US20090087805A1 - In-Furnace Gas Injection Port - Google Patents

In-Furnace Gas Injection Port Download PDF

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Publication number
US20090087805A1
US20090087805A1 US12/224,983 US22498306A US2009087805A1 US 20090087805 A1 US20090087805 A1 US 20090087805A1 US 22498306 A US22498306 A US 22498306A US 2009087805 A1 US2009087805 A1 US 2009087805A1
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Prior art keywords
nozzle
furnace
gas
tertiary
flow
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Abandoned
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US12/224,983
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English (en)
Inventor
Yusuke Ochi
Akira Baba
Kouji Kuramashi
Hirofumi Okazaki
Masayuki Taniguchi
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Mitsubishi Hitachi Power Systems Ltd
Original Assignee
Babcock Hitachi KK
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Assigned to BABCOCK-HITACHI KABUSHIKI KAISHA reassignment BABCOCK-HITACHI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TANIGUCHI, MASAYUKI, BABA, AKIRA, KURAMASHI, KOUJI, OCHI, YUSUKE, OKAZAKI, HIROFUMI
Publication of US20090087805A1 publication Critical patent/US20090087805A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C99/00—Subject-matter not provided for in other groups of this subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/008—Flow control devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/02—Disposition of air supply not passing through burner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L9/00—Passages or apertures for delivering secondary air for completing combustion of fuel 
    • F23L9/02—Passages or apertures for delivering secondary air for completing combustion of fuel  by discharging the air above the fire
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2201/00—Staged combustion
    • F23C2201/10—Furnace staging
    • F23C2201/101—Furnace staging in vertical direction, e.g. alternating lean and rich zones

Definitions

  • the present invention relates to a port for gas injection into a furnace such as a boiler, and in particular to a port for gas injection into a furnace such as a boiler advantageous in preventing ash adhesion to a furnace opening.
  • ports for injecting gas such as air and exhaust gas into a furnace are disposed on the wall of a furnace such as a boiler. They include, for example, a burner for injecting fuel and combustion air as a combustion apparatus and an after air port (AAP) (which is also referred to as an over firing air port (OFA)) for feeding two-stage combustion air.
  • AAP after air port
  • OFA over firing air port
  • the gas injection port described in the present specification is not limited to an after air port but includes a port for feeding exhaust gas and a burner port for combusting fuel, as long as it is a port for injecting gas into a furnace.
  • a wall surface of an enlarged pipe configuration opened on a furnace on which the port is disposed is to be referred to as a throat wall or a throat enlarged pipe portion (a furnace wall surface portion at which the opening is gradually increased in diameter toward the outlet side of the furnace).
  • Patent Documents 1 and 2 given below have disclosed inventions of after air ports for feeding into a furnace two-stage combustion air which involves the contracted flow.
  • Patent Document 3 pulverized coal burner
  • Patent Document 4 a burner throat wall
  • Patent Document 5 an over firing air port
  • FIG. 13 shows a structural diagram of a conventional rotating-type AAP.
  • primary air 9 is supplied to a furnace 34 through a primary nozzle 1 .
  • a secondary nozzle 2 is mounted on the outer circumference of the primary nozzle 1 , thereby supplying secondary air 10 .
  • the secondary nozzle 2 is structured so as to be provided with a rotator 7 , a rotating secondary air flow obtained by the rotator 7 is used for mixing air with unburned gas inside the furnace 34 in the vicinity of the AAPs, and a strong air injection flow from the primary nozzle 1 to the center of the furnace 34 is used to mix air with unburned gas (Patent Document 6).
  • the rotating secondary air flow obtained by using the rotator 7 is insufficient in spreading the rotating air flow and there is a case where unburned gas may not be well mixed with combustion air at a region along the inner wall 34 a of the furnace 34 .
  • the present applicant has proposed an AAP equipped with a tertiary nozzle for tertiary air having a drift unit capable of supplying combustion air to the outer circumference of the secondary nozzle 2 having the rotator 7 in a direction along the inner wall 34 a of the furnace 34 (Patent Document 7).
  • Patent Document 1 Japanese Published Unexamined Patent
  • Patent Document 2 JP-A No. 2006-132798
  • Patent Document 3 Japanese Published Unexamined Utility Model Application No. 6-6909
  • Patent Document 4 Japanese Patent No. 3668989
  • Patent Document 5 JP-A No. Hei-10-122546
  • Patent Document 6 JP-A No. Sho-62-138607
  • Patent Document 7 JP-A No. Hei-9-112816
  • Patent Document 4 high-pressure injection air for aspiration is used for suppressing partial adhesion of ash to the wall surface of the throat portion with the lapse of time, by which a system may be complicated in structure or there may be an increase in cost and weight. Further, according to the invention described in Patent Document 3, when the gas flow heading from the outer circumferential side of the furnace throat wall of the burner port toward the central axis direction is increased to enhance the effects of the contracted flow, there may be a decrease in effectively preventing ash adhesion to the wall surface of the throat enlarged pipe portion.
  • a sufficient effect in preventing ash adhesion may not also be obtained in a case where the flow rate of gas such as air for preventing the adhesion of ash to the throat wall of the furnace must be reduced in order to keep a predetermined air ratio.
  • An object of the present invention is to provide a gas injection port which is able to prevent the growth of clinker in lump form caused by ash adhesion and fusion to the wall surface of a throat enlarged pipe portion of a furnace irrespective of conditions such as the flow rate of injection gas or without inviting a complicated structure of a system or cost increase, and where air is used as gas, combustion air in the vicinity of the furnace wall is stably mixed with unburned gas, and the combustion air is reliably brought to the center inside the furnace, thus making it possible to decrease the concentration of NOx in combustion gas.
  • the invention described in claim 1 is an in-furnace gas injection port which is disposed on a furnace wall of the furnace, comprising a contracted flow producing channel having a velocity component flowing toward the central axis of gas flow perpendicular to the furnace wall and a velocity component flowing along the central axis, and provided obliquely toward the central axis from the upstream side of gas flow, a throat enlarged pipe portion in which a gas channel formed on a furnace wall opening on the downstream side of the contracted flow producing channel is gradually enlarged in a direction of the gas flow, and a louver (guide plate) which is disposed on the contracted flow producing channel for guiding gas flowing through the contracted flow producing channel so as to flow along the wall surface of the throat enlarged pipe portion.
  • a contracted flow producing channel having a velocity component flowing toward the central axis of gas flow perpendicular to the furnace wall and a velocity component flowing along the central axis, and provided obliquely toward the central axis from the upstream side of gas flow
  • Gas guided by the louver as constituted in the invention of claim 1 effectively flows in the vicinity of the wall surface of the throat enlarged pipe portion, thereby eliminating a negative pressure in the vicinity of the wall surface of the enlarged pipe portion. Therefore, gas flowing along the wall surface on the outer circumference (a nozzle partition wall constituting the channel) of the contracted flow producing channel can be effectively guided to the wall surface side of the throat enlarged pipe portion, thereby it is less likely to cause ash adhesion to the throat enlarged pipe portion and the wall surface in the vicinity thereof due to the involvement of ash. Further, conventionally, an injection hole for injecting a coolant such as air is disposed separately at a gas injection port in place of a louver.
  • the invention described in claim 1 is able to reduce the pressure loss resulting from gas injection flow by using the louver and simplified in structure, thus eliminating a necessity for providing a sealing air adjustor for preventing the ash adhesion and attaining a reduction in weight of a system and the saving of iron and steel products.
  • the gas flow injected from the contracted flow producing channel of the invention described in claim 1 covers a gas flow arriving at the central portion inside the furnace and a gas flow accelerating a mixture of gas in the vicinity of the furnace wall, by which the gas injection port can be used as an AAP for a two-stage combustion burner to attain a highly reliable fuel combustion which is lower in NOx and CO combustion.
  • the invention described in claim 2 is the in-furnace gas injection port described in claim 1 in which the leading end of the louver on the upstream side of gas flow is located on a surface obtained by extending the outer circumferential wall surface of the contracted flow producing channel toward the central axis direction or on the upstream side of gas flow from the thus extended surface and an enlarged pipe portion gradually enlarged in a direction of gas flow so as to run along the wall surface of the throat enlarged pipe portion is provided at the downstream side portion of gas flow of the louver.
  • a case where the contracted flow of gas is increased is, for example, a case where a gas channel on the upstream side of the gas flow at the port disposed on the furnace wall surface is made up of only the contracted flow producing channel, or a case where the flow ratio of the contracted flow producing channel is 30% or more if another channel is available, a case where a radius of the throat portion on the furnace wall (length Ds given in FIG. 10 ) is 1.1 times or lower than a radius (length Db given in FIG. 10 ) at the inner circumferential downstream end of the contracted flow producing channel (site b given in FIG. 10 ), or a case where an inclined angle is from 30° to 70° with respect to the central axis of the port on the contracted flow producing channel.
  • the leading end portion of the louver on the upstream side of gas flow is located on a surface obtained by extending the outer circumferential wall surface of the contracted flow producing channel to the central axis direction or on the upstream side of gas flow from the thus extended surface. Therefore, gas guided into the louver flows effectively in the vicinity of the wall surface of the throat enlarged pipe portion, thereby eliminating a negative pressure in the vicinity of the wall surface of the enlarged pipe portion.
  • the invention described in claim 3 is the in-furnace gas injection port described in claim 1 or claim 2 which is provided with a mechanism for changing the ratio of a velocity component of air flow flowing through the contracted flow producing channel along the central axis to a velocity component of air flow flowing toward the central axis.
  • the ratio of a velocity component flowing along the central axis direction to a velocity component flowing toward the central axis direction is changed, thus making it possible to adjust a direction of gas injection flow after each of the velocity components inside a furnace is merged.
  • gas is air
  • an air-short unburned gas region localized inside the furnace is favorably mixed with combustion air, thereby reducing an unburned portion of fuel.
  • these two velocity components are adjusted for the rotating strength, thus making it possible to adjust a mixture state of gas after being merged.
  • the invention described in claim 4 is the in-furnace gas injection port described in claim 3 which is provided with a damper starting to open from the near surface side to the furnace so that gas flows along the outer circumferential wall surface of the contracted flow producing channel and capable of adjusting an aperture of the contracted flow producing channel.
  • the invention described in claim 5 is the in-furnace gas injection port described in any one of claims 1 through 4 which is provided with a rotating member for rotating gas between the louver and the wall surface of the throat enlarged pipe portion. It is noted that in order to absorb a heat stretching difference, the louver may be divided into a plurality of louvers in a circumferential direction of the gas injection port and disposed.
  • gas flowing between the louver and the wall surface of the throat enlarged pipe portion is rotated by means of the rotating member and can be injected into the furnace. Therefore, some of the contracted flow can easily flow from the contracted flow producing channel into a space between the louver and the wall surface of the throat enlarged pipe portion, and a gas flow which seals the inner wall surface of the furnace flows effectively in the vicinity of the wall surface of the throat enlarged pipe portion, thereby eliminating a negative pressure in the vicinity of the wall surface of the throat enlarged pipe portion. As a result, it is possible to prevent ash adhesion in the vicinity of the furnace wall surface of the throat enlarged pipe portion due to the involvement of ash.
  • the invention described in claim 6 is the in-furnace gas injection port described in any one of claims 1 through 5 , in which a length of the throat enlarged pipe portion in a gas flow direction formed at the downstream side end portion of the louver is 1 ⁇ 2 or lower than a length of the wall surface of the throat enlarged pipe portion in a gas flow direction.
  • ash is less likely to adhere to an exposed surface inside the enlarged pipe portion of the louver (a surface between the e portion and the f portion in FIG. 12 ).
  • the invention described in claim 7 is the in-furnace gas injection port described in any one of claims 1 through 6 in which the contracted flow producing channel is given as a tertiary nozzle and a primary nozzle is disposed inside from the tertiary nozzle and a secondary nozzle is disposed outside the primary nozzle, through which each gas flows along the central axis.
  • the gas injection port is used as an AAP disposed on the furnace wall at the downstream portion of a two-stage combustion burner, no ash is adhered to the furnace wall, thus making it possible to attain a highly reliable fuel combustion which is lower in NOx and CO combustion.
  • FIG. 1 is a schematic diagram of a boiler in which an after air port or a burner of the present invention is used.
  • FIG. 2 is a schematic sectional view of the after air port of Embodiment 1 in the present invention.
  • FIG. 3 is a perspective view in which the after air port of Embodiment 1 is partially omitted.
  • FIG. 4 is a drawing in which the air port is viewed from the inside of a furnace of Embodiment 1.
  • FIG. 5 is a flow velocity distribution diagram of air flow at an AAP outlet portion obtained by using an AAP model in FIG. 2 .
  • FIG. 6 is a flow velocity distribution diagram of air flow at the AAP outlet portion obtained by using the AAP model in FIG. 2 .
  • FIG. 7 is a flow velocity distribution diagram of air flow at the AAP outlet portion obtained by using the AAP model in FIG. 2 .
  • FIG. 8 is a schematic sectional view showing an after air port of Embodiment 2 of the present invention.
  • FIG. 9 is a schematic sectional view showing an after air port in which a louver of a comparative example in comparison with Embodiment 2 of the present invention is disposed along the furnace throat enlarged pipe portion.
  • FIG. 10 is a schematic sectional view showing an after air port in which a louver of a comparative example in comparison with Embodiment 2 of the present invention is disposed on a tertiary nozzle.
  • FIG. 11 is a schematic sectional view of an after air port of Embodiment 3 of the present invention.
  • FIG. 12 is a schematic sectional view of a part of the after air port for explaining the dimensional relationship where the louver of Embodiment 3 of the present invention and the throat enlarged pipe portion are arranged inside the after air port.
  • FIG. 13 is a schematic sectional view of an after air port of Embodiment 4 of the present invention.
  • FIG. 14 is a longitudinal sectional view showing an AAP structure according to a conventional technique.
  • FIG. 15 is a longitudinal sectional view of an AAP structure according conventional technique.
  • a plurality of burners 30 are arranged so as to face each other on a pair of facing furnace walls of the furnace 34 of a boiler, and after air ports 31 are disposed so as to face each other above a place at which the burners are placed.
  • An air fuel mixture of less than a theoretical air ratio (for example, 0.8) is injected into a flame region inside the furnace 34 from the burners 30 , thereby forming an incomplete combustion region (not illustrated) inside the furnace.
  • the after air ports 31 are to supply air insufficient in effecting combustion to combustible gas at the incomplete combustion region, thereby facilitating the combustion.
  • fuel to be supplied to the burners 30 is supplied to the burners 30 from a pulverized coal supply line 33 as pulverized coal which is obtained by crushing coal inside a bunker 29 by means of a mill 35 .
  • a total air quantity for coal combustion is controlled by an air supply system, and the air quantity is distributed to the burners 30 and the after air ports 31 . More specifically, air supplied from a blower 36 is branched into an air supply line 37 a on the burners 30 side and an air supply line 37 b on the after air ports 31 side, which are respectively guided from window boxes 39 a , 39 b into the burners 30 and the after air ports 31 .
  • Distribution of air flow rate to the line 37 a and the line 37 b is adjusted by the damper 40 a on the burners 30 side and the damper 40 b on the after air ports 31 side.
  • the blower 36 is controlled for the output so that a total air flow rate gives a value having specified oxygen concentrations of exhaust gas.
  • Air of less than a theoretical air ratio is supplied from the air supply line 37 a to the burners 30 and pulverized coal is also pneumatically delivered from the pulverized coal supply line 33 thereto.
  • An air fuel mixture injected from the burners 30 into the furnace 34 is less than air quantity necessary for effecting complete combustion, thus resulting in incomplete combustion. At this time, it is possible to reduce NOx. Since fuel undergoes incomplete combustion, a flow of combustible gas is formed downstream of the burners 30 .
  • Air entered through the air supply line 37 b into the window box 39 b of the after air ports 31 is distributed into a primary nozzle 1 , a secondary nozzle 2 and a tertiary nozzle 3 of the air ports 31 to be described later, and supplied to the flow of combustible gas (incomplete combustion region) inside the furnace.
  • the air is mixed with the flow of combustible gas to effect complete combustion, giving combustion gas, thereby heating water and vapor by heat exchangers 42 such as a superheater, evaporator, fuel economizer, and a reheater mounted inside the furnace 34 to produce steam, and thereafter flowing into an outlet of the furnace 34 .
  • boiler water pipes (not illustrated) are arranged on the wall surface of a boiler furnace and heated by combustion of fuel inside the furnace 34 to produce steam.
  • FIG. 2 is a sectional view of the port 31 in the present embodiment (a sectional view taken along line A-A′ in FIG. 4 ).
  • FIG. 3 is a perspective view in which the port 31 is partially omitted.
  • FIG. 4 is a drawing of the port 31 which is viewed from the furnace 34 side.
  • the port 31 is arranged inside the window box 39 b , and the air nozzle mechanism thereof is provided with a primary nozzle 1 , a secondary nozzle 2 for injecting air of rotating flow along the outer circumference of the primary nozzle 1 as secondary air 10 and a tertiary nozzle 3 for injecting air of flow heading from the outside of the primary nozzle 1 to the central axis C of the port 31 as tertiary air 11 .
  • the primary nozzle 1 , the secondary nozzle 2 and the tertiary nozzle 3 are of a coaxial nozzle structure.
  • the primary nozzle 1 , the secondary nozzle 2 and the tertiary nozzle 3 are arranged respectively at the center, outside the primary nozzle 1 and outside the secondary nozzle 2 .
  • the primary nozzle 1 is formed in a straight tubular shape, having an air injection hole 1 A ( FIG. 3 ) at the front end and an air intake hole 1 B at the rear end.
  • a primary damper 5 adjusts an opening area of the air intake hole 1 B, thereby adjusting the flow rate of primary air.
  • the primary nozzle 1 injects air of straight advancing flow parallel to the central axis C of the port 31 as primary air 9 .
  • the opening area of the air intake hole 1 B can be changed by allowing the primary damper 5 to slide on the outer circumference of the primary nozzle 1 by means of an adjusting lever 15 connected to the primary damper 5 to have a handle outside the window box 39 b.
  • the secondary nozzle 2 is provided with an annular air intake hole 2 B ( FIG. 3 ) at the rear end, and a tubular secondary air channel is formed between the inner circumference of the secondary nozzle 2 and the outer circumference of the primary nozzle 1 .
  • Secondary air 10 flowing from the air intake hole 2 B is given a rotating force by a secondary air resistor (a deflection plate) 7 , injected from the secondary nozzle outlet (front end) 2 A in association with a rotating flow along the outer circumference of the primary nozzle 1 .
  • An opening area of the air intake hole 2 B on the secondary nozzle 2 can be changed by allowing the secondary damper 6 to slide toward the central axis C of the port 31 by means of an adjusting lever 16 connected to a cylindrical secondary damper 6 to have a handle outside the window box 39 b , by which the flow rate of the secondary air is adjusted.
  • a plurality of secondary air resistors 7 are attached to a secondary air intake hole 2 B by operating a resistor drive 13 to activate a cooperating mechanism (not illustrated) so that the deflection angle thereof can be similarly changed via a supporting axis 7 a and arranged at the secondary air intake hole 2 B in a circumferential direction.
  • the secondary air resistors 7 are changed in deflection angle, thus making it possible to change a rotating force imparted to the secondary air 10 .
  • the tertiary nozzle 3 is provided with a conical front wall 301 and a conical rear wall 302 arranged so as to face the front wall 301 , and a conical air channel of the tertiary nozzle 3 is formed between the front wall 301 and the rear wall 302 .
  • An air intake hole 3 B of the tertiary nozzle 3 ( FIG. 3 ) is formed in an annular shape, and the opening area can be changed by allowing a tertiary damper 8 to slide along the central axis C of the port 31 by means of an adjusting lever 17 which is connected to the cylindrical tertiary damper 8 and provided with a handle outside the window box 39 b , by which the flow rate of tertiary air is adjusted.
  • the front wall 301 is coupled to the rear wall 302 via a plurality of connection plates 4 arranged at the air intake hole 3 B.
  • the outlet 3 A of the tertiary nozzle 3 is connected to the leading end of the secondary nozzle 2 and formed in such a manner that tertiary air 11 is merged with secondary air 10 and injected into the furnace 34 as air flow 12 .
  • the secondary air 10 which has flown into the secondary nozzle 2 flows into the furnace 34 in a direction parallel to the central axis C of the port 31 . Further, the secondary air 10 is given a rotating force from the secondary air resistor 7 and injected into the furnace 34 .
  • the tertiary nozzle 3 is inwardly inclined to a direction of the central axis C of the port 31 , and tertiary air 11 flowing into the tertiary nozzle 3 is preferably structured in forming a contracted flow concentrating on the port 31 in a direction of the central axis C. A flow ratio of the secondary air 10 to the tertiary air 11 is changed, thus making it possible to adjust a direction at which the air flow 12 is injected after the secondary air 10 is merged with the tertiary air 11 .
  • an inward velocity component of air flow 12 after the secondary air 10 is merged with the tertiary air 11 (a velocity component heading toward the center of the air flow 12 ) is given as 0.
  • the air flow 12 is increased in inward velocity component occupied by the tertiary air 11 and then injected in a direction at which the tertiary nozzle 3 is inclined (an obliquely inward direction)
  • the air flow 12 is adjusted for the injection direction, by which an air-short unburned gas region localized inside the furnace 34 is preferably mixed with combustion air to reduce an unburned portion of fuel. Further, a state of mixture can be adjusted by a rotating strength of the secondary air 10 .
  • the primary damper 5 In order to adjust an air flow ratio of the primary air 9 to the secondary air 10 to the tertiary air 11 at the port 31 , the primary damper 5 , secondary damper 6 and tertiary damper 8 are used.
  • Fuels such as coal and heavy oil contain ash therein. Where these fuels are used, the tertiary air 11 is increased in flow rate and the air flow 12 is concentrated on the port 31 in a direction of the central axis C to give a so-called contracted flow, thus causing a greater turbulence around the contracted flow. Therefore, ambient combustion gas can be easily associated by the contracted flow, and ash fused in a high-temperature combustion gas 25 rising inside the furnace 34 may also be associated and adhered in the vicinity of a water pipe 23 at an outlet of the port 31 to form an ash adhesion layer 18 . This state is shown graphically in a sectional view of the port 31 given in FIG. 14 .
  • FIG. 5 to FIG. 7 show a mechanism of ash adhesion and preventive measures.
  • FIG. 5 to FIG. 7 show the flow velocity distribution (data based on observed results) at the outlet of the port 31 .
  • the longitudinal axis indicates a distance of an AAP from the central axis C in a range from ⁇ 100 to 2300 mm, with C given as an original point, whereas the horizontal axis indicates a distance from the AAP inside the furnace 34 in a range from 0 to 5000 mm.
  • brown indicates a range of 25 to 30 m/s; red, 20 to 25 m/s; pink, 15 to 20 m/s; yellow, 10 to 15 m/s; green, 5 to 10 m/s; blue, 0 to 5 m/s; mazarine, ⁇ 5 to 0 m/s; and dark mazarine, ⁇ 10 to ⁇ 5 m/s. It is noted that minus symbols in mazarine and dark mazarine indicate reverse flow regions. Further, the AAP model used was of a life size (an AAP with dimensions applicable to a 1000 MW boiler), and the experiment was conducted at an air flow rate corresponding to that of an actual machine. However, since the air temperature was an ordinary temperature, the flow velocity was decreased in absolute value. The flow was measured by changing the flow rate of rotating air of the secondary air 10 and that of the primary air 9 , with the contracted flow rate of the tertiary air 11 kept constant.
  • FIG. 5 is a flow velocity distribution diagram of the furnace 34 in a case where the rotation-free straight advancing primary air 9 , the secondary air 10 and the tertiary air 11 flow in the respective quantities of 14%, 62% and 24% as a total. From this drawing, it is apparent that a reverse flow region is formed to a smaller extent at the center portion of the furnace 34 .
  • FIG. 6 shows a case where the primary air 9 , the secondary air 10 of a weak rotating flow and the tertiary air 11 are in the respective quantities of 0%, 70% and 30%.
  • FIG. 7 shows a case where the primary air 9 , the secondary air 10 of a strong rotating flow and the tertiary air 11 are in the respective quantities of 0%, 63% and 37%. From FIG. 6 and FIG. 7 , it is apparent that little difference is found in spread of the air injection flows inside the furnace 34 but a difference is found in flow velocity distribution at the center portion of the furnace 34 . It is noted that the lower sides of FIG. 5 to FIG. 7 correspond to the central axis C of the AAP.
  • a louver 32 from the outlet of the tertiary nozzle 3 along the furnace throat wall 26 is mounted to provide a clearance between the louver 32 and the furnace throat wall 26 from the outlet of the tertiary nozzle 3 through which a partial flow 11 ′, or a part of the tertiary air 11 , flows.
  • the flow 11 ′, or a part of the tertiary air 11 flows so as to seal the surface of the throat wall 26 , thereby making it possible to suppress to the minimum extent combustion-derived ash in association with the contracted flow of the tertiary air 11 from adhering to the surface of the throat wall 26 .
  • FIG. 2 shows a state in which the ash adhesion layer 18 is formed at an inclined region on the furnace throat wall 26 .
  • ash adhered to the region will not influence the performance of an AAP or the performance of a boiler, which may be negligible.
  • the ash adhesion layer 18 shown in FIG. 14 detaches or drops off into the AAP when the boiler is halted, thus influencing the performance of the AAP. For this reason, the layer must be eliminated.
  • FIG. 8 shows a sectional view of the port 31 of Embodiment 2. Additionally, FIG. 9 and FIG. 10 are schematic diagrams of the port 31 , which is a comparative example for comparison with the port 31 of Embodiment 2 given in FIG. 8 .
  • the primary nozzle 1 , the secondary nozzle 2 and the tertiary nozzle 3 are shown, through which the primary air, the secondary air and the tertiary air flow respectively in a concentric manner.
  • a flow from the outer circumference of the tertiary nozzle 3 in the present embodiment toward the central axis C of the port is increased and allowed to flow through a port opening of the furnace 34 (throat wall 26 ), thereby the air injection flow is able to appropriately form a so-called contracted flow.
  • the primary nozzle 1 and the secondary nozzle 2 are not essential in forming the so-called contracted flow.
  • Air flowing through the primary nozzle 1 which is a central air nozzle of the port 31 , forms a straight advancing flow.
  • a secondary air resistor 7 having the rotating function is provided at an inlet of the secondary nozzle 2 , and a major portion including the end portion of the furnace 34 side on the secondary nozzle 2 (an outlet of the secondary nozzle) is a straight tube, with the central axis C of the port being at the center. Therefore, the radius Da at the end portion of the tube inlet of the secondary nozzle 2 given in FIG. 8 is equal to the radius Db at the end portion of the tube outlet thereof.
  • the tertiary nozzle 3 which is different from the primary nozzle 1 and the secondary nozzle 2 , forms an injection flow having an inclined angle of 30° to 70° with respect to the central axis C of the port and is constituted so as to obtain effects of contracted flow.
  • the effects of contracted flow are those generating a strong associated gas 20 , which is an ambient gas inside the furnace 34 , in the vicinity of the throat wall 26 at which a gas channel formed at an opening of the port on the furnace wall is enlarged.
  • the air flow rate of the primary nozzle 1 is adjusted by using a damper 5 disposed at an air intake hole 1 B of the primary nozzle 1 to operate an adjusting lever 15 from outside the window box 39 b , thus adjusting an aperture of the air intake hole 1 B of the primary nozzle 1 .
  • the air flow rate of the secondary nozzle 2 is adjusted by using a damper 6 disposed at an air intake hole 2 B of the secondary nozzle 2 to operate an adjusting lever 16 from outside the window box 39 b , thus adjusting an aperture of the air intake hole 2 B of the secondary nozzle 2 and at the same time a resistor 7 disposed at the air intake hole 2 B of the secondary nozzle 2 is rotated by a secondary air resistor drive 13 , thereby adjusting an air rotating strength.
  • the air flow rate of the tertiary nozzle 3 is adjusted by using a damper 8 disposed at an air intake hole 3 B of the tertiary nozzle 3 to operate an adjusting lever 17 from outside the window box 39 b , thus adjusting an aperture of the air intake hole 3 B of the tertiary nozzle 3 .
  • a throat portion 26 of the furnace wall on the outlet side of the tertiary nozzle 3 (the side heading to the inside of the furnace 34 ) is gradually enlarged in diameter to the downstream side of gas flow with respect to the central axis C of the port 31 as it moves downstream. Additionally, when the tertiary damper 8 is fully closed, a rotating flow from the throat wall 26 of the enlarged pipe configuration and the secondary nozzle 2 forms air flow spreading in a radial direction of the central axis C of the port.
  • a ring-shaped louver 32 which guides a flow 11 ′ or a part of the tertiary air 11 into the throat wall 26 in an outer circumferential direction and the cross section of which is enlarged as it moves toward the furnace 34 side.
  • the leading end of the louver 32 on the upstream side of gas flow (an inlet side of the air nozzle 3 ) is disposed so as to be located on an extended line E of the outer circumferential partition wall of the tertiary nozzle 3 or on the upstream side of gas flow (an inlet side of the air nozzle; a direction moving away from the inside of the furnace) from the extended line E.
  • the port 31 of the present embodiment shown in FIG. 8 is provided with a ring-shaped louver 32 which is enlarged in cross section toward the side closer to the inside of the furnace 34 of the throat wall 26 so as to be parallel to the furnace wall surface of the throat wall 26 of enlarged pipe configuration on the outlet side of the tertiary nozzle 3 (the side toward the inside of the furnace 34 ).
  • FIG. 9 and FIG. 10 show sectional views of the port 31 which is substantially similar in constitution to that given in FIG. 8 .
  • a difference in constitution from the port 31 given in FIG. 8 is that in which in FIG. 9 , the leading end of a louver 32 ′′ on the upstream side of gas flow is provided so as to be located on the downstream side of gas flow from an extended line E of the outer circumferential partition wall of the tertiary nozzle 3 and in FIG. 10 , all the louvers 32 ′′ are disposed so as to be located inside the contracted flow at which a gas flow from the tertiary nozzle 3 heads to the central axis C of the port.
  • the leading end portion of the louver 32 on the upstream side of gas flow in the present embodiment shown in FIG. 8 is disposed in a projecting manner so as to block a part of the tertiary nozzle 3 . Therefore, the leading end portion of the louver 32 on the upstream side creates obstacles to the contracted flow of the tertiary air 11 flowing through the tertiary nozzle 3 , a dynamic pressure is generated by the tertiary air 11 on the outer circumference of the louver 32 (the side of the throat wall 26 ), and a flow 11 ′, or a part of the tertiary air 11 , flows between the louver 32 and the throat wall 26 of enlarged pipe configuration.
  • the associated gas flow 20 in the vicinity of the side wall surface of the furnace 34 is influenced by the flow 11 ′, or a part of the tertiary air 11 , generated in the vicinity of the throat wall 26 , which is a furnace opening, from an arrangement relationship between the louvers 32 ′, 32 ′′ and the tertiary nozzle 3 , thereby giving a circulating flow. Therefore, an ash adhesion layer 18 is formed on the throat wall 26 of the furnace 34 .
  • a radius (Dg) of the leading end of the louver 32 on the downstream side of gas flow (the furnace side) is set to be less than one time, preferably less than 0.95 times a minimum radius (Ds) (hereinafter, sometimes referred to as “throat diameter,” refer to FIG. 12 ) of the throat wall 26 of enlarged pipe configuration of the tertiary nozzle 3 .
  • the radius of the leading end of the louver 32 on the downstream side of gas flow (the furnace side) is set to be less than one time of the radius of the throat wall 26 of enlarged pipe configuration, thereby if the louver 32 is made in an integrated manner (constituted so as not to be divided), it is easy to dispose the louver 32 outside the furnace 34 or to draw it outside the furnace 34 . Further, it is easier to dispose the louver 32 outside the furnace 34 or the like when the radius is set to be less than 0.95 times, with a manufacturing tolerance taken into account. It is noted that the louver 32 is not made in an integrated manner but may be constituted to be divided in a circumferential direction so that it can be easily taken outside the furnace 34
  • the length of a flat surface of the louver 32 on which the diameter is enlarged as it moves to the downstream side of gas flow (a length connecting e part given in FIG. 12 (a circumferential direction) with f part (a circumferential direction)) is set to be 1 ⁇ 2 or lower than the length of the wall surface of the throat wall 26 of enlarged pipe configuration in a gas flow direction (a length connecting h part given in FIG. 12 (a circumferential direction) with i part (a circumferential direction)) so that ash is less likely to adhere to the flat surface.
  • This is not limited to the present embodiment but generally applicable to the present invention.
  • a spreading angle of the louver 32 in a gas flow direction is equal to or greater than a spreading angle of the throat wall 26 of enlarged pipe configuration of the port 31 , it is possible to guide air in a quantity effective in preventing ash adhesion.
  • the damper 8 at the inlet area of the tertiary nozzle 3 is arranged on the side spaced away from the furnace 34 at the inlet area of the nozzle 3 and allowed to slide to a direction at which the damper 8 is brought closer to the furnace 34 when the damper 8 is used to close an air intake hole 3 B of the tertiary nozzle 3 .
  • damper 8 is illustrated as such that in which a cylindrical member slides substantially parallel to the central axis C of the port.
  • a plurality of butterfly-type valves or flaps may be arranged so that the rotating axes are placed circumferentially at a position parallel to the central axis C of the port 31 .
  • This constitution is not limited to the present embodiment but also applicable to each of the following embodiments.
  • the port 31 is of a triple structure.
  • the above effects can be obtained by the port 31 which is not provided with the primary nozzle 1 or the secondary nozzle 2 but constituted only by the tertiary nozzle 3 which is of a contracted flow structure. It is noted that the port 31 which is constituted only by the tertiary nozzle 3 may be used in other embodiments.
  • the louver 32 is structured so as to be supported on the outer channel wall of the tertiary nozzle 3 constituting the contracted flow by means of fixing ribs 27 (refer to FIG. 11 ).
  • thermal expansion is different depending on individual parts of the furnace 34 , by which a distance between the wall surface of the furnace 34 constituting the outer circumference portion of an outermost circumferential air nozzle (the tertiary nozzle 3 in the case of FIG. 8 ) and the central axis C of the port is changed according to operating loads.
  • the louver 32 or the like is fixed from inside the port 31 , thus making it possible to keep constant a clearance between the throat wall 26 of enlarged pipe configuration of the port 31 and the louver 32
  • FIG. 11 is a schematic diagram of the port 31 showing the present embodiment 3.
  • the same parts as those of the constitution given in FIG. 8 are given the same numerals or symbols, an explanation of which will be omitted here.
  • a parallel portion 26 a which is constant in cross section of the channel and parallel to the central axis C is provided on the throat wall 26 of enlarged pipe configuration of the port 31 .
  • a cylindrical portion 32 a running along the parallel portion 26 a is also provided on the louver 32 .
  • the contracted flow from the tertiary nozzle 3 partially flows into a space between the louver 32 and the throat wall 26 of enlarged pipe configuration, a flow 11 ′, or a part of the tertiary air 11 which seals the surface of the throat wall 26 of the furnace 34 , flows effectively in the vicinity of the wall surface of the throat wall 26 , thus making it possible to eliminate a negative pressure in the vicinity of the wall surface of the throat wall 26 . It is, therefore, less likely to cause ash adhesion in the vicinity of the throat wall 26 due to the involvement of ash.
  • FIG. 12( a ) is an enlarged view showing an outlet area of the port 31 given in FIG. 11 , in which the leading end portion of the louver 32 on the upstream side of gas flow (point c) is disposed so as to be located on an extended line E of the outer circumferential wall surface (front wall) 301 of the tertiary nozzle 3 constituting the contracted flow or on the upstream side of gas flow (a direction spaced away from the inside of the furnace) from the extended line E. Additionally, the radius Dg of the leading end on the furnace 34 of the louver 32 is set to be less than one time of the radius Ds of the throat wall 26 so that the louver 32 can be inserted from the window box 39 b .
  • the radius Ds of the parallel portion 26 a on the throat wall 26 of enlarged pipe configuration is set to be greater than the radius Dg of a maximum diameter portion of the louver 32 (radius Dg ⁇ radius Ds).
  • the radius Ds of the parallel portion 26 a on the throat wall 26 of enlarged pipe configuration is desirably set to be less than 0.95 times the radius Dg of the maximum diameter portion of the louver 32 (Ds ⁇ 0.95 Dg).
  • the radius Dp of the parallel portion 32 a of the louver 32 is set to be 20% or lower than the radius Ds of the parallel portion 26 a of the throat wall 26 (1.0 Ds>Dp>0.8 Ds; however, the length Dp is a radius of the cylindrical portion 32 a of the louver 32 (a part parallel to the central axis C of the port)), and if a spreading angle of the louver 32 is made equal to or greater than a spreading angle of the throat wall 26 of the port 31 , it is possible to guide air in a quantity effective in preventing ash adhesion to the throat wall 26 .
  • the radius Dp is made smaller by about 10% with respect to the radius Ds (1.0 Ds>Dp ⁇ 0.9 Ds).
  • an air injection flow for controlling combustion is allowed to arrive at the central portion of the furnace 34 and gases in the vicinity of the furnace wall are also mixed in a facilitating manner.
  • FIG. 12( a ) shows a case where the radius of the port, Da (point a; a radius of an introduction part of the secondary nozzle 2 ) and Db (point b; the edge portion of the partition wall constituting the secondary nozzle 2 on the down stream side of gas flow) are substantially equal to a radius of the throat wall 26 , Ds (a radius of the parallel portion on the throat wall 26 ).
  • Ds a radius of the parallel portion on the throat wall 26
  • similar effects can be obtained in a case where the radius of the throat wall 26 , Ds, is greater or smaller than the radius of the secondary nozzle 2 , Da and Db.
  • the end portion of the louver 32 on the upstream side is arranged in such a range that an absolute value of an angle ⁇ formed by a line G connecting the end portion (point b given in FIG. 12( b )) with the end portion of the louver 32 on the upstream side (point c given in FIG. 12) is lower than 15 degrees.
  • the length of a flat surface of the louver 32 on which the diameter is enlarged as it moves to the downstream side of gas flow (a length connecting e part given in FIG. 12 (a circumferential direction) with f part (a circumferential direction)) is set to be 1 ⁇ 2 or lower than the length of the wall surface of the throat wall 26 in a gas flow direction (a length connecting h part given in FIG. 12 (a circumferential direction) with i part (a circumferential direction)) so that ash is less likely to adhere to the flat surface.
  • the radius of the throat wall 26 , Ds is set to be greater than the radius of the louver 32 , Dg, thereby the louver 32 can be easily drawn outside the furnace wall.
  • FIG. 13 is a schematic diagram showing the port 31 of the present embodiment 4.
  • the same parts as those of the constitution given in FIG. 2 are given the same numerals or symbols, an explanation of which will be omitted here.
  • a parallel portion 26 a which is constant in the cross section area of the channel and parallel to the central axis C is disposed on the throat wall 26 , and a cylindrical portion 32 a is also disposed on the louver 32 .
  • a rotator 22 for inducing a circumferential flow velocity component of the throat wall 26 is disposed between the parallel portion 26 a and the cylindrical portion 32 a of the louver 32 .
  • the contracted flow from the tertiary nozzle 3 partially flows into a space between the louver 32 and the throat wall 26 , the air flow 11 ′ for sealing the surface of the throat wall 26 of the furnace 34 effectively flows in the vicinity of the wall surface on the throat wall 26 of enlarged pipe configuration, thus making it possible to eliminate a negative pressure in the vicinity of the wall surface of throat wall 26 .
  • it is less likely to cause ash adhesion in the vicinity of the throat wall 26 due to the involvement of ash.
  • louver 32 can be decreased in temperature, and heat loss such as thermal deformation and corrosion at high temperature sites is less likely to take place.
  • the ring-shaped louver 32 for guiding gas flow in a direction of the throat wall 26 which is enlarged in the cross sectional area, is disposed at the leading end of the rotator 22 on the downstream of gas flow, it is possible to prevent ash adhesion in the vicinity of a nozzle due to the involvement of ash.
  • the present invention is not limited to a furnace of a boiler but may be applicable to a furnace wall surface of a combustion apparatus to which ash generated from combustion of coal or others can easily adhere.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Supply (AREA)
US12/224,983 2006-03-14 2006-10-27 In-Furnace Gas Injection Port Abandoned US20090087805A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2006-068870 2006-03-14
JP2006068870 2006-03-14
PCT/JP2006/322040 WO2007105335A1 (fr) 2006-03-14 2006-10-27 Orifice d'injection de gaz dans un four

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US20090087805A1 true US20090087805A1 (en) 2009-04-02

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US12/224,983 Abandoned US20090087805A1 (en) 2006-03-14 2006-10-27 In-Furnace Gas Injection Port

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US (1) US20090087805A1 (fr)
EP (1) EP1995517A1 (fr)
JP (1) JPWO2007105335A1 (fr)
CA (1) CA2645680A1 (fr)
WO (1) WO2007105335A1 (fr)

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Publication number Priority date Publication date Assignee Title
WO2011058352A1 (fr) 2009-11-16 2011-05-19 Doosan Power Systems Limited Dispositif de régulation du débit
EP3021046A4 (fr) * 2013-07-09 2017-02-22 Mitsubishi Hitachi Power Systems, Ltd. Dispositif de combustion
TWI665408B (zh) * 2017-02-22 2019-07-11 日商三菱日立電力系統股份有限公司 燃燒裝置
US10375901B2 (en) 2014-12-09 2019-08-13 Mtd Products Inc Blower/vacuum

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JP5530373B2 (ja) * 2011-01-12 2014-06-25 バブコック日立株式会社 ボイラ装置
JP6556871B2 (ja) * 2016-01-20 2019-08-14 三菱日立パワーシステムズ株式会社 アフタエアポート及びこれを備えた燃焼装置

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US5408943A (en) * 1992-01-27 1995-04-25 Foster Wheeler Energy Corporation Split stream burner assembly
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US6068470A (en) * 1998-01-31 2000-05-30 Mtu Motoren-Und Turbinen-Union Munich Gmbh Dual-fuel burner
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WO2011058352A1 (fr) 2009-11-16 2011-05-19 Doosan Power Systems Limited Dispositif de régulation du débit
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US10375901B2 (en) 2014-12-09 2019-08-13 Mtd Products Inc Blower/vacuum
US10674681B2 (en) 2014-12-09 2020-06-09 Mtd Products Inc Blower/vacuum
TWI665408B (zh) * 2017-02-22 2019-07-11 日商三菱日立電力系統股份有限公司 燃燒裝置

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JPWO2007105335A1 (ja) 2009-07-30
WO2007105335A1 (fr) 2007-09-20
EP1995517A1 (fr) 2008-11-26

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