WO2020178880A1 - Brûleur à combustible solide - Google Patents

Brûleur à combustible solide Download PDF

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Publication number
WO2020178880A1
WO2020178880A1 PCT/JP2019/008014 JP2019008014W WO2020178880A1 WO 2020178880 A1 WO2020178880 A1 WO 2020178880A1 JP 2019008014 W JP2019008014 W JP 2019008014W WO 2020178880 A1 WO2020178880 A1 WO 2020178880A1
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WO
WIPO (PCT)
Prior art keywords
fuel
burner
mixed fluid
nozzle
axial direction
Prior art date
Application number
PCT/JP2019/008014
Other languages
English (en)
Japanese (ja)
Inventor
馬場　彰
嶺　聡彦
昌平 水戸
恒輔 北風
Original Assignee
三菱日立パワーシステムズ株式会社
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 三菱日立パワーシステムズ株式会社 filed Critical 三菱日立パワーシステムズ株式会社
Priority to PCT/JP2019/008014 priority Critical patent/WO2020178880A1/fr
Priority to TW109106448A priority patent/TW202102799A/zh
Priority to JP2021504008A priority patent/JPWO2020179593A1/ja
Priority to KR1020217031078A priority patent/KR20210134356A/ko
Priority to PCT/JP2020/007934 priority patent/WO2020179593A1/fr
Publication of WO2020178880A1 publication Critical patent/WO2020178880A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D1/00—Burners for combustion of pulverulent fuel
    • F23D1/02—Vortex burners, e.g. for cyclone-type combustion apparatus
    • 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
    • F23D2900/01001—Pulverised solid fuel burner with means for swirling the fuel-air mixture

Definitions

  • the present invention relates to a solid fuel burner that conveys and burns solid fuel, and particularly to a solid fuel burner suitable for fuel particles having a large particle size such as biomass particles.
  • Patent Document 1 Patent No. 5886031 specification: JP 5886031 B2
  • a swirl vane (16) is arranged in the flow path of the biomass fuel injection nozzle (11) to make a swirl flow, thereby making the fuel flow to the outer periphery. It is described to concentrate in part.
  • a swirl degree adjusting plate (17) is arranged on the downstream side of the swirl vanes (16) to adjust swirling of the fuel flow.
  • Patent Document 2 (patent No. 6231047 specification: JP 6231047 B2), a first swirler (6) for imparting swirl to the mixed fluid and a first swirler (at the center of the primary air nozzle (9)
  • the technique of providing the 2nd turning device (7) which gives a turning in the direction opposite to 6) is described.
  • the first swirler (6) strongly swirls the mixed fluid to move the solid fuel particles to the outer peripheral side of the primary air nozzle
  • the second swirler (7) moves the solid fuel particles to the outer peripheral side.
  • the swirl of the mixed fluid is weakened by imparting a swirl in the direction opposite to that of the one swirler (6). Therefore, while the solid fuel particles are concentrated around the flame stabilizer (10) installed in the opening of the burner, the mixed fluid with less swirling flows out from the opening to improve the ignitability.
  • Patent Document 3 US Patent Publication No. 2013/0305971: US 2013/0305971 A1
  • a spiral blade-shaped deflecting means (deflection means 17,18,19) is provided in a flow channel (flow channel 5)
  • a technique for concentrating fuel on the outer peripheral side of the flow channel 5 is described.
  • Patent Document 4 Choinese Patent Publication No. 101832551 gazette: CN 101832551A
  • a conical member (10) that moves the flow to the outer peripheral side is arranged upstream of the member (11) that imparts swirl. ..
  • the cone-shaped member (10) and the member (19) that imparts a turn are configured by rod-shaped members (19, 20) so that their axial positions can be adjusted.
  • Japanese Patent No. 5886031 ([0030]-[0031], FIGS. 1-3, 21) Japanese Patent No. 6231047 ([0048]-[0061], FIGS. 1-3, 21) US Patent Publication No. 2013/0305971 ([0041] to [0043], FIG. 1) Chinese Patent Publication No. 101832551 ([0036]-[0038], FIG. 1)
  • the present invention has a technical problem of enabling switching between coal and biomass fuels while maintaining the risk of wear and ignitability.
  • the solid fuel burner of the invention is A fuel nozzle in which a mixed fluid of solid fuel and its carrier gas flows and opens toward the furnace, A combustion gas nozzle arranged on the outer peripheral side of the fuel nozzle to eject a combustion gas, A fuel concentrator which is provided on the center side of the fuel nozzle and applies a velocity component in a direction away from the center of the fuel nozzle to the mixed fluid;
  • a solid fuel burner comprising: The fuel concentrator has a plurality of blades that give a swirl to the mixed fluid, and is installed at two positions apart from the burner axial direction, and the swirling direction of each of the plurality of blade structures is opposite. It is characterized in that at least the deflection angle of the blade on the upstream side with respect to the flow direction of the mixed fluid with respect to the burner axis direction is adjustable.
  • the invention according to claim 2 is the solid fuel burner according to claim 1.
  • the fuel concentrator may include a vane having a fixed vane angle and movable along an axial direction.
  • the solid fuel burner of the invention is A fuel nozzle in which a mixed fluid of solid fuel and its carrier gas flows and opens toward the furnace, A combustion gas nozzle arranged on the outer peripheral side of the fuel nozzle to eject a combustion gas, A fuel concentrator provided on the center side of the fuel nozzle and imparting a velocity component in a direction away from the center of the fuel nozzle to the mixed fluid.
  • a solid fuel burner comprising: The fuel concentrator has a plurality of blades that give a swirl to the mixed fluid, and is installed at two positions apart from the burner axial direction, and the swirling direction of each of the plurality of blade structures is opposite. The fuel concentrator is configured to be movable along the burner axis direction.
  • the fuel concentrator has a plurality of blades that give a swirl to the mixed fluid, and is installed at two positions apart from the burner axial direction, and the swirling direction of each of the plurality of blade structures is opposite.
  • the deflection angle of at least the upstream blade with respect to the flow direction of the mixed fluid with respect to the burner axis direction is adjustable.
  • the deflection angle of at least the blade on the upstream side can be adjusted, the deflection angle can be adjusted according to the fuel used, and the risk of wear and ignitability are maintained. Meanwhile, coal and biomass fuel can be switched and made usable.
  • the position of the fuel concentrator can be adjusted according to the fuel used, and the risk of burning can be dealt with. it can.
  • the fuel concentrator having the blades in the opposite directions is movable in the axial direction, the position in the axial direction can be adjusted according to the fuel to be used, and the wear can be prevented against wear. It is possible to switch between coal and biomass fuel for use while maintaining risk and ignitability.
  • the deflection angle of at least the upstream blade can be adjusted, the deflection angle is adjusted according to the fuel used. Therefore, it is possible to deal with the risk of wear and the risk of ignitability and burnout.
  • FIG. 1 is an overall explanatory diagram of a combustion system according to a first embodiment of the present invention.
  • FIG. 2 is an explanatory diagram of the solid fuel burner of the first embodiment.
  • FIG. 3 is an explanatory diagram of a blade swing angle tilting mechanism of the fuel concentrator of the embodiment.
  • FIG. 4 is an explanatory diagram of analysis results of the position of the downstream blade and the opening diameter for the coal fuel and the biomass fuel.
  • FIG. 5 is an explanatory diagram of another embodiment of the present invention.
  • FIG. 1 is an overall explanatory view of the combustion system according to the first embodiment of the present invention.
  • a biomass fuel solid fuel
  • a bunker fuel hopper
  • the biomass fuel of the bunker 4 is crushed by the mill (crusher) 5.
  • the crushed fuel is supplied to the solid fuel burner 7 of the boiler 6 through the fuel pipe 8 and burned.
  • a plurality of solid fuel burners 7 are installed in the boiler 6.
  • the exhaust gas discharged from the boiler 6 is denitrated by the denitration device 9.
  • the denitrated exhaust gas passes through the air preheater 10.
  • the air preheater 10 heat exchange between the air sent from the blower 11 and the exhaust gas is performed. Therefore, the temperature of the exhaust gas is lowered and the air from the blower 11 is heated.
  • Air from the blower 11 is supplied to the solid fuel burner 7 and the boiler 6 as combustion air through the air pipe 12.
  • the exhaust gas that has passed through the air preheater 10 is recovered in heat when passing through the gas gas heater (heat recovery device) 13, and is cooled down.
  • the exhaust gas that has passed through the gas gas heater (heat recovery device) 13 is recovered and removed by the dry dust collector 14.
  • the exhaust gas that has passed through the dry dust collector 14 is sent to the desulfurization device 15 to be desulfurized.
  • the exhaust gas that has passed through the desulfurization device 15 is collected and removed by the wet dust collector 16 such as dust in the exhaust gas.
  • the exhaust gas that has passed through the wet dust collector 16 is reheated by the gas gas heater (reheater) 17.
  • the exhaust gas that has passed through the gas gas heater (reheater) 17 is exhausted to the atmosphere from the chimney 18.
  • the mill 5 itself may have various conventionally known configurations, and is described in, for example, Japanese Unexamined Patent Publication No. 2010-242999, so detailed description thereof will be omitted.
  • FIG. 2 is an explanatory diagram of the solid fuel burner of the first embodiment.
  • FIG. 3 is an explanatory diagram of a blade swing angle tilting mechanism of the fuel concentrator of the embodiment.
  • the solid fuel burner 7 of the first embodiment has a fuel nozzle 21 through which a carrier gas flows.
  • the downstream end opening of the fuel nozzle 21 is provided in the wall surface (furnace wall, water tube wall) 23 of the furnace 22 of the boiler 6.
  • the fuel pipe 8 is connected to the upstream end.
  • the fuel nozzle 21 is formed in a hollow cylindrical shape, and inside the fuel nozzle 21, a flow path 24 through which solid fuel (crushed biomass fuel) and carrier gas flow is formed.
  • An inner combustion gas nozzle (secondary combustion gas nozzle) 26 that ejects combustion air to the furnace 22 is installed on the outer periphery of the fuel nozzle 21. Further, an outer combustion gas nozzle (third combustion gas nozzle) 27 is installed on the outer peripheral side of the inner combustion gas nozzle 26. The combustion gas nozzles 26 and 27 eject the air from the wind box 28 into the furnace 22.
  • a guide vane 26a is formed at the downstream end of the inner combustion gas nozzle 26 so as to incline radially outward with respect to the center of the fuel nozzle 21 (the diameter increases toward the downstream side). ..
  • a throat portion 27a along the axial direction and an enlarged portion 27b parallel to the guide vane 26a are formed in the downstream portion of the outer combustion gas nozzle 27. Therefore, the combustion air ejected from the combustion gas nozzles 26 and 27 is ejected so as to diffuse from the center in the axial direction.
  • a flame stabilizer 31 is supported at the opening at the downstream end of the fuel nozzle 21. 2 and 3, the flame stabilizer 31 is formed with an inner peripheral side protrusion 31a.
  • the inner peripheral side protrusions 31a are formed so as to project toward the center side of the fuel nozzle 21, and the inner peripheral side protrusions 31a are periodically arranged at intervals along the circumferential direction.
  • a tubular or rod-shaped central shaft member is provided so as to penetrate the collision plate 32a supported by the collision plate flange 21a of the fuel nozzle 21, whereby the fuel concentrator 34
  • the first swirler 41 on the upstream side and the second swirler 42 on the downstream side are supported.
  • the oil starting burner (oil gun) 32 is arranged so as to penetrate therethrough. The oil starting burner 32 is supported in a state of penetrating the collision plate 32a supported by the collision plate flange 21a of the fuel nozzle 21.
  • a fuel concentrator 34 is supported on the oil starting burner 32.
  • the fuel concentrator 34 has an inner cylinder 35 supported by the oil starting burner 32.
  • the inner cylinder 35 is formed in a cylindrical shape, and the oil starting burner 32 penetrates the inside.
  • An outer cylinder 36 is arranged on the outer circumference of the inner cylinder 35.
  • the outer cylinder 36 is supported by the collision plate 32a via a support (not shown). Therefore, the inner cylinder 35 is axially slidably supported with respect to the oil starting burner 32 and the outer cylinder 36.
  • a position adjusting rod 37 as an example of a position adjusting member is supported on the inner cylinder 35.
  • the position adjusting rod 37 is formed in a rod shape and extends parallel to the oil starting burner 32 toward the upstream side in the fluid flow direction.
  • the upstream portion of the position adjusting rod 37 penetrates the collision plate 32a and extends to the outside of the flow path 24.
  • the position adjusting rod 37 may be installed so as to be built in a cylindrical or rod-shaped central shaft member, whereby wear damage due to collision of fuel particles can be avoided.
  • an opening 38 is formed in the inner cylinder 35.
  • the opening 38 has a quadrangular shaft passing portion 38a and a quadrangular fitting portion 38b connected to the shaft passing portion 38a.
  • the fuel concentrator 34 has a first swivel 41 on the upstream side and a second swivel 42 on the downstream side.
  • each of the swirlers 41 and 42 has a plurality of blades 41a and 42a that incline the oil starting burner 32 with respect to the axis.
  • the blades 42a are fixedly supported on the outer peripheral surface of the outer cylinder 36.
  • the blades 41 a are supported by the rotating shaft 43.
  • the rotating shaft 43 is rotatably supported on the outer surface of the oil starting burner 32.
  • the rotating shaft 43 penetrates the shaft passing portion 38a of the inner cylinder 35.
  • a cam portion 44 that projects radially outward is supported on the rotating shaft 43.
  • the cam portion 44 is housed in the fitting portion 38b. Therefore, in the fuel concentrator 34 of the first embodiment, when the position adjusting rod 37 is inserted or pulled out in the axial direction, the inner cylinder 35 moves in the axial direction. In response to this, the fitting portion 38b moves in the axial direction, the cam portion 44 moves in the axial direction, and the rotating shaft 43 rotates.
  • the blade 41a moves between the low angle position shown by the solid line in FIG. 3 and the high angle position shown by the broken line in FIG.
  • the deflection angle of the blade 42a of the second swirler 42 is set to the opposite direction and the same angle as the deflection angle of the blade 41a at the low angle position.
  • the position adjusting rod 37 is pushed in. Therefore, the inner cylinder 35 moves to the downstream side in the fluid flow direction. Therefore, the swirlers 41 and 42 move to the downstream side in the axial direction (the side closer to the furnace 22). At this time, the blade 41a of the upstream first swirler 41 moves to the high angle position. Therefore, the deflection angle of the vanes 41a of the first swirler 41 becomes large.
  • the biomass fuel has a lower ignitability than coal, and it is desired to concentrate the fuel particles to enhance the ignitability. Therefore, in the first embodiment, the deflection angle of the blade 41a is increased to strengthen the swirling of the mixed fluid. Therefore, even if biomass fuel is used, the ignitability of the fuel can be improved.
  • the fuel concentrator 34 is moved to the downstream side, and the opening (maintenance) is opened before the fuel once moved to the outer peripheral side is reflected by the inner surface of the fuel nozzle 21 and moves to the inner peripheral side.
  • Easy to reach flamearm 31 Therefore, compared with the case where the fuel concentrator 34 is located on the upstream side, the ignitability and the fuel concentration effect are improved.
  • Biomass fuel has a larger average particle size and is inferior in ignitability as compared with coal fuel, so that the radiant heat received by the burner from the flame is smaller than that in the case of coal combustion.
  • the risk of burnout of the fuel concentrator 34 is lower than that at the time of coal combustion, and therefore the risk of burnout is suppressed even if the fuel concentrator 34 moves to the downstream side. Further, since the biomass fuel has a lower risk of wear than coal, even if the deflection angle of the blade 41a is increased, the adverse effect on the life is reduced.
  • the biomass fuel is an oxygen-containing fuel, and the amount of additional oxygen required after ignition is small. Therefore, the amount of air ejected from the outer peripheral secondary air nozzle (inner combustion gas nozzle 26) is reduced as compared with coal, and the amount of primary air that contributes to ignition is set to be larger by that amount.
  • a guide vane 26a is installed at the downstream end so that the air jet from the secondary air nozzle (inner combustion gas nozzle 26) forms a circulating flow having a large spread. ..
  • the amount of the secondary air is reduced and the amount of the primary air is set to be large, the spread of the jet flow ejected from the solid fuel burner 7 becomes relatively small.
  • the deflection angle of the first swirler 41 >(the deflection angle of the second swirler 42) is set. Therefore, the swirl strongly applied by the blade 41a on the upstream side is reduced on the downstream side, and the swirl is ejected while leaving the swirl. Therefore, the jet flow ejected from the solid fuel burner 7 is in a state in which the jet flow is effectively spread by swirling. Therefore, the spread of the jet flow is also prevented from being insufficient.
  • the position adjusting rod 37 is pulled out in the axial direction. Therefore, the swirlers 41 and 42 move to the upstream side in the axial direction (direction away from the furnace 22). Therefore, the blade 41a of the first swirler 41 moves to the low angle position, and the deflection angle becomes small. Therefore, the abrasion of the blades 41a due to the coal fuel is suppressed as compared with the case where the deflection angle is large. Further, since the ignitability of the coal fuel is higher than that of the biomass fuel, the ignitability can be sufficiently ensured even if the fuel concentrator 34 is on the upstream side or the turning is weak. On the other hand, since the burning risk of coal fuel is high, the burning risk can be reduced by locating the fuel concentrator 34 on the upstream side.
  • FIG. 4 is an explanatory diagram of analysis results of the position of the downstream blade and the opening diameter for the coal fuel and the biomass fuel.
  • FIG. 4 shows the maximum and intermediate L / D when the distance from the opening end of the fuel nozzle 21 to the installation reference position of the downstream blade 42a is L and the opening diameter of the fuel nozzle 21 is D for coal and biomass.
  • CFD Computational Fluid Dynamics
  • UBC ash
  • Medium unburned carbon Unburned Carbon
  • Coal has almost no effect of ⁇ on performance when L / D is between the minimum and intermediate (small sensitivity), but when L / D is maximum, the effect of ⁇ is large, and when the angle is maximum, the effect of ⁇ is large. Sufficient performance can be obtained, but performance decreases as the angle is reduced. Therefore, it is desirable to set the risk of flashback, wear, and accumulation to the minimum, that is, set L / D to the middle and ⁇ to the minimum.
  • biomass has a greater influence of ⁇ than any coal at any L/D (a high sensitivity), and a combination with a minimum L/D and a maximum ⁇ is sufficient for sufficient performance. desirable.
  • the biomass fuel and the coal fuel can be switched and used by operating the position adjusting rod 37, and at the time of use, there is a risk of wear, ignitability, and burnout. Can be suppressed.
  • both the runout angle adjustment and the axial position adjustment are possible by operating the position adjustment rod 37. Therefore, compared with the case where the members for adjusting the deflection angle and the position in the axial direction are respectively provided, the operation is easy, the number of parts is reduced, and the cost is reduced. It is desirable that the position adjusting rod 37 be provided with a protective cover as a measure against wear.
  • FIG. 5 is an explanatory diagram of another embodiment of the present invention.
  • the positions of the cam portion 44'and the fitting portion 38b' are changed to positions shifted by 90 degrees, and the outer cylinder 36 can be rotated in the circumferential direction with respect to the oil starting burner 32, whereby the blade 41a It is also possible to adopt a configuration in which the angle can be adjusted.
  • the present invention is not limited to the above embodiments, and various modifications can be made within the scope of the gist of the present invention described in the claims. It is possible.
  • the configuration in which the deflection angle of only the upstream blade 41a can be adjusted has been illustrated, the deflection angle of the downstream blade 42a can also be adjustable.
  • the configuration of the two-stage combustion gas nozzles 26 and 27 having the secondary combustion gas nozzle 26 and the tertiary combustion gas nozzle 27 has been illustrated, but the configuration is not limited to this, and the combustion gas nozzle is one stage or three stages or more. It is also possible to do so.
  • one deflection rod 37 is used to adjust the deflection angle and the axial position is illustrated, but the invention is not limited to this. It is also possible to provide a member for adjusting the deflection angle and a member for adjusting the position in the axial direction, respectively.
  • the rotary shaft of the blades (fulcrum for adjusting the deflection angle) is installed in a double cylindrical inner cylinder that is slidable relative to each other, and a cam movable mechanism as shown in FIG. It is possible to adjust the deflection angle of the swirl vane by shifting the relative positional relationship between the cylinder and the outer cylinder or rotating one of the cylinders around the axis.
  • the axial position can be adjusted by sliding the inner cylinder and the outer cylinder integrally in the nozzle axial direction. Note that the relative rotation of the inner cylinder and the outer cylinder and the movement in the nozzle axis direction can be operated, for example, by providing rods respectively.
  • Solid fuel burner 21... Fuel nozzle, 22... furnace, 26, 27... Combustion gas nozzle, 34... Fuel concentrator, 41a... blades on the upstream side, 41a, 41b... blades.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)

Abstract

Un concentrateur de combustible (34), lequel est disposé vers le centre d'une buse de combustible (21) et confère à un fluide mélangé une composante de vitesse à l'opposé du centre de la buse de combustible (21), est conçu de manière à avoir une pluralité de pales (41a, 41b) qui impriment un tourbillon au fluide mélangé et sont disposées à deux emplacements qui sont séparés l'un de l'autre dans une direction axiale du brûleur, les directions de tourbillonnement de la pluralité de structures de pales (41a, 42a) étant dans des directions mutuellement opposées, et l'angle de déviation d'au moins une pale côté amont (41a) par rapport à la direction axiale du brûleur peut être ajusté par rapport à la direction d'écoulement du fluide mélangé; il est ainsi possible de commuter entre l'utilisation de charbon et de combustible de biomasse tout en conservant l'inflammabilité et le risque d'abrasion.
PCT/JP2019/008014 2019-03-01 2019-03-01 Brûleur à combustible solide WO2020178880A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
PCT/JP2019/008014 WO2020178880A1 (fr) 2019-03-01 2019-03-01 Brûleur à combustible solide
TW109106448A TW202102799A (zh) 2019-03-01 2020-02-27 固體燃料燃燒器
JP2021504008A JPWO2020179593A1 (ja) 2019-03-01 2020-02-27 固体燃料バーナ
KR1020217031078A KR20210134356A (ko) 2019-03-01 2020-02-27 고체 연료 버너
PCT/JP2020/007934 WO2020179593A1 (fr) 2019-03-01 2020-02-27 Brûleur à combustible solide

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Application Number Priority Date Filing Date Title
PCT/JP2019/008014 WO2020178880A1 (fr) 2019-03-01 2019-03-01 Brûleur à combustible solide

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WO2020178880A1 true WO2020178880A1 (fr) 2020-09-10

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PCT/JP2020/007934 WO2020179593A1 (fr) 2019-03-01 2020-02-27 Brûleur à combustible solide

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KR (1) KR20210134356A (fr)
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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6231047B2 (fr) * 1977-04-25 1987-07-06 Tokyo Shibaura Electric Co
JP2756098B2 (ja) * 1995-07-14 1998-05-25 川崎重工業株式会社 微粉炭バーナ
CN101832551A (zh) * 2010-06-18 2010-09-15 上海交通大学 中心弱旋可调旋流煤粉燃烧器

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11118105A (ja) * 1997-10-20 1999-04-30 Ishikawajima Harima Heavy Ind Co Ltd 微粉炭バーナ
JP5886031B2 (ja) 2011-12-26 2016-03-16 川崎重工業株式会社 バイオマス燃料燃焼方法
JP5799875B2 (ja) 2012-03-29 2015-10-28 三菱マテリアル株式会社 ボールエンドミル
DE102012007884A1 (de) 2012-04-23 2013-10-24 Babcock Borsig Steinmüller Gmbh Brenner für staub- und/oder partikelförmige Brennstoffe mit veränderlichem Drall
JP6231047B2 (ja) * 2015-06-30 2017-11-15 三菱日立パワーシステムズ株式会社 固体燃料バーナ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6231047B2 (fr) * 1977-04-25 1987-07-06 Tokyo Shibaura Electric Co
JP2756098B2 (ja) * 1995-07-14 1998-05-25 川崎重工業株式会社 微粉炭バーナ
CN101832551A (zh) * 2010-06-18 2010-09-15 上海交通大学 中心弱旋可调旋流煤粉燃烧器

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TW202102799A (zh) 2021-01-16
KR20210134356A (ko) 2021-11-09
JPWO2020179593A1 (ja) 2021-12-16

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