combustion gas is guided to the gas turbine through the scroll portion, not shown, to drive it. It has become.
- the main burner 59 includes a main injection valve 59a and a premixing tube 59b arranged coaxially with each other.
- the main injection valve 59a is also supplied with fuel by external force through the casing 53.
- As this fuel for example, gas fuel is used.
- the premixing tube 59b is It is a cylindrical tube with an open end that facilitates mixing of fuel and air inside. That is, the main burner 59 is a premixed lean burner composed of a main injection valve 59a and a premixing tube 59b.
- fuel can be injected into the premixing pipe 59b by the main injection valve 59a, and the fuel can be premixed with a sufficient amount of air in the premixing pipe 59b, and this can be burnt lean.
- the fuel is premixed with a sufficient amount of air and this is burnt in a lean manner, which eliminates the generation of high-temperature flames with hot spots and achieves low NOx emissions. There are merits such as being able to do.
- FIG. 2 is a diagram showing another example of a conventional low-NOx combustor using a lean premixed combustion method.
- a swirl vane 62 is provided in a mainstream gas flow path 61 through which a large amount of air flows, whereby air flowing in the axial direction of the combustor is introduced into the combustion chamber 63 as a spiral flow, while fuel A gas is ejected in the axial direction toward the combustion chamber, and a large amount of air in a spiral flow and fuel gas are mixed and ignited to perform combustion.
- the low-NOx combustor with a lean lean premixed combustion system has a problem that stable combustion of lean fuel gas is difficult, and flashback and vibration combustion are likely to occur. Moreover, although low NOx emissions can be obtained by lean premixed combustion, there is a problem that the CO concentration tends to be high due to the low flame temperature.
- Non-patent Document 1 In order to avoid such problems of the lean premixed combustion method, a low combustion NOx combustor using a swirling flame has been proposed (for example, [Non-patent Document 1]).
- FIGS. 3A and B In Asymmetric Whirl Combustion of [Non-Patent Document 1], as shown in FIGS. 3A and B, air connected to a side surface near one end of a cylindrical frame tube 71 having a combustion space therein. By blowing air from the jet pipe 72 in the tangential direction of the frame tube to make a swirl flow, and by jetting fuel gas from the fuel gas supply pipe 73 connected to one end face of the frame tube in the axial direction of the frame tube, It promotes mixing of air and fuel gas to reduce NOx in combustion exhaust gas.
- This asymmetric swirl combustor 70 is different from a conventional swirl (swivel) having a large axial flow velocity in that the air flow does not have an axial component. For this reason, the swirl flame that is formed exhibits a kind of exhaust gas circulation action, and can achieve a low NOx concentration, and has high flame holding properties and stable combustion.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2002-130675
- Non-Patent Document 1 H. C. Gabler, et al. "Asymmetric Whirl Combustion: A
- the above-described conventional premixed combustion type combustor has a problem that backfire, self-ignition, or combustion vibration occurs. That is, as described above, in order to achieve low NOx in this combustor, it is necessary to perform premix combustion, but the premixing section (prevaporization premixing pipe 59b) for mixing air and fuel and combustion Since the area is directly connected by the premixed flow path, if the flow velocity of the premixed gas flowing through the premixed flow path is slower than the combustion speed, the flame in the combustion area flashes back into the premixed flow path. There was a problem.
- an object of the present invention is to provide a fuel injection valve that can essentially prevent backfire, self-ignition and vibration combustion, and can realize low NOx, a combustor using the fuel injection valve, and a fuel injection method thereof. It is in.
- a cylindrical injection valve main body whose one end is closed, and a fuel nozzle that is disposed on the central axis of the injection valve main body and injects fuel.
- the cylindrical portion has a plurality of air injection ports in the circumferential direction for injecting air inwardly in the tangential direction and forming a swirling flow therein, and the fuel nozzle is directed toward the inner peripheral surface of the injection valve body.
- a fuel injection valve characterized by having a fuel injection port for injecting fuel is provided.
- air is injected tangentially inward from an air injection port provided in the injection valve main body to form a strong swirl flow, and on the central axis of the injection valve main body. Because the fuel is injected radially outward, that is, the inner peripheral surface of the injection valve body, the fuel that collided with the inner peripheral surface is injected by the air injection locuser. Air (strong swirl flow) can instantly produce fine particles and rapidly mix fuel. This effectively prevents the occurrence of flashback, self-ignition, and vibration combustion without the need for a premixing part like a conventional premixing type fuel injection valve, and achieves low NOx combustion. it can.
- the fuel injection port is disposed so as to inject fuel between the air injection ports adjacent to each other.
- the injected fuel is atomized by the strong swirl flow described above in the region of the strong shear field formed in the vicinity of the outer peripheral portion of the injection valve body. Promotes rapid mixing and ensures flashback, self-ignition and combustion vibrations. Suppression is improved.
- the fuel nozzle preferably has a diffusion injection port for diffusing and injecting fuel from the central axis of the injection valve body.
- the fuel is diffused and rapidly injected from the diffusion injection port even under conditions where combustion is relatively unstable, such as ignition and low load!
- combustion is relatively unstable, such as ignition and low load!
- a combustor including a combustion chamber for forming a flame and the fuel injection valve upstream of the combustion chamber.
- the combustor of the present invention includes a fuel injection valve that rapidly mixes fuel with a strong swirl flow! /, thus effectively preventing the occurrence of backfire, self-ignition and combustion vibration, and low NOx combustion can be realized.
- air is injected inwardly in the tangential direction from the air injection port provided in the injection valve body to form a strong swirl flow, and the inside of the injection valve body Fuel is injected radially outward from the fuel nozzle force arranged on the mandrel, that is, the inner peripheral surface of the injection valve body, so that the fuel colliding with the inner peripheral surface is injected from the air injection port.
- the air strong swirl flow
- the air can be instantly atomized and the fuel can be rapidly mixed, which makes it unnecessary to provide a premixing part like a conventional premixing type fuel injection valve. It has excellent effects such as effective prevention of self-ignition and combustion vibration and low NOx combustion.
- a hollow cylindrical injection valve body having one end opened to the combustion chamber and the other end closed, and fuel attached to the central axis of the other closed end of the injection valve body
- a fuel injection nozzle that injects with air, and the injection valve main body includes a plurality of air introduction ports that introduce combustion air inwardly in the vicinity of the inner wall of the cylindrical portion to form a strong swirl flow therein.
- the fuel injection valve is characterized in that a strong shear region in the outer peripheral portion where a flame extension is caused by the strong swirl flow and a rigid vortex region in the central portion are formed.
- a combustor comprising a combustion chamber for forming a flame and the fuel injection valve upstream of the combustion chamber.
- a hollow cylindrical injection valve having one end opened to the combustion chamber and the other end closed. Fuel is injected into the main body alone or with air, and combustion air is introduced tangentially inward in the vicinity of the inner wall of the cylindrical portion of the injection valve body to form a strong swirl flow inside, which causes flame extension due to the strong swirl flow.
- a fuel injection method characterized by forming a strong shear region at the outer peripheral portion and a rigid vortex region at the central portion.
- fuel is injected into the strong shear region, mixing of air and fuel is promoted by strong disturbance, and extinguishing action due to flame extension acting thereon. This prevents the formation of a flame in the mixing region, forms a uniform lean air-fuel mixture, and forms a stable flame by the backflow region formed at the center by the rigid body vortex region to hold the flame.
- low NOx combustion is achieved by a uniform lean mixture close to premixed combustion formed in a strong shear region, and also due to flame extension occurring in the mixing region.
- the flame extinguishing action prevents back-fired self-ignition in the air-Z fuel mixing section, such as premixed combustion, even at high temperatures and pressures, preventing combustor burnout and increased NOx.
- the stable flame in the center of the injection valve formed in the backflow region becomes a flame-holding source for low NOx flames close to the premixed flame formed in the outer periphery, and stable combustion is possible without the need for a pilot burner. Can be maintained.
- the flame extinguishing action caused by the flame extension occurring in the mixed region can essentially prevent backfire, self-ignition and vibration combustion, and low NOx emission can be realized.
- FIG. 1 is an overall configuration diagram of a conventional fuel injection valve and a combustor equipped with the same.
- FIG. 2 is a schematic configuration diagram of a conventional low-NOx combustor using a lean premixed combustion method.
- FIG. 3 A and B are schematic configuration diagrams of a conventional low-NOx combustor of an asymmetric swirl combustion method.
- Fig. 3 is an overall configuration diagram of a combustor including a fuel injection valve according to the present invention.
- FIG. 5A is a structural diagram of an embodiment of a fuel injection valve according to the present invention.
- FIG. 5B is a view taken along arrows 5B-5B in FIG. 5A.
- FIG. 6 is a diagram showing a radial velocity distribution of a circumferential velocity component of a strong swirling flow.
- FIG. 7 is a fuel injection valve according to another embodiment of the present invention.
- FIG. 8 is an embodiment of the low NOx injection valve of the present invention.
- FIG. 9 A, B and C are explanatory views of the operation of the low NOx injection valve of the present invention.
- FIG. 4 is an overall configuration diagram of a combustor including a fuel injection valve according to the present invention.
- the combustor 1 shown in FIG. 4 includes a pilot burner 8 disposed upstream and in the center of the combustion chamber 15, and a plurality of (for example, six) fuel injection valves 10 (main) disposed on the concentric circles of the pilot burner. Pana).
- 2 is a combustor liner
- 3 is a casing
- 4 is a hydrant.
- the air 6 flows between the casing 3 and the liner 2 and reaches the pilot burner 8 and the fuel injection valve 10, and flows into the combustion chamber 15 through the fuel injection valve 10 and other parts to enter the flame 7 a, 7b is formed, and the combustion gas generated in the combustion chamber 15 is guided to a gas turbine (not shown) through a scroll portion (not shown) to drive it.
- FIG. 5A is a structural diagram of an embodiment of the fuel injection valve 10 according to the present invention
- FIG. 5B is a view taken along arrows 5B-5B.
- the fuel injection valve 10 includes a cylindrical injection valve main body 11 and a fuel nozzle 13 with one end (rear end) closed.
- the other end portion (tip portion) of the injection valve main body 11 has an opening bent outward in the radial direction.
- the injection valve body 11 has six air injection ports 12 on the outer periphery along the circumferential direction.
- the air injection ports 12 inject air in the tangential direction from the outside of the injection valve to the inside of the injection valve.
- the force with six air injection ports 12 is not limited to this, and it is possible to arrange less or more than this.
- the fuel nozzle 13 is disposed on the central axis of the injection valve main body 11 and has a fuel injection port 14 that injects fuel toward the inner peripheral surface of the injection valve main body 11. Further, the fuel nozzle 13 is configured to inject the fuel 5 in the direction between the air injection ports 12 adjacent to each other.
- the fuel 5 is injected from the fuel injection port 14 of the fuel nozzle 13 toward the inner peripheral surface of the injection valve body 11. When hit, the fuel 5 collides with the inner wall and forms a fuel liquid film. On the other hand, the air 6 introduced from the air injection port 12 forms a strong swirl flow inside the injection valve. The fuel liquid film is atomized by a strong swirling flow at the lip portion 12a at the outlet of the air injection port 12.
- Fig. 6 shows the radial velocity distribution of the circumferential velocity component of the strong swirling flow formed when air is injected from the air injection port 12 in the fuel injection valve 10 of the present invention. It is. As is apparent from FIG. 6, the radial velocity distribution has a large velocity gradient in the vicinity of the outer periphery of the injection valve body 11, and this region is a strong shear field. Therefore, the fuel 5 atomized by the lip portion 12a at the outlet 12 of the air injection port 12 is just supplied to this strong shear site, and this strong shear promotes atomization and mixing, A uniform gas mixture can be formed even in a relatively small volume in a short time. This air-fuel mixture advances toward the combustion region while rotating at a high speed with a strong whirling flow, and forms a flame in the combustion region.
- the air-fuel mixture that travels with the strong swirl flow has an absolute velocity higher than the combustion velocity, so there is no possibility of causing backfire.
- the mixing region and the mixing time are short, it is possible to further suppress the occurrence of combustion vibration without the possibility of generating self-ignition. In other words, it is possible to prevent the occurrence of flashback and self-ignition, reduce the generation of combustion vibrations, and realize low NOx combustion without providing a long premixing part like a conventional premixing type fuel injection valve be able to.
- the combustor in the present embodiment is provided with the pilot burner 8. As described above, the combustion of the flame is stabilized according to the present invention, and therefore the pilot burner 8 is not necessarily provided.
- FIG. 7 is a structural diagram of the fuel injection valve 20 according to the second embodiment of the present invention.
- a diffusion injection port 23 for diffusing and injecting fuel is provided at the tip of the fuel nozzle 21 located on the central axis of the injection valve body. Speak. Since other configurations are the same as those of the first embodiment described above, description thereof is omitted. By adopting such a configuration, it is not necessary to provide a pilot partner as in the first embodiment. For example, even under conditions where combustion is relatively unstable, such as ignition and low load, diffusion is performed. By diffusing and injecting fuel from the injection port to assist combustion of the air-fuel mixture by rapid mixing Thus, more stable combustion is possible.
- FIGS. 8A and 8B are embodiments of the low NOx injection valve according to the third embodiment of the present invention.
- FIG. 8A is a cross-sectional view
- FIG. 8B is a cross-sectional view of 8B-8B.
- the fuel injection valve 30 of the present invention includes an injection valve main body 32 and a fuel injection nozzle 34.
- the injection valve main body 32 is a hollow cylindrical member having one end 32a opened to the combustion chamber 41 and the other end 32b closed.
- the injection valve body 32 includes a plurality (four in this example) of air introduction ports 33 in the vicinity of the inner wall of the cylindrical portion, and introduces combustion air inwardly in the tangential direction to form a strong swirl flow 42 inside.
- the strong swirl flow 42 forms a strong shear region 43 that causes flame extension and a rigid vortex region 4 in the center as shown in FIG. 8B.
- the fuel injection nozzle 34 is a nozzle that is attached on the central axis of the other closed end 32b of the injection valve main body 32 and injects fuel together with air.
- the rigid vortex region 44 in the central part forms a circulating flow 46 in which the combustion gas circulates in the central part, and a stable flame holding source 47 is formed in the rigid vortex region 44.
- the flow rate and flow rate of the air introduced from the air introduction port 33 are set so that a uniform lean mixture 45 and a circulation flow 46 are formed by the strong shear region 43 and the rigid vortex region 44. It is good.
- the fuel injection method of the present invention uses the low NOx injection valve 30 described above, and the fuel is used alone or in a hollow cylindrical injection valve body 32 having one end opened to the combustion chamber 41 and the other end closed. Injected with air, combustion air is introduced tangentially inward in the vicinity of the inner wall of the cylindrical portion of the injection valve body 32 to form a strong swirl flow 42 inside, and the strong swirl flow 42 causes flame extension. A shear region 43 and a central rigid vortex region 44 are formed.
- fuel is injected into the strong shear region 42 to promote the mixing of air and fuel by strong turbulence, and in the mixing region 43 by the extinguishing action due to the flame extension acting thereon.
- a uniform lean mixture 45 is formed by preventing the formation of a flame, and a stable flame holding source 47 is formed and held by a circulating flow 46 formed in the center by a rigid vortex region 44.
- FIGS. 9A, 9B, and 9C are operation explanatory views of the low NOx injection valve of the present invention.
- FIG. 9A is a schematic diagram showing the development state of the jet along the wall surface
- FIG. 9C is a schematic diagram of the rigid vortex region 44.
- Fig. 9A the velocity distribution in the central portion of the jet immediately after the nozzle force flows along the wall surface is uniform, but this uniform velocity portion is eroded and reduced by the boundary layer that develops both-side forces, It disappears at a certain distance.
- This part is wedge-shaped and is called the potential core.
- the distribution of velocity and turbulence changes even in the fully developed region after the disappearance of the potential core, and these distribution shapes are similar enough downstream.
- the length of the potential core is about 5-8d, where d is the nozzle height or diameter.
- the potential core region or the fully developed region in a strong swirl flow is divided into a region with free vortex properties (Fig. 9B) and a region with forced vortex properties (Fig. 9C) at the peak of the maximum velocity.
- a region with free vortex properties Fig. 9B
- a region with forced vortex properties Fig. 9C
- mixing is significantly accelerated by shear. Accordingly, when fuel is injected into this region, flame extension occurs and the flame lump is cooled in a short time, so that it can be prevented from igniting.
- the swirling flame that is formed exhibits a kind of exhaust gas circulation action, which can achieve both low NOx and a reduction in the amount of CO generated. Highly stable and stable combustion is possible.
- low NOx combustion can be realized by the homogeneous lean air-fuel mixture 45 close to the premixed combustion formed in the strong shear region 43.
- the flame extinguishing action caused by the flame extension occurring in the mixing zone 43 prevents back-fire and self-ignition in the air Z fuel mixing section, such as premixed combustion, even at high temperatures and high pressures. Increase can be prevented.
- the stable flame in the center of the injection valve formed in the backflow region 46 becomes a flame holding source 47 of a low NOx flame close to the premixed flame formed in the outer periphery, and it is stable without the need for a pilot pan. Can maintain combustion.
- the flame extinguishing action caused by the flame extension occurring in the mixed region can essentially prevent backfire, self-ignition and vibration combustion, and low NOx emission can be realized.
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/817,195 US20090031729A1 (en) | 2005-02-25 | 2005-02-25 | Fuel injection valve, combustor using the fuel injection valve, and fuel injection method for the fuel injection valve |
CA2599113A CA2599113C (en) | 2005-02-25 | 2005-02-25 | Fuel injection valve, combustor using the fuel injection valve, and fuel injection method for the fuel injection valve |
EP05719506A EP1852657A4 (en) | 2005-02-25 | 2005-02-25 | FUEL INJECTION VALVE, COMBUSTION CHAMBER USING SAID VALVE, AND FUEL INJECTION METHOD FOR SAID VALVE |
PCT/JP2005/003105 WO2006090466A1 (ja) | 2005-02-25 | 2005-02-25 | 燃料噴射弁とこれを用いた燃焼器及びその燃料噴射方法 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2005/003105 WO2006090466A1 (ja) | 2005-02-25 | 2005-02-25 | 燃料噴射弁とこれを用いた燃焼器及びその燃料噴射方法 |
Publications (1)
Publication Number | Publication Date |
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WO2006090466A1 true WO2006090466A1 (ja) | 2006-08-31 |
Family
ID=36927117
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PCT/JP2005/003105 WO2006090466A1 (ja) | 2005-02-25 | 2005-02-25 | 燃料噴射弁とこれを用いた燃焼器及びその燃料噴射方法 |
Country Status (4)
Country | Link |
---|---|
US (1) | US20090031729A1 (ja) |
EP (1) | EP1852657A4 (ja) |
CA (1) | CA2599113C (ja) |
WO (1) | WO2006090466A1 (ja) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100886190B1 (ko) * | 2007-11-12 | 2009-02-27 | 한국에너지기술연구원 | 탈질공정을 갖는 엔진 열병합발전소 배기가스 환원분위기조성용 버너 |
FR2945854B1 (fr) | 2009-05-19 | 2015-08-07 | Snecma | Vrille melangeuse pour un injecteur de carburant dans une chambre de combustion d'une turbine a gaz et dispositif de combustion correspondant |
JP2013178003A (ja) * | 2012-02-28 | 2013-09-09 | Ihi Corp | バーナ及びこのバーナを備えたガスタービン燃焼器 |
JP5818945B2 (ja) * | 2014-05-20 | 2015-11-18 | 三菱日立パワーシステムズ株式会社 | ガスタービンの制御方法及びガスタービンの燃空比設定方法 |
CN104566467B (zh) * | 2014-12-31 | 2018-02-23 | 北京华清燃气轮机与煤气化联合循环工程技术有限公司 | 一种防回火型喷嘴 |
CN115127121B (zh) * | 2022-06-15 | 2024-01-12 | 北京航空航天大学 | 稳焰预混燃烧装置及航空发动机模拟试验设备 |
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JPH11257664A (ja) * | 1997-12-30 | 1999-09-21 | United Technol Corp <Utc> | ガスタ―ビンエンジンの燃料噴射ノズル/ガイドアセンブリ |
JP2004093076A (ja) * | 2002-09-04 | 2004-03-25 | Ishikawajima Harima Heavy Ind Co Ltd | 拡散燃焼方式低NOx燃焼器 |
JP2004340416A (ja) * | 2003-05-13 | 2004-12-02 | Ishikawajima Harima Heavy Ind Co Ltd | 急速混合燃料噴射弁及び低NOx燃焼器 |
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JPS5857655B2 (ja) * | 1976-08-27 | 1983-12-21 | 株式会社日立製作所 | ガスタ−ビン用燃焼器 |
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JPS56124834A (en) * | 1980-03-05 | 1981-09-30 | Hitachi Ltd | Gas-turbine combustor |
DE4110507C2 (de) * | 1991-03-30 | 1994-04-07 | Mtu Muenchen Gmbh | Brenner für Gasturbinentriebwerke mit mindestens einer für die Zufuhr von Verbrennungsluft lastabhängig regulierbaren Dralleinrichtung |
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GB2337102A (en) * | 1998-05-09 | 1999-11-10 | Europ Gas Turbines Ltd | Gas-turbine engine combustor |
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DE10040869A1 (de) * | 2000-08-21 | 2002-03-07 | Alstom Power Nv | Verfahren und Vorrichtung zur Unterdrückung von Strömungswirbeln innerhalb einer Strömungskraftmaschine |
US20020162333A1 (en) * | 2001-05-02 | 2002-11-07 | Honeywell International, Inc., Law Dept. Ab2 | Partial premix dual circuit fuel injector |
US7143583B2 (en) * | 2002-08-22 | 2006-12-05 | Hitachi, Ltd. | Gas turbine combustor, combustion method of the gas turbine combustor, and method of remodeling a gas turbine combustor |
US6976363B2 (en) * | 2003-08-11 | 2005-12-20 | General Electric Company | Combustor dome assembly of a gas turbine engine having a contoured swirler |
US7065972B2 (en) * | 2004-05-21 | 2006-06-27 | Honeywell International, Inc. | Fuel-air mixing apparatus for reducing gas turbine combustor exhaust emissions |
JP4626251B2 (ja) * | 2004-10-06 | 2011-02-02 | 株式会社日立製作所 | 燃焼器及び燃焼器の燃焼方法 |
JP5023526B2 (ja) * | 2006-03-23 | 2012-09-12 | 株式会社Ihi | 燃焼器用バーナ及び燃焼方法 |
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2005
- 2005-02-25 CA CA2599113A patent/CA2599113C/en active Active
- 2005-02-25 WO PCT/JP2005/003105 patent/WO2006090466A1/ja active Application Filing
- 2005-02-25 US US11/817,195 patent/US20090031729A1/en not_active Abandoned
- 2005-02-25 EP EP05719506A patent/EP1852657A4/en not_active Ceased
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH11257664A (ja) * | 1997-12-30 | 1999-09-21 | United Technol Corp <Utc> | ガスタ―ビンエンジンの燃料噴射ノズル/ガイドアセンブリ |
JP2004093076A (ja) * | 2002-09-04 | 2004-03-25 | Ishikawajima Harima Heavy Ind Co Ltd | 拡散燃焼方式低NOx燃焼器 |
JP2004340416A (ja) * | 2003-05-13 | 2004-12-02 | Ishikawajima Harima Heavy Ind Co Ltd | 急速混合燃料噴射弁及び低NOx燃焼器 |
Also Published As
Publication number | Publication date |
---|---|
EP1852657A4 (en) | 2012-02-29 |
EP1852657A1 (en) | 2007-11-07 |
CA2599113C (en) | 2011-11-22 |
US20090031729A1 (en) | 2009-02-05 |
CA2599113A1 (en) | 2007-08-24 |
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