WO2007105335A1 - Orifice d'injection de gaz dans un four - Google Patents

Orifice d'injection de gaz dans un four Download PDF

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Publication number
WO2007105335A1
WO2007105335A1 PCT/JP2006/322040 JP2006322040W WO2007105335A1 WO 2007105335 A1 WO2007105335 A1 WO 2007105335A1 JP 2006322040 W JP2006322040 W JP 2006322040W WO 2007105335 A1 WO2007105335 A1 WO 2007105335A1
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WO
WIPO (PCT)
Prior art keywords
gas
flow
furnace
air
wall
Prior art date
Application number
PCT/JP2006/322040
Other languages
English (en)
Japanese (ja)
Inventor
Yusuke Ochi
Akira Baba
Kouji Kuramashi
Hirofumi Okazaki
Masayuki Taniguchi
Original Assignee
Babcock-Hitachi Kabushiki Kaisha
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 Babcock-Hitachi Kabushiki Kaisha filed Critical Babcock-Hitachi Kabushiki Kaisha
Priority to EP06822958A priority Critical patent/EP1995517A1/fr
Priority to JP2008504973A priority patent/JPWO2007105335A1/ja
Priority to CA002645680A priority patent/CA2645680A1/fr
Priority to US12/224,983 priority patent/US20090087805A1/en
Publication of WO2007105335A1 publication Critical patent/WO2007105335A1/fr

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Classifications

    • 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 ejecting gas into a furnace such as a boiler, and more particularly to a gas ejection port into a furnace such as a boiler suitable for preventing ash adhesion at the opening of the furnace. Background technology.
  • Each furnace wall such as a boiler, is provided with various types of pouches that eject gas such as air and combustion exhaust gas into the furnace.
  • a burner that ejects fuel and combustion air as a combustion device, and an after-air port for introducing two-stage combustion air (also called AAP, over-one air port, or OFA) Etc.
  • the gas ejection port as used in the present specification is not limited to the after-air port ⁇ ⁇ ⁇ ⁇ as long as the gas is ejected into the furnace.
  • a port for a burner the expanded tubular wall surface opened to the furnace provided with the port is referred to as a slot wall or a throat expanded tube portion (furnace wall surface portion where the diameter of the opening portion gradually increases toward the furnace outlet side).
  • the gas jet flow reaches the center of the furnace, and the gas jet flow from the outer periphery of the port rod toward the central axis is strengthened and thrown so as to promote gas mixing near the furnace wall.
  • Patent Documents 1 and 2 below disclose an invention of an after-apart for charging the two-stage combustion air accompanied by the contracted flow into a furnace.
  • the gas ejection port suitable for forming a contracted flow of such a gas jet near the opening of the port, ash adheres and melts on the throat wall of the furnace, and the cleaning force is massive.
  • the function and performance of the port may be hindered by the fact that the massive cleansing force peels off from the wall surface.
  • Patent Document 3 As a technology to prevent ash from adhering and melting to the throat wall opened in the furnace and growing the clinching force into a lump, the pulverized coal panner prevents the adhesion of the clinching force to the throat wall.
  • Patent Document 4 Bernas' Rotor Wall
  • Patent Document 5 Over-Airport
  • 'two-stage combustion technique is used as a low NO x combustion technique that keeps the nitrogen oxide (NO x) concentration in the combustion exhaust gas low.
  • AA P after-air port
  • FIG. 13 shows a drawing of a conventional swivel A A P.
  • a A P shown in FIG. 13 the primary air 9 passes through the primary nozzle 1 and is supplied to the furnace 3 4.
  • a secondary nozzle 2 is provided on the outer periphery of the primary nozzle 1 to supply secondary air 10. It is necessary to properly arrange the AAP with the above structure in the furnace 34, but because of the limited number of AAP installed, the combination of air and unburned gas in the vicinity of the AAP and in the center of the furnace 34
  • the secondary nozzle 2 is provided with a swirler 7 for the purpose of strengthening, and the swirler 7 is used for the combination of air and unburned gas in the furnace 3 4 near the AAP. Is used, and a structure in which air and unburned gas are mixed by a strong air jet reaching the center of the furnace 34 from the primary nozzle 1 is used (Patent Document 6).
  • the swirling secondary air flow using the swirler 7 does not sufficiently spread the swirling air flow, and in the region along the inner wall 3 4 a of the furnace 34, the mixing of unburned gas and combustion air is not sufficient There is.
  • a tertiary having a current drift that can supply combustion air in the direction along the inner wall 3 4 a of the furnace 3 4 to the outer peripheral portion of the secondary nozzle 2 having the swirler 7.
  • the applicant has proposed an AAP with a tertiary nozzle for air (Patent Document 7).
  • Patent Document 1 Japanese Patent Laid-Open No. 2 0 0 6 — 1 3 2 8 1 1 Patent Document 2 Japanese Patent Laid-Open No. 2 0 0 6-1. 3 2 7 9 8
  • Patent Document 3 Japanese Utility Model Publication No. 6-6 9 0 9
  • Patent Document 4 Japanese Patent No. 3 6 6 8 9 8 9
  • Patent Document 5 Japanese Patent Laid-Open No. 10-0 1 2 2 5 4 6
  • Patent Document 6 Japanese Patent Application Laid-Open No. 6 2-1 3 8 6 0 7
  • Patent Document 7 Japanese Patent Laid-Open No. 9-1 1 2 8 1 6 Disclosure of Invention
  • the problem of the present invention is that the ash adheres and melts on the wall surface of the furnace throat pipe expansion section without causing an increase in cost, regardless of conditions such as the flow rate of the ejected gas.
  • air is used as a gas to prevent mass growth, the combustion air and unburned gas in the vicinity of the furnace wall are stably mixed, and the combustion air enters the center of the furnace.
  • the aim is to provide a gas ejection port that can be reliably reached and reduce the NOX concentration in the combustion gas.
  • the invention according to claim 1 is provided on a furnace wall of a fire, and has a velocity component flowing toward a central axis of a gas flow perpendicular to the furnace wall and a velocity component flowing along the central axis, A flow path for contraction flow formed obliquely from the upstream side of the flow toward the central axis, and a gas flow path formed in the furnace wall opening 'part on the downstream side of the flow path for contraction flow A throat expansion section that sequentially expands in the direction of gas flow, and a flow path for contraction flow generation for guiding the gas flowing through the flow path for contraction flow to flow along the wall surface of the pipe expansion section.
  • the gas induced in the cylinder having the configuration of the invention according to claim 1 effectively flows in the vicinity of the wall surface of the throat pipe expansion portion, and the negative pressure in the vicinity of the wall surface of the pipe expansion portion can be removed. Since the gas flowing along the outer peripheral side wall surface of the flow channel (nozzle partition wall constituting the flow channel) can be effectively guided to the wall surface side of the throat expanded portion, the throat expanded portion due to ash entrainment and its vicinity Ashes are unlikely to form on the walls of the wall. Furthermore, in the past, instead of using a ruber, an outlet for ejecting a cooling body such as air was separately provided in the gas ejection port. In contrast, in the invention according to claim 1, the louver is provided. By using it, the pressure loss of the gas jet flow can be reduced, the structure is simplified, and there is no need to install an ash adhesion suppression seal air regulator. It can be reduced. .
  • the gas flow ejected from the flow path for contracted flow generation according to the first aspect of the invention becomes a gas flow that accelerates gas mixing reaching the center of the furnace and gas mixing in the vicinity of the furnace wall. Therefore, when the gas ejection port is used as an AAP for a two-stage combustion panner, a highly reliable fuel capable of low NO x and low CO combustion can be burned.
  • the front end portion of the gas flow upstream side of the rubbing bar is a surface extending from the outer peripheral side wall surface of the contracted flow generation flow passage in the central axis direction or the extended surface.
  • the furnace interior according to claim 1 which is located on the upstream side of the gas flow, and has a pipe expansion portion that is sequentially expanded in the gas flow direction along the wall surface of the pipe expansion portion in the gas flow downstream portion of the louver. This is a gas ejection port.
  • the tip of the louver on the upstream side of the gas flow has a surface where the outer peripheral side wall surface of the contracted flow generation channel extends in the direction of the central axis, or the gas flow flows more than the extended surface. Since it is located on the upstream side, the gas guided to the louver effectively flows in the vicinity of the wall surface of the slot expansion section, and the negative pressure in the vicinity of the wall surface of the expansion section can be removed. Therefore, since the gas flowing along the outer peripheral side wall surface (the nozzle partition wall constituting the flow channel) of the contracted flow generation channel can be effectively guided to the wall surface side of the throat pipe expansion part, Ashes are unlikely to form on the wall surface near the expanded pipe due to the above.
  • the invention according to claim 3 includes a mechanism for changing a ratio of a velocity component flowing along the central axis direction and a velocity component flowing toward the central axis direction of the air flow flowing through the contracted flow generation flow path.
  • a gas ejection port into the furnace according to claim 1 or 2. by changing the ratio of the velocity component flowing along the central axis direction and the velocity component flowing toward the central axis direction, the gas ejection after the merging of the respective velocity components in the furnace
  • the flow direction can be adjusted, and when the gas is air, the unburned gas region with insufficient air that is unevenly distributed in the furnace and the combustion air can be suitably mixed to reduce unburned fuel.
  • the mixed state of the gas after merging can be adjusted by adjusting the swirl strength of the two velocity components.
  • the self-contained invention is capable of adjusting an opening degree of the contraction flow generation channel that starts to open from the outer peripheral wall surface so that gas flows along the outer peripheral side wall surface of the contraction flow generation channel. This is a gas ejection port into the furnace as described in claim 3 with a damper.
  • the outer wall surface side of the flow path for contracted flow generation is adjusted.
  • the damper starts to open, the flow rate of the gas flowing through the contracted flow generation flow path is reduced (the damper is close to the closed state), but the reduced flow generation flow path is close to the portion near the slot expansion section. Since air flows, gas is induced to the louver, and ash adhesion to the throat expansion portion can be prevented. .
  • the invention as set forth in claim 5 is characterized in that a swirling member for swirling gas is provided between the louver and the wall surface of the slot expanding portion. Is.
  • the rubber bar may be divided into a plurality of parts in the circumferential direction of the gas ejection port.
  • the gas flowing between the louver and the wall surface of the slot expansion portion can be ejected into the furnace while being swirled by the revolving member.
  • a part of the contracted flow easily flows from the contracted flow generation flow path, and the gas flow that seals the inner wall surface of the furnace effectively flows in the vicinity of the wall surface of the slot expanding portion. Since the negative pressure in the vicinity of the wall surface can be removed, the expansion of the slot by ash entrainment Ash adhesion in the vicinity of the furnace wall surface of the pipe part can be prevented.
  • the invention according to claim 6 is that the length of the throat expansion portion formed at the downstream end of the louver in the gas flow direction is 1 Z 2 or less of the wall length of the throat expansion tube ⁇ in the gas flow direction.
  • the length of the slot formed at the downstream end of the louver in the gas flow direction of the expanded pipe portion is equal to 1 Z 2 of the wall length of the expanded pipe portion in the gas flow direction. If it is as follows, ash is less likely to adhere to the exposed surface (the surface between the e and f parts in Fig. 12) of the expanded portion of the louver.
  • the invention according to claim 7 is characterized in that the flow path for contracted flow generation is a tertiary nozzle, a primary nozzle through which gas flows along the central axis inside the tertiary nozzle, and a secondary outside the primary and slurries.
  • the gas ejection port is used as an AAP installed on the furnace wall downstream of the two-stage combustion burner, there is no ash adhesion on the furnace wall, and the reliability is high. It can be used to burn fuels that can burn low NO x and low CO.
  • FIG. 1 is a schematic view of a boiler in which the after-airport or the panner of the present invention is used.
  • FIG. 2 is a schematic cross-sectional view of an after air bag of Example 1 of the present invention.
  • FIG. 3 is a perspective view in which a part of the after-apart of the first embodiment is omitted.
  • FIG. 4 is a view of the air port viewed from inside the furnace of the first embodiment.
  • FIG. 5 is a flow velocity distribution diagram of the air flow at the A A P outlet portion performed using the A A P model of FIG.
  • FIG. 6 is a flow velocity distribution diagram of the air flow at the A A P outlet portion performed using the A A P model of FIG.
  • FIG. 7 is a flow velocity distribution diagram of the air flow at the AAP outlet part, which was performed using the AAP model of Fig. 2.
  • FIG. 8 is a schematic cross-sectional view of an after air port according to the second embodiment of the present invention.
  • FIG. 9 is a schematic cross-sectional view of an after air porcelain in which a rubber bar of a comparative example for comparison with the second embodiment of the present invention is arranged along the furnace slot widened portion.
  • FIG. 10 is a schematic cross-sectional view of an after air port in which a comparative bar for comparison with Example 2 of the present invention is arranged in a tertiary nozzle.
  • FIG. 11 is a schematic cross-sectional view of an after air port according to the third embodiment of the present invention.
  • FIG. 1'2 is a schematic cross-sectional view of a partial after-air port for explaining the dimensional relationship when the rubber bar and the throat expansion portion of the third embodiment of the present invention are arranged in the after-air port. .
  • FIG. 13 is a schematic cross-sectional view of an after air bag of Example 4 of the present invention.
  • Fig. ⁇ 4 is a longitudinal sectional view of the AAP structure of the prior art.
  • Fig. 15 is a longitudinal sectional view of a conventional AAP structure. Best Mode for Carrying Out the Invention
  • a plurality of burners 30 are arranged opposite to a pair of opposed furnace walls of a boiler furnace 34, and an after-air port 31 is arranged above the burner installation location.
  • An air-fuel mixture less than the stoichiometric air ratio (for example, 0.8) from the Pana 30 is injected into the flame region inside the furnace 34, and an incomplete combustion region (not shown) is formed in the furnace.
  • the after-air port 3 1 promotes combustion by supplying insufficient air to the combustible gas in the incomplete combustion region.
  • the fuel supplied to PANA 30 is supplied to PANA 30 from the pulverized coal supply line 33 by pulverizing the coal in the ban force 29 using a mill 35.
  • the total amount of air for coal combustion is controlled by the air supply system, and the amount of air is distributed to the Pana 30 and the After Air Port 31.
  • the air supplied from the prober 36 is branched into the air supply line 3 7 a on the side of the parner 30 and the air supply line 3 7 b on the side of the abuter air port 3 1, respectively. a, 3 9 b lead to PANA 30 and after air port ⁇ 31. Air flow to line 3 7 a and line 3 7 b
  • the distribution is adjusted by the damper 40 0 a on the side of the PANA 30 and the damper 40 0 b on the side of the after-airport 31 1.
  • the output of the blower 36 is controlled so that the total air flow rate becomes a value that specifies the oxygen concentration of the exhaust gas.
  • Air below the theoretical air ratio is supplied from the air supply line 3 7 a to the PANA 30, and the pulverized coal is conveyed by air from the pulverized coal supply line 33.
  • the air-fuel mixture jetted from the Pana 30 into the furnace 3 4. is less than the amount of air required for complete combustion, resulting in incomplete combustion. At this time, NOx can be reduced. Since the fuel does not burn completely, a flow of combustible gas is formed downstream of the PANA 30.
  • the air that has entered the air box 3 9 b of the after-air port 3 1 through the air supply line 3 7 b is distributed to the primary nozzle 1, the secondary nozzle 2, and the tertiary nozzle 3 of the air port 3 1 described later. It is supplied to the flow of combustible gas in the furnace (incomplete combustion area). This air is mixed with the flow of combustible gas and burned completely to become combustion gas, which is converted into combustion gas in the furnace 3 4 and steamed to water in the heat exchanger 4 2 installed in the furnace 3 4 After the steam is heated and steam is generated, it flows to the outlet of the furnace 34. Also, a boiler water pipe (not shown) is arranged on the boiler furnace wall surface, and is heated by combustion of fuel in the furnace 34 to generate steam.
  • FIG. 2 is a cross-sectional view of the port 3 1 according to the present embodiment (cross-sectional view taken along the line AA ′ of FIG. 4),
  • FIG. 3 is a perspective view with a part thereof omitted, and
  • FIG. 4 is a port view from the furnace 3 4 side. 3 Each figure showing 1 is shown.
  • the port 3 1 is arranged in the wind box 39 b, and its air nozzle mechanism has a primary nozzle 1 and a secondary nozzle that blows out swirling air along the outer periphery of the primary nozzle 1 as secondary air 1 0. It has a nozzle 2 and a tertiary nozzle 3 that blows out air flowing from the outside of the primary nozzle 1 toward the central axis C of the port ⁇ 3 1 as tertiary air 1 1.
  • the primary nozzle 1, the secondary nozzle 2, and the tertiary nozzle 3 have a coaxial nozzle structure.
  • the primary nozzle 1 is in the center, the secondary nozzle 2 is outside, and the tertiary nozzle 3 is outside. Is arranged.
  • the primary nozzle 1 has a straight tubular shape, has an air outlet 1A (Fig. 3) at the front end, and an air intake 1B at the rear end.
  • the primary damper 5 adjusts the primary air flow rate by adjusting the opening area of the air intake 1B.
  • Primary nozzle 1 ejects straight-flowing air parallel to the central axis C of port ⁇ 3 1 as primary air 5.
  • the opening area of the air intake 1 B is adjusted to the primary damper 5 on the outer periphery of the primary nozzle 1 according to the adjustment lever 1 5 connected to the primary damper 5 and provided with a handle on the outside of the wind box 39 b. It can be changed by
  • the secondary nozzle 2 has an annular air inlet 2B (Fig. 3) on the rear end side, and has a tubular secondary air between the inner periphery of the secondary nozzle 2 and the outer periphery of the primary nozzle 1.
  • a passage is formed
  • the secondary air 10 flowing in from the air inlet 2 B is given a swirling force by the secondary air register (deflecting plate) 7, and the secondary nozzle outlet is accompanied by a swirling flow along the outer periphery of the primary nozzle 1. (Front end) 2 Spout from A.
  • the opening area of the air inlet 2 B of the secondary nozzle 2 is connected to the cylindrical secondary damper 6 and the secondary damper 6 is connected to the windbox 3 9 b by the adjusting lever 1 6 with a handle on the outer side. Slided in the direction of the center axis C of port 3 1
  • the secondary air flow rate is adjusted accordingly.
  • the multiple secondary air registers 7 are operated by operating the register drive 1 3 and the secondary air intake 2 so that the deflection angle can be changed in the same way via the support shaft 7a by a cooperative mechanism (not shown). Attached to B, secondary air intake 2 Multiple in the circumferential direction of B
  • the turning force applied to 20 can be changed.
  • the tertiary nozzle 3 has a conical front wall 3 0 1 and a conical rear wall 3 0 2 disposed opposite to the front wall 3 0 1, and the front wall 3 0 1 and the rear wall 3 0 2 A conical air flow path of the tertiary nozzle 3 is formed between them.
  • the air inlet 3B (Fig. 3) of the tertiary nozzle 3 has a ring shape, and the opening area is connected to the cylindrical tertiary damper 8 and is outside the wind box 39b.
  • Adjustment lever 17 equipped with a handle 25 can be changed by sliding the third damper 8 along the central axis C direction of the rod 3 1, thereby adjusting the tertiary air flow rate.
  • the front wall 3 0 1 and the rear wall 3 0 2 are joined via a plurality of connecting plates 4 arranged in the air intake port 3B.
  • the outlet 3 A of the tertiary nozzle 3 is connected to the tip of the secondary nozzle 2, and the tertiary air 1 1 and the secondary air 10 join together to form an air flow 1 2. It is formed so as to be ejected into the furnace 3 4.
  • the secondary air 10 flowing into the secondary nozzle 2 flows into the furnace 34 in a direction parallel to the central axis C of the port 3 1, and the swirl force is further generated by the secondary air register 7. Given and ejected into the furnace 3 4.
  • the tertiary nozzle 3 has an inward inclination toward the central axis C direction of the port 31. Therefore, the tertiary air flowing into the tertiary nozzle 3.
  • the air 1 1 is in the central axis C direction of the port 31. This is a structure suitable for forming a constricted flow concentrated on the surface.
  • the unburned gas region that is unevenly distributed in the furnace 34 and the combustion air can be suitably mixed to reduce unburned fuel.
  • the mixing state can be adjusted by the strength of the swirling of the secondary air 10.
  • Primary damper 5 Secondary damper 6 and tertiary damper 8 are used to adjust the air flow ratio of primary air 9, secondary air ⁇ 0 and tertiary air 11 of port 3 1.
  • Some fuels contain ash, such as coal, heavy oil, etc., but when using such fuels, increase the flow rate of tertiary air 1 1 and 'port air flow 1 2 When concentrated in the direction of the central axis C of 3 1, so-called contracted flow, the turbulence around the contracted flow increases, and the surrounding combustion gas is easily accompanied by the contracted flow.
  • the ash melted in the combustion gas 25 is also entrained and may adhere to the vicinity of the water pipe 23 at the outlet of the porridge 31 to produce an ash adhesion layer 18. This state is schematically shown in the cross-sectional view of the pouch 31 in FIG.
  • FIGs. 5 to 7 show the flow velocity distribution (actual measurement data) at the outlet of Po ⁇ 31.
  • the vertical axis shows the distance from the central axis C of the AAP, with C as the origin.
  • the horizontal axis shows the distance from the AAP in the furnace 3 4 to 0 to 5 Shown in the range of 0 0 O mm.
  • the color of the flow velocity distribution chart is 25 to 30 m / s for brown, 20 to 25 m / s for red, 15 to 20 m / s for pink, 10 to yellow: L 5 mZ s
  • the dark blue color is 5 to: L 0 m / s, the blue color is 0 to 5 m / s, the dark blue color is -5 to Om / s, and the dark blue color is 10 to 5. m / s. 'Note that the minus sign of dark blue and dark blue represents the reverse flow area.
  • the AAP model used was a full-scale machine (AAP of the size applicable to a 100 MW MW boiler), and the air flow was also tested in the same way as the actual machine.
  • Figure 6 shows the case where the primary air 9 is 0%, the secondary swirling flow of the secondary air 10 is 70%, and the tertiary air 11 is 30%.
  • Fig. 7 shows the case where primary air 9 is 0%, secondary air 10 is 63% of the strong swirling flow, and tertiary air 11 is 37%. 6 and 7, there is little difference in the spread of the air jet in the furnace 34, and there is a difference in the flow velocity distribution in the central part of the furnace 34.
  • the lower side of Figs. 5 to 7 corresponds to the central axis C of A A P.
  • the air flow 1 2 (the confluence of secondary air 10 + tertiary air 1 1) peeled off from the furnace throw wall 2 6 and was reduced in flow. Indicates the situation. Therefore, the ash adhesion layer 18 shown in Fig. 14 is formed on the furnace throat wall 26. It is.
  • a rubar 3 2 is installed along the furnace throat wall 26 from the outlet of the tertiary nozzle 3, and the outlet force of the rubar 3 2 and the tertiary nozzle 3 is set.
  • the space between the furnace throat wall 2 6 and the furnace throat wall 2 6 is provided with an interval in which a partial flow 1 1 ′ of the tertiary air 1 1 flows. Because of this structure, the partial flow 1 1 ′ of the tertiary air 1 1 flows so as to seal the surface of the throat wall 2 6, so that the combustion ash accompanying the contracted flow of the tertiary air 1 1 throat wall 2 Adhering to the surface of 6 can be minimized.
  • FIG. 2 shows the situation where the ash 'adhesion layer 18 is formed on the inclined portion of the furnace throw wall 26, but ash removal in this region is impossible in this embodiment.
  • ash adhesion in this area does not affect the performance of A A P and does not affect boiler performance, so it can be ignored.
  • the ash adhesion layer 18 shown in Fig. 14 must be removed because it has an impact on the A A P performance because it peels and falls into the A A P when the boiler stops. .. '' (Example 2).
  • FIG. 8 shows a cross-sectional view of the port 3 1 of the second embodiment.
  • FIGS. 9 and 10 are schematic diagrams of the port 31 of the comparative example shown for comparison with the port 31 of the embodiment 2 shown in FIG. .
  • the primary nozzle 1 ', the secondary nozzle 2 and the tertiary nozzle 3 are shown as concentric primary air, secondary air and tertiary air, respectively. However, at least the flow from the outer peripheral side of the tertiary nozzle 3 in the present embodiment toward the port central axis C is strengthened to pass through the port opening (slow wall 2 6) of the furnace 3 4. Jet force Any structure suitable for forming a so-called contracted flow may be used. That is, the primary nozzle 1 and the secondary nozzle 2 are not essential for forming a so-called contracted flow.
  • the air flowing through the primary nozzle 1 that is the central air nozzle of the port 3 1 forms a straight flow
  • the secondary nozzle 2 has a secondary air register 7 having a swirling function at the inlet, and the secondary nozzle 2 furnace.
  • the main part including the end on the 4 side (secondary nozzle outlet) is a straight pipe centered on the port center axis C. Accordingly, in FIG. 8, the radius D a of the pipe inlet end of the secondary nozzle 2 is equal to the radius D b of the pipe outlet end.
  • the tertiary nozzle 3 forms a jet flow having an inclination angle of 30 ° to 70 ° with respect to the port center axis C, thereby obtaining a contraction effect. It is said.
  • the contracted flow effect means that the entrained gas 20 of the surrounding gas in the furnace 34 is generated in the vicinity of the inlet wall 26 where the gas flow path formed at the opening of the furnace wall is expanded. It is an effect. ,
  • the air flow rate of the tertiary nozzle 3 can be adjusted by operating the adjustment lever 1 7 from the outside of the wind box 3 9 b by operating the damper 8 provided at the air inlet 3 B of the tertiary nozzle 3 and removing the air from the tertiary nozzle 3. 3 Adjust the opening of B. .
  • the throat part 26 of the furnace wall on the outlet side of the tertiary nozzle 3 (the side going into the furnace 34) has a diameter downstream from the central axis C of the port 31 toward the downstream side of the gas flow. It is expanding.
  • the tertiary damper 8 When the tertiary damper 8 is fully closed, the swirling flow from the expanded throat wall 26 and the secondary nozzle 2 forms an air flow that expands in the radial direction of the port center axis C. Also, in order to prevent ash from adhering to the expanded throat wall 2 6 on the outlet side of the tertiary nozzle 3, a part of the flow 1 1 ′ of the tertiary air 1 1 is thrown in the outer circumferential direction of the wall 2 6.
  • a ring-shaped louver 3 2 is provided that expands as the cross-sectional area goes to the furnace 3 4 side.
  • the upstream end of the gas bar 3 2 (the inlet side of the air nozzle 3) is on the extension line E of the outer wall of the tertiary nozzle 3 or on the upstream side of the gas flow (on the air line) It is provided so that it is located on the nozzle inlet side; the direction away from the inside of the furnace.
  • the port ⁇ 3 1 of this embodiment shown in FIG. 8 is parallel to the furnace wall surface of the expanded wall 1 6 on the outlet side of the tertiary nozzle 3 (the side going into the furnace 3 4).
  • the throat wall A ring-shaped bar 3 2 whose cross-sectional area increases toward the side closer to the inside of the furnace 6 of 26 is provided.
  • FIG. 9 and FIG. 10 show a cross-sectional view of the port 3 1 having the same configuration as FIG. 8, but the configuration different from the port 3 1 in FIG. Gas flow
  • the tip on the upstream side is provided so that it is located on the downstream side of the gas flow downstream of the extension line E of the outer partition wall of the tertiary nozzle 3, and in FIG. 10 all the louvers 3 2 "are from the third nozzle 3.
  • This pouch is provided so as to be located in a contracted flow toward the central axis C.
  • the upstream end of the gas flow upstream of the louver 3 2 of this embodiment shown in FIG. 8 is provided so as to block a part of the tertiary nozzle 3, so that the tertiary air 1 1 flowing through the tertiary nozzle 3 is reduced.
  • the upstream end of the louver 3 2 becomes an obstacle to the flow, and dynamic pressure is generated by the tertiary air 1 1 on the outer periphery side (slow wall 2 6 side) of the louver 3 2.
  • a partial flow 1 1 ′ of tertiary air 1 1 flows between the throat wall 2 6 and the expanded throat wall 2 6.
  • the flow 1 1 ′ which becomes the seal air flowing between the rubber bar 3 2 and the inlet wall 2 6, is induced in the furnace 3 4 by being guided by the rubber 3 2.
  • Flows in the vicinity of the furnace 6 • Entrained gas flow inside the furnace wall (wall seal air flow) 2 0 effectively flows along the inner wall of the furnace 3 4 near the throat wall 2 6 of the port 3 1, Slow ⁇ Wall 2 6 The negative pressure near the wall surface can be removed.
  • the radius (D g) of the gas flow downstream side (furnace side) of the louver 3 2 is the minimum radius (D s) of the expanded tubular throat wall 26 of the tertiary nozzle 3 (hereinafter referred to as “slow”).
  • the diameter is sometimes referred to as “diameter.” Refer to Fig. 12), less than 1 times, particularly preferably less than 0.95 times.
  • louver 3 2 may be divided in the circumferential direction so that the louver 3 2 can be easily taken out of the furnace 3 4 without being integrated.
  • the length of the plane whose diameter increases toward the downstream side of the gas flow of the louver 3 2 (the length of the line connecting the e part (circumferential direction) and the heel part (circumferential direction) in FIG.
  • the length of the line connecting the 10h part (circumferential direction) and the i part (circumferential direction) in Fig. 12 It is desirable that the value be 1 or 2 or less. This applies not only to the present embodiment but also to the present invention as a whole.
  • the spreading angle of the gas bar 3 2 in the gas flow direction is equal to or larger than the spreading angle of the expanded tubular wall 26 of the port 31, it is effective for preventing ash adhesion. It is possible to induce air volume.
  • the damper 8 at the inlet of the tertiary nozzle 3 is arranged on the side away from the furnace 3 4 at the inlet of the nozzle 3, and when the air intake 3B of the tertiary nozzle 3 is closed by the damper 8. It is desirable to slide the damper 8 in a direction approaching the furnace 3 4. This is because even when the air flow rate when the inlet of the nozzle 3 is closed is reduced (the damper 8 is close to the closed state), the expanded throat wall 20 of the pipe 3 1 in the tertiary nozzle 3 20 This is because air flows in a portion close to 26, so that air is guided to louver 3 2 and ash adhesion to the expanded tubular slot wall 26 can be prevented.
  • the damper 8 is shown in the form of a cylindrical member that slides substantially parallel to the port center axis C.
  • a plurality of butterfly-shaped valves or flaps whose rotation axis is the port ⁇ 3 1 It may be arranged in a line in the circumferential direction at a position parallel to the central axis C. This is not limited to the present embodiment but is a configuration example that can be applied to the following embodiments.
  • the port 3 1 has a triple structure. However, the port 3 1 does not have the primary nozzle 1 or the secondary nozzle 2 and is composed only of the tertiary nozzle 3 having a contracted flow structure. The above effect can be obtained even with 3 1. In other embodiments, the point 3 1 may be composed only of the tertiary nozzle 3.
  • an air nozzle such as the secondary nozzle 2 is provided inside the tertiary nozzle 3 shown in FIG. 8, the end of the partition wall constituting the secondary nozzle 2 on the downstream side of the gas flow (point of Fig. I?
  • the configuration of the present embodiment allows the throat wall 2 under any operating conditions of the port 31.
  • the louver 3 2 is supported by a fixing rib 2 7 (see FIG. 11) on the outer flow path wall of the tertiary nozzle 3 constituting the contracted flow.
  • a fixing rib 2 7 see FIG. 11
  • the thermal expansion is different in each part of the furnace 3 4, so that the wall surface of the furnace 3 4 that forms the outer periphery of the outermost air nozzle (the tertiary nozzle 3 in the case of FIG. 8)
  • the distance from Po ⁇ center axis C varies depending on the operating load.
  • FIG. 11 is a schematic diagram of a port 31 showing the third embodiment. In the configuration shown in FIG. 11, the same parts as those shown in FIG. .
  • the expanded tubular throat wall 26 of the port 31 has a parallel portion 26 a parallel to the center axis C with a constant flow path cross-sectional area.
  • the cylinder 3 2 is also provided with a cylindrical portion 3 2 a along the parallel portion 2 6 a.
  • Fig. 12 (a) is an enlarged view of the port 31 first outlet portion of Fig. 11.
  • the tip of the louver 32 on the upstream side of the gas flow is the tertiary nozzle that forms the contracted flow.
  • the outer peripheral side wall surface of 3 (front wall) is located on the extension line E of 301 and on the upstream side of the gas flow (in the direction away from the furnace) from the extension line E.
  • the radius D g of the furnace 3 of the ruby 3 3 is less than one half of the half wall D s of the slot wall 26 so that the ruby 3 2 can be inserted from the side of the wind box 3 9 and b.
  • the radius D s of the parallel portion 2 6 a of the expanded tubular throat wall 2 6 is made larger than the radius D g of the maximum diameter portion of the louver 3 2 (radius D g ⁇ radius D s).
  • the radius D s of the parallel part 2 6 a of the pipe 26 2 is less than 0.95 times larger than the radius D g of the largest diameter part of the bar 3 2 (D s ⁇ 0.95 D. g) is desirable.
  • the radius D p of the parallel portion 3 2 a of the louver 3 2 is 20% or less of the radius D s of the parallel portion 2 6 a of the throat wall 26 (1.0 0 D s> D p ⁇ 0.8 D s
  • the length D p is the radius of the cylindrical portion 3 2 a of the louver 3 2 (part parallel to the port center axis C), and the divergence angle of the louver 3 2 If the angle is equal to or larger than the spreading angle of the low ridge wall 26, it is possible to induce an effective amount of air for preventing ash adhesion to the throat wall 26.
  • the radius Dp with respect to the radius Ds is reduced by about 10% (1.0 D s> D p ⁇ 0.9 D s) I hope that.
  • the air jet for the original combustion control reaches the center of the furnace 3 4, while the vicinity of the furnace wall Facilitate gas mixing This is because the purpose of the contraction flow formation is hindered.
  • the air jet flow from the outer periphery of port 3 1 toward the central axis C is strengthened to pass through the throat part 26, and the air jet is concentrated on the central axis C of the port ⁇ 31 while the throat part is concentrated. It is not desirable that the flow that entrains the gas in the furnace 3 4 around 2 6 cannot be maintained. '
  • Figure 12 (a) shows the port radius D a (point a; radius at the introduction of the secondary nozzle 2) and D b (point b; secondary nozzle 2)
  • D a point a; radius at the introduction of the secondary nozzle 2
  • D b point b; secondary nozzle 2
  • the radius of the slow ⁇ wall 26 the radius of the parallel portion of the throw Dwall 26
  • the radius D s of the throat wall 2 6 is larger or smaller than the radius D a of 2 and the radius D b.
  • the length of the plane of the louver 3 2 whose diameter increases toward the downstream side of the gas flow (the length of the line connecting e 3 ⁇ 4 (circumferential direction) and f part (circumferential direction) in FIG. 12) is In order to prevent ash from adhering to the flat surface, the gas flow in the surface surrounded by the wall length of the slot wall 26 in the gas flow direction (Fig. 12 h part (circumferential direction) and heel part (circumferential direction ')) The length in the direction) should be 1 or 2 or less.
  • FIG. 13 is a schematic diagram of a part 31 showing the fourth embodiment. In the configuration shown in FIG. 13, the same parts as those shown in FIG.
  • a parallel portion 2 6 a parallel to the central axis C having a constant flow path cross-sectional area is provided on the slow trough wall 26 and the cylindrical portion 3 is provided on the louver 3 2.
  • 2 Set a Have A swirler 2 2 for inducing a flow velocity component in the circumferential direction of the throat wall 2 6 is provided between the parallel portion 2 6 a and the cylindrical portion 3 2 a of the cylinder 3 2.
  • the projected area of the surface perpendicular to the port center axis C as seen from the furnace side of the rubber bar 32 can be reduced, and the amount of radiant heat received from the flame can be reduced. For this reason, the temperature of the louver 32 can be reduced, and heat loss such as thermal deformation and corrosion in a high temperature field is unlikely to occur.
  • the ring-shaped louver 3 2 having an enlarged cross-sectional area for guiding the gas flow in the direction of the throat wall 26 6 is provided at the tip of the swirler 22 2 on the downstream side of the gas flow, ash is involved. Can prevent ash adhesion near the nozzle. '.. Industrial applicability
  • the present invention is not limited to boiler furnaces, but can be applied to the furnace wall surfaces of combustion equipment where ash produced by combustion of coal or the like tends to adhere.

Abstract

La présente invention concerne une buse tertiaire (3) d'orifice (31) servant à injecter du gaz dans un four (34) qui comprend : un canal générant un flux restreint disposé de manière oblique vers l'axe central (C) à partir du côté situé en amont du flux de gaz de telle sorte que le flux de gaz possède une composante vitesse partant du côté circonférentiel externe de l'orifice (31) et se dirigeant vers l'axe central (C) ainsi qu'une composante vitesse se dirigeant le long de l'axe central (C) vers l'intérieur du four ; et un volet (32) destiné au guidage disposé de manière à permettre au gaz de s'écouler le long de la surface de la paroi de rétrécissement (26) d'une configuration de tuyau élargie dans laquelle le canal de gaz est élargi sur l'ouverture d'une paroi de four disposée sur une zone de sortie du canal générant un flux restreint. On peut ainsi obtenir un orifice d'injection de gaz qui sans dépendre de conditions telles que le débit du flux de gaz injecté par l'orifice, sans entraîner de complication relative à la configuration de l'appareil ou d'augmentation du coût, permet d'empêcher la croissance de morceaux de clinker provoquée par l'adhésion de la cendre et la fusion sur la surface mural de la partie tuyau de rétrécissement élargie du four.
PCT/JP2006/322040 2006-03-14 2006-10-27 Orifice d'injection de gaz dans un four WO2007105335A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP06822958A EP1995517A1 (fr) 2006-03-14 2006-10-27 Orifice d'injection de gaz dans un four
JP2008504973A JPWO2007105335A1 (ja) 2006-03-14 2006-10-27 火炉内への気体噴出ポート
CA002645680A CA2645680A1 (fr) 2006-03-14 2006-10-27 Orifice d'injection de gaz dans un four
US12/224,983 US20090087805A1 (en) 2006-03-14 2006-10-27 In-Furnace Gas Injection Port

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006068870 2006-03-14
JP2006-068870 2006-03-14

Publications (1)

Publication Number Publication Date
WO2007105335A1 true WO2007105335A1 (fr) 2007-09-20

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PCT/JP2006/322040 WO2007105335A1 (fr) 2006-03-14 2006-10-27 Orifice d'injection de gaz dans un four

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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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WO2012096319A1 (fr) * 2011-01-12 2012-07-19 バブコック日立株式会社 Dispositif de chaudière
WO2015005350A1 (fr) * 2013-07-09 2015-01-15 バブコック日立株式会社 Dispositif de combustion
WO2017126240A1 (fr) * 2016-01-20 2017-07-27 三菱日立パワーシステムズ株式会社 Orifice de post-air, et dispositif de combustion le comprenant
WO2018155102A1 (fr) * 2017-02-22 2018-08-30 三菱日立パワーシステムズ株式会社 Dispositif de combustion

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GB0919964D0 (en) 2009-11-16 2009-12-30 Doosan Babcock Energy Ltd Flow control device
US10375901B2 (en) 2014-12-09 2019-08-13 Mtd Products Inc Blower/vacuum

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JPH066909U (ja) 1992-06-25 1994-01-28 石川島播磨重工業株式会社 微粉炭バーナ
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JP2012145267A (ja) * 2011-01-12 2012-08-02 Babcock Hitachi Kk ボイラ装置
WO2015005350A1 (fr) * 2013-07-09 2015-01-15 バブコック日立株式会社 Dispositif de combustion
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JPWO2015005350A1 (ja) * 2013-07-09 2017-03-02 三菱日立パワーシステムズ株式会社 燃焼装置
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WO2017126240A1 (fr) * 2016-01-20 2017-07-27 三菱日立パワーシステムズ株式会社 Orifice de post-air, et dispositif de combustion le comprenant
WO2018155102A1 (fr) * 2017-02-22 2018-08-30 三菱日立パワーシステムズ株式会社 Dispositif de combustion
CN110300871A (zh) * 2017-02-22 2019-10-01 三菱日立电力系统株式会社 燃烧装置

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CA2645680A1 (fr) 2007-09-20
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US20090087805A1 (en) 2009-04-02

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