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WO2018133292A1 - Buse à rapports d'équivalence de canaux d'écoulement interne et externe réglables, réseau de buses et brûleur - Google Patents

Buse à rapports d'équivalence de canaux d'écoulement interne et externe réglables, réseau de buses et brûleur Download PDF

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Publication number
WO2018133292A1
WO2018133292A1 PCT/CN2017/087611 CN2017087611W WO2018133292A1 WO 2018133292 A1 WO2018133292 A1 WO 2018133292A1 CN 2017087611 W CN2017087611 W CN 2017087611W WO 2018133292 A1 WO2018133292 A1 WO 2018133292A1
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WIPO (PCT)
Prior art keywords
wave
nozzle
cylinder
cyclone
embedded
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.)
Ceased
Application number
PCT/CN2017/087611
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English (en)
Chinese (zh)
Inventor
李钢
徐纲
尹娟
卢新根
朱俊强
杜薇
穆勇
刘存喜
刘富强
杨金虎
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Institute of Engineering Thermophysics of CAS
Original Assignee
Institute of Engineering Thermophysics of CAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Institute of Engineering Thermophysics of CAS filed Critical Institute of Engineering Thermophysics of CAS
Publication of WO2018133292A1 publication Critical patent/WO2018133292A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/26—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid with provision for a retention flame
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details
    • F23D14/48—Nozzles
    • F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details
    • F23D14/62—Mixing devices; Mixing tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details
    • F23D14/70—Baffles or like flow-disturbing devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/007—Mixing tubes, air supply regulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/14—Special features of gas burners
    • F23D2900/14241—Post-mixing with swirling means

Definitions

  • the present disclosure relates to the field of combustion device technology, and more particularly to a nozzle, a nozzle array and a burner with adjustable internal and external flow passage equivalent ratios, which are particularly suitable for various industrial burners such as gas turbines, boilers, and chemical furnaces.
  • the equivalence ratio is an important parameter of the nozzle and the burner, which has an important influence on the combustion performance. Different equivalence ratios are directly related to combustion stability and pollutant discharge. The equivalence ratio needs to be adjusted for different working conditions in order to improve combustion. performance. Therefore, there is a need in the art to develop a burner having an adjustable internal and external flow passage equivalent ratio.
  • the present disclosure provides a nozzle having an adjustable internal and external flow passage equivalent ratio, comprising: an intermediate cylinder, an outer wall cylinder and a wave cyclone; wherein the wave cyclone is coaxially disposed in the outer wall cylinder;
  • the intermediate cylinder is embedded in the wave cyclone in the axial direction of the wave cyclone by the outlet end of the wave cyclone, and the wave cyclone is divided into an inner ring swirling structure and an outer ring a swirling structure;
  • the outer ring swirling structure, the intermediate cylinder and the outer wall cylinder enclose an outer flow passage, the inner ring swirling structure and the intermediate cylinder enclosing an inner flow passage;
  • the intermediate cylinder is embedded with a wave swirling flow
  • the portion of the device is an embedded segment that is a non-cylindrical structure to adjust the equivalence ratio of the inner flow passage and the outer flow passage.
  • the wave cyclone is formed by circumferentially arranging a plurality of peaks and a plurality of valleys undulating in a radial direction;
  • the embedded section is a toothed structure, the toothed structure
  • a plurality of strip-shaped sheets arranged in a circumferential direction are formed, and grooves are formed between adjacent strip-shaped sheets.
  • the groove corresponds to the trough position
  • the strip piece corresponds to the peak position
  • the groove corresponds to the peak position, the strip piece Corresponding to the trough position.
  • the strip is provided with a through hole.
  • the strips and grooves are elongated, sinusoidal, square, triangular or polygonal.
  • the wave cyclone is formed by circumferentially arranging a plurality of peaks and a plurality of valleys undulating in a radial direction; the embedded section is a wave structure, and the wave structure is A plurality of peaks and a plurality of troughs of radial undulations are arranged circumferentially.
  • the trough of the embedded segment corresponds to a peak position of the wave cyclone
  • the peak of the embedded segment corresponds to a trough position of the wave cyclone
  • the trough of the embedded segment The valley position of the wave cyclone corresponds to the peak of the embedded segment corresponding to the peak position of the wave cyclone.
  • the crests and troughs of the wave structure are open with through holes.
  • the cross-sectional profile of the wave structure is a sinusoidal waveform, a square waveform, a triangular waveform, or a polygonal waveform.
  • some or all of the inner ring swirling structure is trimmed in the axial direction, and the upstream section of the wave swirler forms a cavity.
  • a mesh plate is further included, the mesh plate is disposed in the intermediate cylinder, and an inner blending zone is formed between the outlet end of the wave cyclone, and the inner blending zone The inner flow path is connected.
  • the outer wall cylinder protrudes in the downstream direction from the intermediate cylinder, and the outer wall cylinder, the outlet end of the wave cyclone and the intermediate cylinder enclose an outer mixing zone, the outer The blending zone is in communication with the outer flow channel, the portion of the outer wall cylinder projecting from the intermediate cylinder forming an outlet blending zone.
  • the through holes are circular, elliptical, triangular, or polygonal.
  • the intermediate cylinder is embedded in the wave swirler to a depth that is half the diameter of the outer wall cylinder.
  • the present disclosure also provides an array of nozzles comprising a plurality of the above-described nozzles, the array of nozzles being a circular array or a rectangular array.
  • the present disclosure also provides a burner comprising the above described nozzle or array of nozzles.
  • the inner and outer flow passage equivalent ratio of the nozzle, the nozzle array and the burner are adjustable, and the embedded section of the middle cylinder embedded in the wave cyclone is a wave structure or a tooth structure, and the embedded section can also be Opening a through hole can adjust the equivalence ratio of the inner flow channel and the outer flow channel, reduce the flame propagation speed, avoid tempering in the middle portion of the nozzle outlet, and widen the tempering margin of the nozzle.
  • FIG. 1 is a half cross-sectional view of a nozzle having an adjustable internal and external flow passage equivalent ratio according to a first embodiment of the present disclosure
  • Figure 2 is a plan view of the nozzle shown in Figure 1;
  • Figure 3 is a three-dimensional view of the nozzle shown in Figure 1 with the outer wall cylinder omitted;
  • Figure 4 is a schematic view of the intermediate cylinder of the nozzle of Figure 1;
  • Figure 5 is a schematic view showing a combined structure of the intermediate cylinder and the wave cyclone shown in Figure 4;
  • Figure 6 is a schematic view showing another combined structure of the intermediate cylinder and the wave cyclone shown in Figure 4;
  • Figure 7 is a schematic view showing the size of the nozzle shown in Figure 1;
  • Figure 8 is a schematic view showing the axial dimension of the nozzle shown in Figure 1;
  • Figure 9 is a schematic view of an intermediate cylinder of a nozzle according to a second embodiment of the present disclosure.
  • Figure 10 is a sectional view of Figure 9 along the axial position
  • Figure 11 is a schematic view showing a combined structure of the intermediate cylinder and the wave cyclone shown in Figure 9;
  • Figure 12 is a schematic view showing another combined structure of the intermediate cylinder and the wave cyclone shown in Figure 9;
  • Figure 13 is a schematic view of an intermediate cylinder of a third embodiment of the present disclosure.
  • Figure 14 is a schematic view of an intermediate cylinder of a fourth embodiment of the present disclosure.
  • a first embodiment of the present disclosure provides a nozzle having an adjustable internal and external flow passage equivalent ratio, comprising: an intermediate cylinder 6, an outer wall cylinder 3, a mesh plate 8, and a wave swirling structure.
  • the wave swirling structure is located in the outer wall cylinder 3 and is disposed coaxially with the outer wall cylinder 3; the wave swirling structure comprises a wave swirler 5 and a support cylinder 4, and the wave swirler 5 is surrounded by a plurality of peaks undulating in the radial direction 51 and a plurality of troughs 52 are arranged in the circumferential direction, and the circumferentially arranged troughs 52 enclose an inscribed circle, and an inscribed circular space is formed in the center of the wave cyclone 5, and the circumferentially arranged peaks 51 are formed outside.
  • the wave cyclone 5 is transiently connected to the support cylinder 4 from the downstream to the upstream direction.
  • the intermediate cylinder 6 is inserted into the wave swirler 5 in the axial direction of the wave cyclone 5 from the outlet end of the wave swirler 5, the diameter of the intermediate cylinder 6 being between the diameter of the inscribed circle and the diameter of the circumscribed circle, which will
  • the wave cyclone 5 is divided into two parts: an inner ring swirling structure 13 and an outer ring swirling structure 14, and the outer ring swirling structure 14, the intermediate cylinder 6 and the outer wall cylinder 3 enclose an outer flow passage, and the inner ring swirling structure 13
  • the inner cylinder 6 is surrounded by the inner cylinder.
  • the mesh plate 8 is disposed in the intermediate cylinder 6, and the inner mixing zone 7 is formed between the mesh plate 8 and the outlet end of the wave cyclone 5, and the inner mixing zone 7 is in communication with the inner flow passage, and the outer wall cylinder 3 is along
  • the downstream direction protrudes from the intermediate cylinder 6, and the outer wall cylinder 3, the outlet end of the wave cyclone 5 and the intermediate cylinder 6 enclose an outer mixing zone 9, the outer mixing zone 9 communicates with the outer flow channel, and the outer wall cylinder 3 protrudes.
  • An outlet blending zone 11 is formed in a portion of the intermediate cylinder 6.
  • the fuel and air are not blended before entering the nozzle, and the intermediate cylinder inlet 1 may be a fuel inlet or an air inlet.
  • the outer cylinder inlet 2 may also be a fuel inlet or an air inlet.
  • fuel and air must be blended together.
  • the fuel is introduced into the intermediate cylinder inlet 1 and the inlet of the outer cylinder inlet 2 is taken as an example.
  • the fuel enters the nozzle from the intermediate cylinder inlet 1 and enters the wave cyclone 5 through the support cylinder 4, and a part of the fuel flows into the inner flow passage.
  • the air enters the nozzle from the outer wall cylinder inlet 2, part of the air flows into the inner flow passage, part of the air flows into the outer flow passage, and the fuel and air flowing into the inner flow passage enter the inner mixing zone 7 to be blended into a swirling combustible mixture.
  • the fuel and air flowing into the outer flow passage enter the outer mixing zone 9 to be blended into a swirling combustible mixture, and the mesh plate 8 serves as a filtering action. After the spinning mixture of the inner blending zone 7 passes through the mesh plate 8, the rotation thereof The motion is filtered to become a spin-free combustible mixture.
  • the non-rotating combustible mixture flows out through the intermediate cylinder outlet zone 10, it is blended with the swirling combustible mixture flowing out of the outer mixing zone 9 in the outlet blending zone 11 and exited by the nozzle. 12 sprayed out to burn.
  • the combustible mixture of the outer blending zone 9 has a rotary motion
  • the combustible mixer forms an expanding flame at the nozzle outlet 12 under the action of centrifugal force, thereby improving the stability of combustion, and the intermediate cylinder outlet region 10 flows out.
  • the combustible material is a non-rotating axial movement, which prevents a strong recirculation zone from being formed at the nozzle outlet, reduces flow loss, and reduces pollutant emission.
  • the nozzle of the present disclosure has both good combustion stability and low pollutant emission. .
  • the operation of the nozzle is similar to the above process, and will not be described herein.
  • Figure 4 shows the specific structure of the intermediate cylinder 6 of the nozzle of Figures 1 to 3.
  • the portion of the intermediate cylinder 6 embedded in the wave cyclone 5 is an embedded section.
  • the embedded section is a toothed structure including a plurality of strips 16 arranged in the circumferential direction.
  • a groove 17 is formed between adjacent strips 16.
  • the embedded section of the tooth structure can adjust the equivalence ratio of the inner and outer flow channels, and at the same time reduce the nozzle weight and reduce the flow friction loss.
  • the groove 17 of the tooth structure corresponds to the position of the trough 52 of the wave cyclone, i.e. the groove 17 is located in the trough 52 of the wave cyclone.
  • the strip-shaped strip 16 of the toothed structure corresponds to the position of the crest 51 of the wave cyclone, i.e. the strip piece 16 is located within the crest 51 of the wave cyclone.
  • the groove 17 of the tooth structure corresponds to the position of the peak 51 of the wave cyclone, that is, the groove 17 is located in the wave swirl Within the crests 51 of the device; the strips 16 of the toothed structure correspond to the locations of the troughs 52 of the wave cyclone, i.e., the strips 16 are located within the troughs 52 of the wave cyclone.
  • the intermediate cylinder inlet 1 is an air inlet and the outer wall cylinder inlet 2 is a fuel inlet
  • the groove 17 increases the fuel flow rate into the outer flow passage and increases the equivalence ratio of the outer flow passage mixture as compared with the straight cylindrical embedded portion. The equivalent ratio of the inner flow path is reduced.
  • the nozzle Since the nozzle is tempered, it is mostly triggered from the middle area of the nozzle outlet. If the equivalent ratio of the mixture in the middle area is small, the flame propagation speed is low, and tempering can be avoided in the middle portion of the nozzle outlet, so that the nozzle and its burner can be widened.
  • the tempering margin, the embedding section of the above-mentioned tooth structure can reduce the equivalence ratio of the inner flow passage, thereby reducing the flame propagation speed and avoiding tempering in the middle portion of the nozzle outlet, thereby widening the tempering margin of the nozzle.
  • the strips 16 are elongated in shape, and the grooves 17 are also elongated, and the strips 16 and grooves 17 may also be sinusoidal, square, triangular, polygonal, preferably square.
  • the cross-sectional profile of the inlet end of the swirling waver may be a circular or polygonal ring shape, preferably a circular shape; the cross-sectional profile of the outlet end of the swirling wave device may be a sinusoidal waveform, a square waveform, a triangular waveform, and a square with a rounded chamfer.
  • Waveform; the guide line of the swirling waver is a straight line or a curve.
  • the inner flow channel and the outer flow channel are oblique flow channels, and fuel and air are respectively on both sides of the wave cyclone, and a circular rotation motion is generated under the action of the oblique flow channel, and the fuel and air are mixed at the outlet of the wave cyclone Mixed.
  • the angle between the oblique flow channel and the axial direction ranges from -90° to 0°, preferably from -30° to -60°; or the direction of rotation of the diagonal flow channel
  • the angle between the oblique flow passage and the axial direction ranges from 0 to 90, preferably from 30 to 60.
  • the diameter of the outer wall cylinder is A
  • the diameter of the intermediate cylinder is B
  • the diameter of the inscribed circle of the wave cyclone 5 is C
  • the cross-sectional profile of the intermediate cylinder 6 may be circular, triangular, polygonal, preferably circular.
  • the height of the outlet blending zone H is from 1 mm to 1000 mm, preferably H is between 1.5 A. Between ⁇ 3A.
  • the ratio of the opening area of the mesh plate to the area of the mesh plate is 0-100%, that is to say the mesh plate 8
  • the hole and the air can be mixed only through the outer flow channel.
  • the ratio of the opening area of the mesh plate to the area of the mesh plate is 0; the mesh plate 8 can be completely opened, which is equivalent to not setting the mesh plate.
  • the combustible mixture of the intermediate cylinder outlet zone 10 is also a flammable mixing zone with a spin, and the ratio of the open area of the mesh plate to the area of the mesh plate is 100%.
  • the ratio of the area of the opening on the mesh plate to the area of the mesh plate is 40% to 80%.
  • the diameter of the holes in the mesh plate is 0.1-10 mm, and the sizes of the holes may be the same or different; the shape of the holes may be circular, elliptical, triangular, polygonal or a combination of these shapes.
  • the embedded section is a wave structure 15 which is formed by circumferentially arranging a plurality of peaks 151 and a plurality of valleys 152 which are undulating in the radial direction.
  • the embedding section of the wave structure can also adjust the equivalence ratio of the inner and outer flow channels.
  • the valley 152 of the embedded segment corresponds to the position of the peak 51 of the wave cyclone, i.e., the valley 152 of the embedded segment is embedded in the peak 51 of the wave cyclone, and the peak 151 of the embedded segment and the valley of the wave cyclone 52
  • the position corresponds to the fact that the peak 151 of the embedded section is embedded in the trough 52 of the wave cyclone.
  • the wave structure embedded section in FIG. 11 reduces the fuel flow into the inner flow passage and increases the air flow rate as compared with the straight cylindrical embedded portion.
  • the equivalence ratio of the inner flow passage is decreased, the fuel flow rate entering the outer flow passage is increased, and the air flow rate is decreased, thereby increasing the equivalence ratio of the outer flow passage, thereby reducing the flame propagation speed and avoiding tempering in the middle portion of the nozzle outlet. Widen the tempering margin of the nozzle.
  • the valleys 152 of the embedded segments correspond to the locations of the valleys 52 of the wave cyclone, i.e., the valleys 152 of the embedded segments are embedded in the valleys 52 of the wave cyclone, and the peaks 151 of the embedded segments are The position of the peak 51 of the wave cyclone corresponds to that the peak 151 of the embedded section is embedded in the peak 51 of the wave cyclone.
  • the wave structure embedded section in FIG. 12 reduces the fuel flow into the inner flow passage and increases the air flow rate as compared with the straight cylindrical embedded portion.
  • the internal flow passage equivalent ratio is decreased; the fuel flow rate entering the outer flow passage is increased, and the air flow rate is decreased, thereby increasing the equivalence ratio of the outer flow passage, thereby reducing the flame propagation speed and avoiding tempering in the middle portion of the nozzle outlet. Widen the tempering margin of the nozzle.
  • the embedded section wave structure cross-sectional profile can be sinusoidal waveform, square waveform, triangular waveform, multilateral
  • the waveform or a combination thereof is preferably a sinusoidal waveform.
  • the strip-shaped piece 16 of the tooth structure has a through hole 18, and the shape of the through hole 18 may be circular, elliptical, triangular, polygonal, preferably circular, and the diameter is 0.1 mm. 100mm.
  • the wave cyclone is shown for clarity of view, and a row of circular holes is formed in the strips located in the wave swirler troughs.
  • the equivalent ratio of the combustible mixture of the inner and outer flow passages is adjusted to widen the tempering margin of the nozzle.
  • a through hole may be formed in the peak 151 and the trough 152 of the embedded portion of the wave structure. Similar to the above case, by adjusting the area of the through hole, the equivalent ratio of the combustible mixture of the inner and outer flow channels can also be adjusted. Widen the tempering margin of the nozzle.
  • a portion of the structure of the inner ring swirling structure 13 located in the intermediate cylinder 6 is trimmed in the axial direction, and the upstream portion of the wave swirler 5 forms a cavity, the bottom of which is meshed with the mesh plate.
  • the inner blending zone is formed to reduce the nozzle weight and reduce the flow friction loss.
  • the inner ring swirling structure 13 can be completely trimmed, and the swirling wave structure only includes the outer ring swirling structure 14, and the upstream section of the wave swirler is divided into a cavity, which is empty.
  • An inner blending zone is formed between the bottom of the cavity and the mesh plate, which further reduces nozzle weight and reduces flow friction losses.
  • a fifth embodiment of the present disclosure provides a nozzle array comprising a plurality of nozzles according to any of the above embodiments.
  • the nozzle array is a circular array, and the circular array comprises a P-circle nozzle, and each nozzle comprises Q nozzles, wherein 1 ⁇ P, Q ⁇ 100.
  • the nozzle array is a rectangular array comprising P rows of nozzles, each row of nozzles comprising Q nozzles, wherein 1 ⁇ P, Q ⁇ 100.
  • a sixth embodiment of the present disclosure provides a burner comprising the nozzle according to any one of the above first to fourth embodiments, or the multi-nozzle nozzle array of the fifth embodiment.

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Abstract

L'invention concerne une buse ayant des rapports d'équivalence de canaux d'écoulement interne et externe réglables, ladite buse comprenant un cylindre central (6), un cylindre de paroi externe (3), et une coupelle de turbulence d'onde (5). La coupelle de turbulence d'onde (5) est disposée de manière coaxiale dans le cylindre de paroi externe (3). Le cylindre central (6) est inséré dans la coupelle de turbulence d'onde (5) dans la direction axiale de la coupelle de turbulence d'onde (5) et à travers une extrémité de sortie de la coupelle de turbulence d'onde (5). La coupelle de turbulence d'onde (5) est divisée en une structure de turbulence de bague interne (13) et une structure de turbulence de bague externe (14). La structure de turbulence de bague externe (14), le cylindre central (6) et le cylindre de paroi externe (3) délimitent un canal d'écoulement externe. La structure de turbulence de bague interne (13) et le cylindre central (6) délimitent un canal d'écoulement interne. La partie du cylindre central (6) intégrée dans la coupelle de turbulence d'onde (5) est une section intégrée. La section intégrée a une structure non cylindrique et est utilisée pour régler un rapport d'équivalence des canaux d'écoulement interne et externe. La section intégrée règle le rapport d'équivalence des canaux d'écoulement interne et externe, ce qui permet de réduire la vitesse de propagation de la flamme, d'éviter un retour de flamme dans la zone centrale d'une sortie d'une buse, et d'augmenter une marge de retour de flamme de buse.
PCT/CN2017/087611 2017-01-22 2017-06-08 Buse à rapports d'équivalence de canaux d'écoulement interne et externe réglables, réseau de buses et brûleur Ceased WO2018133292A1 (fr)

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CN201710053759.XA CN106705045B (zh) 2017-01-22 2017-01-22 一种内外流道当量比可调的喷嘴、喷嘴阵列和燃烧器
CN201710053759.X 2017-01-22

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Publication number Priority date Publication date Assignee Title
CN106705045B (zh) * 2017-01-22 2019-08-09 中国科学院工程热物理研究所 一种内外流道当量比可调的喷嘴、喷嘴阵列和燃烧器
CN109519970B (zh) * 2018-11-12 2020-12-08 中国航发湖南动力机械研究所 双级轴向涡流器及使用其的航空发动机燃烧室

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5235813A (en) * 1990-12-24 1993-08-17 United Technologies Corporation Mechanism for controlling the rate of mixing in combusting flows
JPH06330765A (ja) * 1993-05-20 1994-11-29 Ishikawajima Harima Heavy Ind Co Ltd ジェットエンジンの保炎装置
US20040050056A1 (en) * 2002-09-13 2004-03-18 Pederson Robert J. Compact, lightweight high-performance lift thruster incorporating swirl-augmented oxidizer/fuel injection, mixing and combustion
JP2005180799A (ja) * 2003-12-19 2005-07-07 Mitsubishi Heavy Ind Ltd 予混合燃料ノズル、燃焼器及びそれを用いたガスタービン
CN101743442A (zh) * 2007-12-21 2010-06-16 三菱重工业株式会社 燃气轮机燃烧器
CN105737200A (zh) * 2016-03-28 2016-07-06 中国科学院工程热物理研究所 一种雾化喷嘴、喷嘴阵列和燃烧器
CN106016358A (zh) * 2016-05-30 2016-10-12 中国科学院工程热物理研究所 一种兼具旋流、喷射与掺混作用的旋流器
CN106091008A (zh) * 2016-06-13 2016-11-09 中国科学院工程热物理研究所 兼具旋流、雾化与掺混作用的旋流器和喷射装置
CN106705045A (zh) * 2017-01-22 2017-05-24 中国科学院工程热物理研究所 一种内外流道当量比可调的喷嘴、喷嘴阵列和燃烧器

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11101436A (ja) * 1997-09-30 1999-04-13 Nissan Motor Co Ltd セラミック燃焼器の構造
WO2011054766A2 (fr) * 2009-11-07 2011-05-12 Alstom Technology Ltd Système d'injection de brûleur de postcombustion
US9435537B2 (en) * 2010-11-30 2016-09-06 General Electric Company System and method for premixer wake and vortex filling for enhanced flame-holding resistance
CN106164592B (zh) * 2014-04-03 2019-08-30 西门子公司 燃烧器、具有这种燃烧器的燃气轮机和燃料喷嘴

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5235813A (en) * 1990-12-24 1993-08-17 United Technologies Corporation Mechanism for controlling the rate of mixing in combusting flows
JPH06330765A (ja) * 1993-05-20 1994-11-29 Ishikawajima Harima Heavy Ind Co Ltd ジェットエンジンの保炎装置
US20040050056A1 (en) * 2002-09-13 2004-03-18 Pederson Robert J. Compact, lightweight high-performance lift thruster incorporating swirl-augmented oxidizer/fuel injection, mixing and combustion
JP2005180799A (ja) * 2003-12-19 2005-07-07 Mitsubishi Heavy Ind Ltd 予混合燃料ノズル、燃焼器及びそれを用いたガスタービン
CN101743442A (zh) * 2007-12-21 2010-06-16 三菱重工业株式会社 燃气轮机燃烧器
CN105737200A (zh) * 2016-03-28 2016-07-06 中国科学院工程热物理研究所 一种雾化喷嘴、喷嘴阵列和燃烧器
CN106016358A (zh) * 2016-05-30 2016-10-12 中国科学院工程热物理研究所 一种兼具旋流、喷射与掺混作用的旋流器
CN106091008A (zh) * 2016-06-13 2016-11-09 中国科学院工程热物理研究所 兼具旋流、雾化与掺混作用的旋流器和喷射装置
CN106705045A (zh) * 2017-01-22 2017-05-24 中国科学院工程热物理研究所 一种内外流道当量比可调的喷嘴、喷嘴阵列和燃烧器

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