EP2667094A1 - Festbrennstoffbrenner und verbrennungsvorrichtung damit - Google Patents

Festbrennstoffbrenner und verbrennungsvorrichtung damit Download PDF

Info

Publication number
EP2667094A1
EP2667094A1 EP12736749.8A EP12736749A EP2667094A1 EP 2667094 A1 EP2667094 A1 EP 2667094A1 EP 12736749 A EP12736749 A EP 12736749A EP 2667094 A1 EP2667094 A1 EP 2667094A1
Authority
EP
European Patent Office
Prior art keywords
combustion gas
pressure detection
flow rate
duct
solid fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12736749.8A
Other languages
English (en)
French (fr)
Inventor
Jun Kashima
Hitoshi Okimura
Noriyuki Ohyatsu
Yusuke OCHI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Power Ltd
Original Assignee
Babcock Hitachi KK
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 KK filed Critical Babcock Hitachi KK
Publication of EP2667094A1 publication Critical patent/EP2667094A1/de
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D1/00—Burners for combustion of pulverulent fuel
    • F23D1/005—Burners for combustion of pulverulent fuel burning a mixture of pulverulent fuel delivered as a slurry, i.e. comprising a carrying liquid
    • 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 
    • F23C5/00—Disposition of burners with respect to the combustion chamber or to one another; Mounting of burners in combustion apparatus
    • F23C5/08—Disposition of burners
    • 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 
    • F23C5/00—Disposition of burners with respect to the combustion chamber or to one another; Mounting of burners in combustion apparatus
    • F23C5/08—Disposition of burners
    • F23C5/28—Disposition of burners to obtain flames in opposing directions, e.g. impacting flames
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D1/00—Burners for combustion of pulverulent fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N3/00—Regulating air supply or draught
    • F23N3/002—Regulating air supply or draught using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N3/00—Regulating air supply or draught
    • F23N3/02—Regulating draught by direct pressure operation of single valves or dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N5/00—Systems for controlling combustion
    • F23N5/18—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel
    • F23N5/184—Systems for controlling combustion using detectors sensitive to rate of flow of air or fuel using electronic means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2225/00—Measuring
    • F23N2225/04—Measuring pressure
    • F23N2225/06—Measuring pressure for determining flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23N—REGULATING OR CONTROLLING COMBUSTION
    • F23N2235/00—Valves, nozzles or pumps
    • F23N2235/02—Air or combustion gas valves or dampers
    • F23N2235/06—Air or combustion gas valves or dampers at the air intake

Definitions

  • the present invention relates to a burner that is mainly used in a thermal power generation plant and combusts a solid fuel such as pulverized coal and a combustion device using the burner.
  • a boiler that comprises a plurality of burners that combust a solid fuel such as pulverized coal and adopts a two-stage combustion system as a measure for reducing NOx in a combustion exhaust gas of the fuel in the burners, to achieve both a reduction in air excess ratio and a reduction in emission of unburned combustible such as CO
  • a technology WO 2008/133051A1
  • a flow rate of the solid fuel is measured in accordance with each burner and combustion air that is complementary with this rate is input from each burner or a two-stage combustion air port (which will be also referred to as an after-air port: AAP or an over-fire air port: OFA). It is required to have the capability of measuring and adjusting a flow rate of a combustion gas accurately in accordance with each burner in order to apply the technology to an actual boiler.
  • a flow of the combustion air ejected from each burner is greatly affected by a configuration of the burner, especially a conformation of the flow path for the combustion gas.
  • To accurately measure and adjust a flow rate of the combustion gas in accordance with each burner it is desirable to provide a long linear flow path in the vicinity of measuring means or adjusting means so that the combustion gas can uniformly flow.
  • a conformation of the flow path that can uniform a flow of the combustion air cannot be necessarily adopted, drift may be locally produced, and the measurement and the adjustment of a flow rate may be affected.
  • the drift is apt to be generated. Furthermore, in a burner that actively adjusts each flow rate of the combustion gas flowing through divided flow paths, the number of targets is increased, and an adjustment width or an adjustment frequency is also increased, thus resulting in a highly demanding problem.
  • a solid fuel burner comprising: a cylindrical fuel nozzle (10) that discharges a mixed fluid of a solid fuel and a carrier gas into a furnace (40) from a wall surface of the furnace (40); a cylindrical combustion gas throat (6) that is provided at an outer periphery of the fuel nozzle (10) and discharges a combustion gas into the furnace (40); a duct (2) that constitutes a flow path for the combustion gas that is connected to the combustion gas throat (6) ; flow rate adjusting means (1) for the combustion gas that is provided in the duct (2) ; and a differential pressure detection device (32, 35) that detects a pressure difference (a differential pressure) between the combustion gases flowing on the upstream side and the downstream side in the duct (2), the solid fuel burner characterized in that the duct (2) has an inlet opening (8) into which the combustion gas is taken from one direction orthogonal to a central axis direction of the fuel nozzle (10) and is formed
  • a second aspect of the invention provides the solid fuel burner according to the first aspect, characterized in that the flow path for the combustion gas in the duct (2) that is connected to the combustion gas throat (6) is divided by a partition wall (4) into a plurality of flow paths that the combustion gas does not flow from one flow path to another, and the upstream-side pressure detection point (31, 33) and the downstream-side pressure detection point (30, 34) are provided to each of the plurality of flow paths.
  • a third aspect of the invention provides the solid fuel burner according to the first aspect, characterized in that the downstream-side pressure detection point (30, 34) is provided on the combustion gas throat (6) where an interval between the combustion gas flow paths in a radial direction becomes maximum with the central axis of the fuel nozzle (10) being determined as a reference.
  • a fourth aspect of the invention provides the solid fuel burner according to the first aspect, characterized in that the differential pressure detection device (32, 35) is configured to detect a value of a differential pressure between an upstream-side pressure and a downstream-side pressure of the combustion gas in the duct (2) through respective pressure conduits constituting the upstream-side pressure detection point (31, 33) and the downstream-side pressure detection point (30, 34).
  • a fifth aspect of the invention provides a combustion apparatus comprising solid fuel burners (44) according to the first aspect on a plurality of stages along an up-and-down direction and in a plurality of rows along a furnace width direction on a wall surface of a furnace (40), the solid fuel burners (44) characterized in that the combustion apparatus comprises solid fuel flow rate measuring means (71) for individually adjusting and measuring flow rates of a solid fuel that flows into the plurality of solid fuel burners (44),and a control device (37) is configured to adjust an opening degree of flow rate adjusting means (1) for a combustion gas based on a combustion gas flow rate detected by a differential pressure detection device (32, 35) of each solid fuel burner (44) in accordance with a change in solid fuel flow rate measured by the solid fuel flow rate measuring means (71), and to individually control each flow rate of the combustion gas.
  • the combustion apparatus comprises solid fuel flow rate measuring means (71) for individually adjusting and measuring flow rates of a solid fuel that flows into the plurality of solid fuel burners (44),and a control device (37)
  • the stagnation region 90 ( FIG. 2 , FIG. 3 ) for the combustion gas in which each upstream-side pressure detection point 31 or 33, one of pressure detection points, is set means a region where a flow velocity of the combustion gas is nearly zero or relatively minimum in the flow path.
  • a portion near the inner wall of the duct 2 which is the farthest from the inlet opening 8 of the duct 2 for the combustion gas corresponds to each upstream-side pressure detection point 31 or 33.
  • the flow path of the cube is constituted of a front wall 56 close to the furnace side, a rear wall 57 which is provided to be parallel to the front wall 56 at an interval and placed at a position distanced from the furnace side, and a sidewall 55 which connects ridge line portions of the front and rear walls 56 and 57
  • a region of the sidewall 55 that faces and is the farthest from an inlet opening surface of the duct 2 which functions as the inlet opening 8 of the combustion air corresponds to each upstream-side pressure detection point 31 or 33.
  • each of the front wall 56 and the rear wall 57 is ovalized and has a U-like shape as a whole (see FIG. 2 ) and the sidewall 55 separates the flow path (the duct 2) for the combustion gas from the outside over linear portions and curved portions of the ridge lines of the front wall 56 and the rear wall 57, a top portion of a curved surface formed of the sidewall 55 corresponds to each of the upstream-side pressure detection points 31 or 33 ( FIG. 1 ).
  • the top portion of the curved surface formed of the sidewall 55 can function as a region where a flow path cross-sectional area of the duct 2, i.e., an area of the duct cross section orthogonal to the flow direction of the combustion gas in the straight portion of the duct 2 through which the combustion gas travels straight from the inlet opening 8 of the duct 2 approximates zero without limit.
  • FIG. 1 shows an example of the oval shape
  • FIG. 1 shows an example of the oval shape
  • a region where a plane including a top portion of the long-diameter portion and the central axis of the fuel nozzle 10 (which is the same plane as a partition wall (a center partition) 4 in the conformation shown in FIG. 1 ) is parallel to a line crossing the sidewall 55 of the duct 2 corresponds to each upstream-side pressure detection point 31 or 33 ( FIG. 1 ).
  • each of the downstream-side pressure detection points 30 and 34 which is the other pressure detection point is provided at a top portion of the combustion gas throat 6 that is the farthest from the partition wall (the center partition) 4 that divides the combustion gas duct 2 into upper and lower portions when the combustion gas throat 6 is arranged in a burner attachment opening 58 ( FIG. 2 ) of the furnace 40.
  • each of these points is present in a region of the combustion gas throat 6 where a difference between the diameter of the concentrically arranged cylindrical combustion gas throat 6 and the short diameter of the fuel nozzle 100 having the oval cross-sectional shape, i.e., a cross-sectional area of the flow path of the duct 2 for the combustion gas with running through a central axis of the fuel nozzle 10 in the radial direction of the fuel nozzle 10 becomes maximum.
  • a cross-sectional area of the flow path of the duct 2 for the combustion gas with running through a central axis of the fuel nozzle 10 in the radial direction of the fuel nozzle 10 becomes maximum.
  • it is present in a region where the plane including the short-diameter portion of the fuel nozzle 10 and the central axis of the fuel nozzle 10 are parallel to a line crossing the fuel gas throat 6.
  • the two pressure detection points are not restricted to one specific point or line, and they are the region which have a given width and more specifically, can also be defined by the following geometric numerical range.
  • the stagnation region 90 ( FIG. 2 , FIG. 3 ) of the combustion gas dust 2 where each upstream-side pressure detection point 31 or 33 is arranged is a region where a flow velocity of the combustion gas is substantially zero or it is relatively minimum in the duct 2, and this region is present in a region that runs through the central axis of the fuel nozzle 10 with the partition wall (the center partition) 4 that divides the downstream-side duct 2 of the duct 2 into upper and lower parts at the center and is surrounded by planes each of which is in the range of 15° on the upper or lower side.
  • the top portion of the combustion gas throat 6 which is the position where each of the downstream-side pressure detection points 30 and 34 is arranged is present in the range of ⁇ 2° in the circumferential direction (see FIG. 12 ) and on the downstream side of a half point of a throat length of the combustion gas throat 6 in the central axis direction when a position at which the difference between the diameter of the throat 6 and the diameter of the flow path of the fuel nozzle 10 becomes maximum (a perpendicular running through the central axis of the combustion gas throat 6 in FIG. 1 ) is determined as a reference.
  • the present invention has the following operation.
  • a value of a differential pressure of the combustion gas at each upstream-side pressure detection point 31 or 33 and each downstream-side pressure detection point 30 or 34 detected by each of the differential pressure detection devices 32 and 35 can be converted into a flow rate of the combustion gas when it is assigned to a predetermined conversion formula, whereby the flow rate of the combustion gas (gas such as air) each burner can be measured.
  • the combustion gas duct 2 has the inlet opening 8 into which the combustion gas is introduced from one direction orthogonal to the central axis direction (a flow direction of the fluid flowing toward the outlet opening portion on the furnace side) of the combustion gas throat 6, and it is formed so that the flow path (the duct) 2 of the combustion gas can bend at a right angle toward the central axis direction of the combustion gas throat 6.
  • the duct 2 is compactly accommodated in a wind box 41 parallel to the wall surface of the boiler furnace 40 while obtaining a duct length required to suppress an influence of drift produced in the duct 2.
  • the flow rate adjusting means 1 for the combustion gas is provided on an upstream-side of the installing portion for each differential pressure detection device 32 or 35 in the duct 2 for the combustion gas.
  • the flow rate adjusting means 1 can reduce a flow velocity distribution of the combustion gas in the duct cross section that is produced and is apt to increase when an opening degree of the inlet opening 8 is small.
  • the flow rate adjusting means 1 which involves a mechanical operation such as opening/closing can be prevented from directly receiving radiant heat from the inside of the furnace 40 or from colliding with clinkers or the like falling from, e.g., the upper side of the furnace 40, and a possibility that damage or an inconvenience of an operation caused thereby can be lowered.
  • each of the differential pressure detection devices 32 and 35 determines an inner wall position of the duct 2 farthest from the inlet opening 8 of the duct 2 corresponding to the stagnation region 90 of the combustion gas on the wake side of the flow rate adjusting means 1 as each of the upstream-side pressure detection points 31 and 33, an influence of a dynamic pressure acting on each of the pressure detection points 31 and 33 is reduced, and the combustion gas flow rate can be measured without being affected by the drift of the combustion gas because the downstream-side pressure detection points 30 and 34 are arranged on the top portion wall surface and the bottom portion wall surface of the combustion gas throat 6, thereby highly accurately measuring the flow rate of the combustion gas.
  • the duct 2 for the combustion gas connected to the combustion gas throat 6 is divided into two portions by the partition wall (the center partition) 4, and the upstream-side pressure detection points 31 and 33 and the downstream-side pressure detection points 30 and 34 are provided to the respective divided flow paths.
  • the flow rates of the combustion gas flowing through the plurality of ducts 2 are deviated on upper and lower sides of the combustion air outlet opening 7 of the burner 44, accurate adjustment can be individually carried out, a flame forming position in the furnace 40 can be controlled, and NOx concentration of a nitrogen oxide in a combustion exhaust gas can be effectively reduced, or an amount of heat transfer to a heat transfer tube (not shown) installed in the boiler furnace 40 can be effectively controlled.
  • the duct 2 When the duct 2 is divided into the plurality of flow paths, the number of targets of the combustion gas flow rate measurement and adjustment is increased, the flow rate is actively changed in accordance with each flow path, its span of adjustable range or frequency is thereby increased, and hence the configuration using the upstream-side pressure detection points 31 and 33 and the downstream-side pressure detection points 30 and 34 has high importance.
  • the shape of the cross section of the fuel nozzle 10 orthogonal to the central axis direction (the flow direction of the fluid flowing toward the outlet opening on the furnace side) in which drift of the combustion gas is apt to be generated is the rectangular shape, the oval shape, or the elliptic shape having the long-diameter portion and the short-diameter portion, when each of the downstream-side pressure detection points 30 and 34 is provided on the outer wall surface of the combustion gas throat 6 where the flow path cross-sectional area of the combustion gas in the radial direction becomes maximum with the central axis of the combustion gas throat 6 determined as the reference, the flow rate of the combustion gas can be accurately measured with being hardly affected by the drift.
  • each of the differential pressure detection devices 32 and 35 can be easily realized without greatly increasing facility cost.
  • a combustion apparatus such as a boiler that comprises the solid fuel flow rate measuring means 71 provided in a plurality of stages in the vertical direction and a plurality of rows in the furnace width direction on the wall surface of the furnace 40 in particular and individually measure the flow rate of the solid fuel flowing into the solid fuel burner 44 and that is configured to individually control the combustion gas flow rate of each solid fuel burner 44 in accordance with a change in fuel flow rate measured by the solid fuel flow rate measuring means 71, when the flow rate of the combustion gas flowing through each of the plurality of flow paths must be individually accurately adjusted, this is important since the number of required devices is large. It is to be noted that this configuration can be applied not only the combustion device according to the present invention but also any other combustion devices using the solid fuel burner 44.
  • the duct 2 of the combustion gas has the inlet opening 8 into which the combustion gas is introduced from one direction orthogonal to the central axis direction of the combustion gas throat 6, the duct 2 is formed to bend at a right angle toward the central axis direction of the combustion gas throat 6, the flow rate adjusting means 1 for the combustion gas is provided at the anterior flow portion in the duct 2 for the combustion gas, and hence the length of the duct 2 can be assured to some extent, whereby the flow rate adjusting means 1 can decrease spread of the flow velocity distribution of the combustion gas in the duct cross section for the combustion gas that is produced and apt to increase when an opening degree of the inlet opening 8 is small in particular.
  • each of the upstream-side pressure detection points 31 and 33 is provided in the stagnation region 90 of the combustion gas in the duct 2, the flow rate of the combustion gas can be highly accurately measured with being hardly affected by a dynamic pressure acting on each of the upstream-side pressure detection points 31 and 33, and assigning a value of the differential pressure detected by each of the differential pressure detection devise 32 and 35 into a predetermined conversion formula (1) enables conversion into a flow rate of the combustion gas and allows each burner to measure a flow rate of the combustion gas (gas such as air). In this manner, the combustion gas flow rate can be measured without being affected by drift of the combustion gas.
  • the duct 2 can be compactly accommodated in the wind boxy 41 parallel to the wall surface of the boiler furnace 40 while obtaining a duct length required for suppressing an influence of the drift produced in the duct 2 for the fuel gas.
  • the flow rate adjusting means 1 since the flow rate adjusting means 1 is provided in the duct 2, the flow rate adjusting means 1 that involves a mechanical operation such as opening/closing can be prevented from directly receiving the radiant heat from the furnace 40 or from colliding with clinkers or the like falling from, e.g., the upper side of the furnace 40, thus lowering a possibility that damage or an inconvenience of an operation caused thereby occurs.
  • the flow rate of the combustion gas flowing through each of the plurality of ducts 2 can be individually and accurately adjusted on the upper and lower sides, and the forming position of a flame in the furnace 40 can be controlled.
  • the number of targets for measurement and adjustment of the combustion gas flow rate is increased, and the flow rate can be actively changed in accordance with each flow path, whereby the flow rate can be finely adjusted.
  • the shape of the cross section of the fuel nozzle 10 orthogonal to the central axis direction (the flow direction of the fluid flowing toward the outlet opening on the furnace side) in which drift of the combustion gas is apt to be produced is the rectangular shape, the oval shape, or the elliptic shape having the long-diameter portion and the short-diameter portion, when each of the downstream-side pressure detection points 30 and 34 is provided on the outer wall surface of the combustion gas throat 6 where the flow path cross-sectional area of the combustion gas in the radial direction becomes maximum with the central axis of the fuel nozzle 10 determined as a reference, the flow rate of the combustion gas can be accurately measured with being hardly affected by the drift.
  • each of the differential pressure detection devices 32 and 35 can detect a value of the differential pressure between the upstream-side pressure and the downstream-side pressure of the combustion gas in the duct 2 through the pressure conduits connected to each upstream-side pressure detection point 31 or 33 and each downstream-side pressure detection point 30 or 34, and it can be easily realized without greatly increasing facility cost.
  • the flow rates of the solid fuel flowing into the plurality of solid fuel burners 44 in the combustion device are individually adjusted and measured by the solid fuel flow rate measuring means 71, the control device 37 adjusts an opening degree of the flow rate adjusting means 1 for the combustion gas based on each combustion gas flow rate detected by the differential pressure detection device 32 or 35 of each solid fuel burner 44 in accordance with a change in measured solid fuel flow rate, and the control device 37 individually controls each flow rate of the combustion gas, thereby rapidly coping with a change in solid fuel flow rate of each burner 44.
  • adjusting the combustion gas alone can suffice, and the adjusting means can have a simpler configuration as compared with a case where the solid fuel is conveyed with use of a carrier gas.
  • a solid fuel especially pulverized coal, woody biomass, or a mixture of the pulverized coal and the woody biomass is combusted as a main fuel by a solid fuel burner, but a type of fuel is not necessarily restricted, and a liquid or a gas may be used as a main fuel.
  • air is assumed to be used as a combustion gas, but the air alone is not necessarily restricted, and a recirculating gas of a combustion exhaust gas, a high-oxygen concentration gas, or a mixed gas of the various kinds of gases may be used.
  • FIG. 1 is a schematic perspective view of a solid fuel burner according to an embodiment of the present invention
  • FIG. 5 is a schematic front view ( FIG. 5(a) ) and a side view ( FIG. 5 (b) ) when the solid fuel burners 44 to which the present invention is applied are incorporated in a boiler furnace 40.
  • Combustion air enters burners 44 from a wind box 41 provided on the outer side of a sidewall of the boiler furnace 40 shown in FIG. 5 through a combustion air duct 2 depicted in FIG. 1 and flows into the furnace 40 from a combustion air throat 6 provided at an opening portion of the sidewall of the furnace 40.
  • pulverized coal and its carrier air are ejected into the furnace 40 through a solid fuel carrying tube (a fuel nozzle) 10.
  • the combustion air throat 6 that ejects the combustion air into the furnace 40 is provided on the outer peripheral side of the solid fuel carrying tube 10, and the combustion air is supplied into the combustion air throat 6 from the combustion air duct 2.
  • An air inlet opening 8 into which the combustion air from the window box 41 is introduced is provided in the combustion air duct 2, an air inflow direction of the air inlet opening 8 indicated by an arrow B in FIG. 1 is provided to be parallel to a furnace wall surface on which a burner 44 is installed so that the combustion air is bent at a substantially right angle from the air inlet opening 8 and is spouted into the furnace 40 from a combustion air outlet opening 7 toward the furnace wall surface.
  • the combustion air duct 2 is provided at the outer peripheral portion of the solid fuel carrying tube (the fuel nozzle) 10, and the air that has flowed into the air inlet opening 8 is bent at a substantially right angle to surround the outer peripheral portion of the solid fuel carrying tube 10 and supplied to the combustion air throat 6.
  • an outlet opening portion of the solid fuel carrying tube 10 has a flow path formed into an oval configuration as seen from the inside of the furnace 40, whereas an outlet opening of the throat 6 has a gas flow path formed into a circular configuration as seen from the inside of the furnace. Therefore, the furnace outlet opening of the throat 6 has an opening portion that is large in an up-and-down direction around the outlet opening of the solid fuel carrying tube 10.
  • the combustion air duct 2 is divided into two parts in the up-and-down direction by a center partition 4, and upper air and lower air (combustion gas) do not become confluent in the combustion duct 2. Moreover, the combustion air inlet opening 8 of the combustion air duct 2 is divided by an upper partition 3 and a lower partition 5 and consists of four spaces in total including the spaces divided by the center partition 4, and a combustion air (combustion gas) amount adjustment damper 1 is installed in each of the spaces.
  • FIG. 2 is a detailed perspective view of the combustion air duct 2.
  • the combustion air duct 2 is connected to the combustion air throat 6, and it is constituted of a U-shaped front wall 56 arranged to be parallel to a furnace wall surface on the side close to the furnace wall surface, a U-shaped rear wall 57 arranged to be parallel to the front wall 56 on the side far from the furnace wall surface on the back side of the front wall 56, and a sidewall 55 that has both end portions connected to ridge line portions of the front wall 56 and the rear wall 57 and covers the spaces of the combustion air duct 2.
  • the front wall 56 has a circular opening portion 58 connected to the combustion air throat 6, and the sidewall member 57 has an opening 59 connected to the solid fuel carrying tube 10.
  • the center partition 4 is installed at a position having a height 0.5L1 which is a center position having a height L1 of the inlet opening 8 of the combustion air duct 2, divides the combustion air inlet opening 8 into two parts in the up-and-down direction, and is joined to the front and rear walls 56 and 57 for the configuration of the duct 2, and the spaces in the combustion air duct 2 divided into two parts in the up-and-down direction by the center partition 4 are independent from each other so that the combustion air does not flow into or out from these spaces.
  • an upper partition plate 3 and a lower partition plate 5 are arranged, respectively.
  • the upper partition plate 3 is arranged on the lower side with a height L3 from a top portion of the combustion air inlet opening 8
  • the lower partition plate 5 is arranged on the upper side with a height L4 from a bottom portion of the combustion air inlet opening 8, and these plates are arranged so as to be parallel to the center partition 4.
  • the height L3 and the height L4 can be arbitrarily determined, they must be set not less than a length of a blade of the damper 1 in a gas flow direction.
  • a length L6 of each of the upper partition plate 3 and the lower partition plate 5 in the gas flow direction can be also arbitrarily determined, it must be less than a length L5 of the center partition 4 in order to allow the combustion air to flow out from the outlet opening 7 into the furnace 40.
  • the two partition plates i.e., the upper partition plate 3 and the lower partition plate 5 are used as partition members, but an arbitrary number of the partition plates can be used.
  • FIG. 3 is a front view of the combustion air duct 2 as seen from the boiler front side (a front furnace wall of the boiler furnace 40).
  • a curvature radius r2 of a cross-sectional semicircular portion of the sidewall 55 which is a constituent member of the combustion air duct 2 must be set larger than a radius r1 of the combustion air throat 6 (r2>r1). As a result, an effect of alleviating drift at the combustion air outlet opening 7 can be obtained.
  • FIG. 4 is a cross-sectional view taken along a line A-A in FIG. 3 .
  • the combustion air 20 that has flowed into the combustion air duct 2 from the combustion air (the combustion gas) inlet opening 8 bends at a right angle, flows through a space between the combustion air throat 6 and the solid fuel carrying tube 10, and flows out into the furnace 40 from the combustion air outlet opening 7.
  • the space between the combustion air throat 6 and the solid fuel carrying tube 10 is also divided into two parts in the up-and-down direction by the center partition 4 to reach the combustion air outlet opening 7.
  • a combustion air amount is deviated depending on each of the upper and lower sides of the combustion air outlet opening 7, and flames are changed to the upward direction or the downward direction, which is effective for a reduction in NOx concentration of a nitrogen oxide in the combustion exhaust gas or control over an amount of heat transfer to the heat transfer tube (not shown) installed in the boiler furnace 40.
  • the combustion air duct 2 is divided into two parts in the up-and-down direction by the center partition 4 to reach the combustion air outlet opening 7.
  • the center partition 4 allows a combustion air amount to deviate depending on each of the upper and lower sides of the combustion air outlet opening 7, and flames are changed to the upward direction or the downward direction in the boiler furnace 40, which is effective for a reduction in NOx concentration of a nitrogen oxide in the combustion exhaust gas or control over an amount of heat transfer to the heat transfer tube (not shown) installed in the boiler furnace 40.
  • a deviation between measured pressure values at an upstream-side pressure detection point 31 and a downstream-side pressure detection point 30 which are pressure conduits and a deviation between measured pressure values at an upstream-side pressure detection point 33 and a downstream-side pressure detection point 34 which are pressure conduits are measured, respectively.
  • the upstream-side pressure detection points 31 and 33 as the pressure conduits configured to measure a flow rate of the combustion air are disposed in a stagnation region 90 ( FIG. 3 ) of the combustion air duct 2.
  • the stagnation region 90 means the region 90 represented by a filled portion in FIG. 2 and a hatched portion in FIG.
  • downstream-side pressure detection points 30 and 34 as the other pressure conduits are respectively installed at a top portion and a bottom portion of the combustion air throat 6 that are positions at which a difference between the radius r1 of the combustion air throat 6 and an outlet radius r3 of the solid fuel carrying tube 10 becomes maximum.
  • the downstream-side pressure detection points 30 and 34 are disposed on the wall surface of the combustion air throat 6 shown in FIG. 1 with a longitudinal direction of each of the downstream-side pressure detection points 30 and 34 being set in the vertical direction so as not to be affected by a dynamic pressure.
  • An upstream-side fluid pressure (a high-pressure side pressure) of the combustion air flowing through the combustion air duct 2 is led from each of the upstream-side pressure detection points 31 and 33, and a downstream-side fluid pressure (a low-pressure side pressure) of the combustion air is led from each of the downstream-side pressure detection points 30 and 34.
  • the upstream- and downstream-side pressure detection points 30 and 31 as the pressure conduits are connected to the differential pressure detection device 32, the upstream- and downstream-side pressure detection points 33 and 34 are connected to the differential pressure detection device 35, and differential pressures obtained at these points are assigned to the predetermined flow rate conversion formula (1), thereby calculating a flow rate of the combustion air.
  • each of the pressure conduits constituting the upstream- and downstream-side pressure detection points 30 and 31; and 33 and 34 a temperature of the combustion air (approximately 300°C) must be taken into consideration in regard to the material. Furthermore, as to the diameter of each of the pressure conduits constituting the upstream- and downstream-side pressure detection points 30 and 31; and 33 and 34, clogging or the like by dust contained in the combustion air must be taken into consideration, and applying a purge system and the like is also effective.
  • FIG. 5 is a schematic view of the furnace 40 using the burners 44 in which the present invention is incorporated.
  • the wind box 41 is installed in the furnace 40, and a plurality of two-stage combustion air (combustion gas) ports 42 and burners 44 to which the present invention is applied are disposed.
  • a solid fuel supplied from the outside of the furnace 40 is connected to each burner 44 from the solid fuel carrying tubes 10.
  • FIG. 5 shows an example where the burners 44 are disposed on a boiler front side of the furnace 40, and the present invention can be also used for the opposed combustion burners installed on the boiler front side and a boiler rear side of the furnace 40.
  • FIG. 5 shows an example where the two-stage combustion air (combustion gas) ports 42 are installed on two stages, and the number of stages may be one. The six ports 42 are installed in one row in FIG. 5 , but an arbitrary number can be set.
  • FIG. 16 shows an example of a generalized combustion air (combustion gas) flow rate measurement device.
  • FIG. 16 shows an example of a flow rate measurement device using a pitot tube 61.
  • the pitot tube 61 is installed in a flow path 60 with an introduction port of a total pressure detection hole 62 facing a direction opposite to a fluid flow 22.
  • a fluid pressure detected by the total pressure detection hole 62 and a static pressure detection hole 63 is supplied to a differential pressure detection device 67 and assigned to the predetermined flow rate conversion formula (1), thereby calculating a flow rate.
  • FIG. 17 shows an example of a combustion air (combustion gas) flow rate measurement device using an orifice.
  • An orifice 64 is disposed in a perpendicular direction relative to a fluid flow 22 in a flow path 60.
  • Pressure conduits 65 and 66 are installed on the upstream side and the downstream side to sandwich the orifice 64 therebetween.
  • a fluid pressure detected by the pressure conduits 65 and 66 is supplied to a differential pressure detection device 67 and assigned to the predetermined flow rate conversion formula (1), thereby calculating a flow rate.
  • pitot tube 61 In case of the pitot tube 61, a sufficient straight pipe length required in the burner 44 cannot be taken, a measurement accuracy for a fuel flow rate is low, and it may probably be influenced by drift. Although many pitot tubes 61 may be used to measure a given cross section in the flow path 60 at a plurality of positions in order to enhance the flow rate measurement accuracy, costs are disadvantageously high. Additionally, in case of using the orifice 64, unwanted pressure loss occurs because of the flow rate measurement, power for a fan or the like increases in order to supply the combustion air to each burner 44, which is not preferable.
  • the flow rate measurement device detects pressure loss of the combustion air (gas) caused due to the burner configuration by using the upstream- and downstream-side pressure detection points 30 and 31 and the differential pressure detection device 32 or the upstream- or downstream-side pressure detection points 33 and 34 and the differential pressure detection device 35 respectively and converts the pressure loss into a combustion air (gas) flow rate, and unwanted pressure loss concerning the flow rate measurement does not occur. Further, when each appropriate differential pressure detection locus is selected, a differential pressure to be detected is not affected by a change in flow pattern due to an operation of the adjustment damper 1 or by drift, and hence highly accurate flow rate measurement can be carried out.
  • FIG. 6 is a view showing the burner 44 from the boiler front side when an angle ⁇ formed between a perpendicular 52 and the combustion air amount adjustment damper 1 is 30°, the perpendicular 52 being obtained by connecting rotary axes 1a, 1b, 1c, and 1d of a plurality of adjustment dampers 1 which are arranged in parallel near the combustion air inlet opening 8 of the combustion air duct 2, and FIG. 7 schematically shows flow rate deviations at the combustion air outlet opening 7.
  • the dampers 1a, 1b, 1c, and 1d are respectively disposed in a space 50a partitioned by the sidewall 55 and the upper partition 3, a space 50b partitioned by the upper partition 3 and the center partition 4, a space 50c partitioned by the center partition 4 and the lower partition 5, and a space 50d partitioned by the lower partition 5 and the sidewall 55.
  • the angle ⁇ formed between the perpendicular 52 and an extended line 53 of each blade of the damper 1 is 30° (a damper opening degree 30°).
  • a flow 21 of the combustion air in the combustion air duct 2 at this time has such a flow rate that varies as shown in FIG. 7 .
  • the flow rate is high in a region B of the combustion air outlet opening 7, and the flow rate is low in a region A of the outlet opening 7.
  • the flow rate is low in a region C of the outlet opening 7, and the flow rate is high in a region D of the outlet opening 7. This is drift of the combustion air.
  • FIG. 8 and FIG. 9 schematically show the burner 44 from the boiler front side when the angle ⁇ formed between the perpendicular 52 and an extended line 53 of the combustion air amount adjustment damper 1 is 90° (a damper opening degree 90°) and flow rate deviations at the combustion air outlet opening 7.
  • the angle ⁇ varies, the flow 21 of the combustion air differs from that when the damper opening degree is 30° in FIG. 6 . Therefore, the flow rate deviations at the combustion air outlet opening 7 are different from those when the damper opening degree is 30°, the flow rate deviation is high in each of the region B of the combustion air outlet opening 7 and the region C of the outlet opening 7, and the flow rate deviation is low in the region A of the outlet opening 7 and the region D of the outlet opening 7.
  • the damper 1 Since the damper 1 is automatically controlled so that a burner air ratio can have a predetermined value, it is desirable to install the upstream-side and downstream-side pressure detection points 30 and 31; and 33 and 34 as the pressure conduits at positions where these points are not affected by the angle ⁇ formed between the perpendicular 52 and the damper 1.
  • the upstream-side pressure detection points 30 and 31; and 33 and 34 must be installed in the stagnation region 90 ( FIG. 2 , FIG. 3 ) that is not affected by a contracted flow of each damper 1.
  • FIG. 10 shows a result of examination obtained when a full-size model was used.
  • An abscissa represents an opening degree (%) of the combustion air amount adjustment damper 1 relative to the perpendicular 52 in FIG. 6 and FIG. 8
  • an ordinate represents a ratio (dimensionless) of a static pressure relative to burner pressure loss when the flow rate is unchanged.
  • the upstream-side pressure detection points 31 and 33 can be installed at arbitrary positions on the sidewall which is a constituent member of the combustion air (combustion gas) duct 2 included in this range.
  • downstream-side pressure detection points 30 and 34 Positions of the downstream-side pressure detection points 30 and 34 as the pressure conduits will now be examined.
  • the downstream-side pressure detection points 30 and 34 must be installed in a region where these points are not affected by the drift of the combustion air (gas) shown in FIG. 6 to FIG. 9 .
  • FIG. 11 is a schematic view showing installing positions 81 to 83 for the downstream-side pressure detection point 30 in the central axis direction of the combustion air throat 6, and
  • FIG. 12 is a schematic view showing installing positions 84 to 87 for the downstream-side pressure detection point 30 in the circumferential direction of the throat 6.
  • the installing positions 81 to 83 for the downstream-side pressure detection point ( FIG. 11 )
  • the installing position 82 for the downstream-side pressure detection point is set at a position with an intermediate length (0.5 ⁇ L 10 ) of a length L 10 of the throat 6, the installing position 81 for the downstream-side pressure detection point is set on the downstream side of the throat 6, and the installing position 83 for the downstream-side pressure detection point is set on the upstream side of the throat 6.
  • the radius r ⁇ 1 of the throat 6 - the radius r ⁇ 3 of the fuel nozzle 10 Further, as shown in FIG.
  • FIG. 13 and FIG. 14 shows a result of examination obtained when a full-size model was used.
  • An abscissa in each of FIG. 13 and FIG. 14 represents an angle (a damper opening degree) formed between the perpendicular 52 and the combustion air (combustion gas) amount adjustment damper 1 in FIG. 6 and FIG. 8 , and an ordinate in the same represents static pressure/burner pressure loss when the flow rate is unchanged.
  • the static pressure is substantially fixed in the damper opening degree range to be used.
  • the static pressure/burner pressure loss is substantially fixed in the range that is approximately 10 to 80% of the damper opening degree range to be used.
  • a differential pressure detected by each of the burner differential pressure detection devices 32 and 35 shown in FIG. 1 is 100 Pa or more, and hence this differential pressure only slightly affects accuracy of a flow rate measurement.
  • each installing position of each of the downstream-side pressure detection points 30 and 34 of the burner shown in FIG. 1 is set in the range of 0.5L 10 ⁇ PL ⁇ L 10 on the downstream side from a center point of the length L of the throat 6.
  • FIG. 15 shows a view for explaining solid fuel measuring means, and the solid fuel is pulverized by a solid fuel pulverization device 70 (e.g., a vertical mill) until a predetermined particle diameter is obtained, and the fuel is carried to each burner 44 by a carrier gas through the solid fuel carrying tube 10.
  • the solid fuel carrying tube 10 comprises solid fuel measuring means 71 (for example, there is a measuring instrument which is of a static charge type or a micro wave type and so forth).
  • flow rates of the solid fuel that flows into the plurality of solid fuel burners 44 in the combustion device are individually adjusted and measured by the solid fuel flow rate measuring means 71, the control device 37 adjusts an opening degree of the flow rate adjusting means 1 for the combustion gas and individually controls the flow rates of the combustion gas based on the combustion gas flow rates detected by the differential pressure detection devices 32 and 35 of the respective solid fuel burners 44 in accordance with a change in measured solid fuel flow rates, and hence it is possible to rapidly cope with a change in solid fuel flow rate of each burner 44.
  • adjusting the combustion gas alone can suffice, and the adjusting means and others can have simpler configurations than those in case of using the solid fuel that is carried by the carrier gas.
  • flames can be changed to the upward direction or the downward direction, and NOx concentration of a nitrogen oxide in the combustion exhaust gas can be reduced, or an amount of heat transfer to the heat transfer tube (not shown) installed in the boiler furnace 40 can be effectively controlled.
  • combustion air outlet opening 7 is divided into the two parts in the up-and-down direction by the center partition 4, the combustion air amount is deviated depending on each of the upper and lower sides of the combustion air outlet opening 7, and the flames are changed to the upward direction or the downward direction in the boiler furnace 40, thereby effectively enabling a reduction in NOx concentration of a nitrogen oxide in the combustion exhaust gas or control over an amount of heat transfer to the heat transfer tube (not shown) installed in the boiler furnace 40.
  • the burner configuration has been explained with use of the fuel nozzle 10 having a flat transverse cross section.
  • the above-described measuring technique can be used with respect to the fuel nozzle 10 having a circular transverse cross section without being restricted to the flat shape.
  • the combustion air outlet opening 7 has a concentric cross-sectional shape formed of the fuel nozzle 10 and the combustion air throat 6, the drift is hardly produced as compared with the example adopting the flat shape.
  • the combustion air that has flowed in from the combustion air inlet opening 8 is not necessarily uniformly discharged from the combustion air throat 6 having the concentric shape in the combustion air duct 2.
  • An example where the fuel nozzle 10 is the fuel nozzle 10 having the circular transverse cross-sectional shape will be assumed and described with reference to FIG. 8 .
  • a flow of the air that has flowed in from the combustion air inlet opening 8 is disturbed by the adjustment damper 1.
  • the angle ⁇ formed between the perpendicular 52 in FIG. 6 and the extended line 53 of the blade of the damper 1 is 30°, an air current flows downward along the vertical direction, and hence an air flow rate from the combustion air outlet opening 7 close to the downstream of the adjustment damper 1 increases.
  • the air flow rate at the combustion air outlet opening 7 is deviated when the transverse cross-sectional shape of the fuel nozzle 10 is either the flat shape or the circular shape.
  • downstream-side pressure detection points (which correspond to the downstream-side pressure detection points 30 and 34 installed on the flat fuel nozzle 10 shown in FIG. 10 , and hence a description will be given with reference to FIG. 1 ) are arranged on the top portion wall surface and the bottom portion wall surface of the combustion gas throat 6.
  • the top portion of the combustion gas throat 6 that is a position where the downstream-side pressure detection point is arranged is determined as a reference, and the detection points are present in the range of ⁇ 2° in the circumferential direction (see FIG. 12 ) on the downstream side that is 1/2 of the throat length of the combustion gas throat 6 along the central axis direction (see FIG. 11 ).
  • downstream-side pressure detection points are arranged on the top portion wall surface and the bottom portion wall surface of the combustion gas throat 6, the combustion gas flow rate can be measured without being affected by the drift of the combustion gas, and the flow rate of the fuel gas can be highly accurately measured.
  • differential pressure detection devices corresponding to the differential pressure detection devices 32 and 35 shown in FIG. 1 are provided, and a control device that converts values of pressure differences between the upstream-side pressure detection points and the downstream-side pressure detection points into the flow rates of the combustion gas and adjusts an amount of combustion air flowing into the combustion air duct based on a damper operation is also provided.
  • the combustion air duct 2 is completely divided into two parts in the up-and-down direction, and the combustion air measurement points must be installed at the two positions on the combustion air duct 2 divided into the upper and lower sides.
  • measuring points corresponding to the pressure detection points 30, 31, 33, and 34 in FIG. 1 are narrowed down to one position.
  • the installing position for the pressure detection point should be set to a position that is not affected by the drift of the damper 1.
  • the air flow rate differs depending on an opening degree of the damper 1 due to an influence of a flow rate deviation in the region (B) or (C).
  • the upper and lower sides are less unbalanced, and hence the flow rate deviation is small irrespective of the opening degree of the damper 1.
  • downstream-side pressure detection point (not shown) on the top portion or the bottom portion of the combustion air throat 6 can suffice. Considering the maintenance or ease of installation, it is good to install this detection point on the top portion.
  • the stagnation space 90 (see FIG. 2 ) in the combustion air duct 2 is installed on the downmost-stream portion on each of the upper and lower sides. Even if there is no center partition 4, a large part of the combustion air flows out to the throat 6 before reaching the downmost-stream portion of the combustion air duct 2, and hence the stagnation region where there is almost no flow of the combustion air is produced. In the stagnation region, a static pressure is stable irrespective of an opening degree of the damper 1. Therefore, one downstream-side pressure detection point is installed in a region where each of the pressure detection points 30 and 34 is disposed on the downmost-stream portion of the combustion air duct 2 in FIG. 1 .
  • a duct center portion (a top part of a semicircular portion of the combustion air duct 2) at which the center partition 4 and the combustion air duct 2 cross each other is provided at the farthest position from the combustion air inlet opening 8, and a static pressure is in the most stable state in the stagnation region. Therefore, it is desirable to provide the upstream-side detection point on the top part (a position corresponding to each of the upstream-side pressure detection points 31 and 33 in FIG. 1 ) of the semicircular portion of the combustion air duct 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Regulation And Control Of Combustion (AREA)
EP12736749.8A 2011-01-21 2012-01-16 Festbrennstoffbrenner und verbrennungsvorrichtung damit Withdrawn EP2667094A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2011010544 2011-01-21
PCT/JP2012/000203 WO2012098848A1 (ja) 2011-01-21 2012-01-16 固体燃料バーナおよび前記バーナを用いる燃焼装置

Publications (1)

Publication Number Publication Date
EP2667094A1 true EP2667094A1 (de) 2013-11-27

Family

ID=46515484

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12736749.8A Withdrawn EP2667094A1 (de) 2011-01-21 2012-01-16 Festbrennstoffbrenner und verbrennungsvorrichtung damit

Country Status (5)

Country Link
US (1) US20130291770A1 (de)
EP (1) EP2667094A1 (de)
JP (1) JP5490924B2 (de)
KR (1) KR20140003558A (de)
WO (1) WO2012098848A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2679899A4 (de) * 2011-02-22 2018-01-24 Mitsubishi Hitachi Power Systems, Ltd. Verbrennungsvorrichtung

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8672670B2 (en) * 2009-11-11 2014-03-18 Trane International Inc. System and method for controlling a furnace
WO2014027611A1 (ja) * 2012-08-14 2014-02-20 バブコック日立株式会社 固体燃料バーナと該固体燃料バーナを備えた燃焼装置の運転方法
JP5867742B2 (ja) * 2012-08-14 2016-02-24 三菱日立パワーシステムズ株式会社 固体燃料バーナを備えた燃焼装置
EP3279562B1 (de) 2015-03-31 2020-08-19 Mitsubishi Hitachi Power Systems, Ltd. Brenner und kessel
RU2661993C1 (ru) 2015-03-31 2018-07-23 Мицубиси Хитачи Пауэр Системз, Лтд. Горелка для сжигания и котел, оснащенный такой горелкой для сжигания
JP6632226B2 (ja) * 2015-06-12 2020-01-22 三菱日立パワーシステムズ株式会社 バーナ、燃焼装置、ボイラ及びバーナの制御方法
JP6642912B2 (ja) 2015-09-11 2020-02-12 三菱日立パワーシステムズ株式会社 燃焼バーナ及びこれを備えたボイラ
US11428407B2 (en) 2018-09-26 2022-08-30 Cowles Operating Company Combustion air proving apparatus with burner cut-off capability and method of performing the same
CN115087834A (zh) * 2020-02-10 2022-09-20 杰富意钢铁株式会社 辐射管燃烧器、辐射管及辐射管燃烧器的设计方法
CN116624871B (zh) * 2023-07-18 2023-10-24 广东金美达实业有限公司 一种一体式燃气气路组件

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5560109A (en) * 1978-10-28 1980-05-07 Babcock Hitachi Kk Burner device
JPS5835325A (ja) * 1981-08-26 1983-03-02 Ebara Corp バ−ナの空気比測定装置
JPS60181557U (ja) * 1984-05-14 1985-12-02 バブコツク日立株式会社 バ−ナ燃焼装置
US4645450A (en) * 1984-08-29 1987-02-24 Control Techtronics, Inc. System and process for controlling the flow of air and fuel to a burner
US5048761A (en) * 1990-03-14 1991-09-17 The Babcock & Wilcox Company Pulverized coal flow monitor and control system and method
JPH0921507A (ja) * 1995-07-05 1997-01-21 Hitachi Ltd 微粉炭燃焼方法および微粉炭燃焼装置ならびに空気旋回器
US5576495A (en) * 1995-10-23 1996-11-19 The Babcock & Wilcox Company Two phase flow meter
JP2000257811A (ja) * 1999-03-03 2000-09-22 Hitachi Ltd 微粉炭燃焼方法及び微粉炭燃焼装置並びに微粉炭燃焼バーナ
DE10037234A1 (de) * 2000-07-31 2002-02-21 Rational Ag Verbrennungssystem für ein Gargerät sowie Gargerät mit solch einem Verbrennungssystem
JP4301422B2 (ja) 2000-11-07 2009-07-22 バブコック日立株式会社 燃焼用バーナ、該バーナを備えた燃焼装置及び前記バーナを用いる燃焼方法
WO2006007111A2 (en) * 2004-07-01 2006-01-19 Nikon Corporation A dynamic fluid control system for immersion lithography
CA2664769C (en) 2006-09-27 2013-03-19 Babcock-Hitachi Kabushiki Kaisha Burner, and combustion equipment and boiler comprising burner
FR2908882B1 (fr) * 2006-11-17 2008-12-26 Thales Sa Dispositif de mesure de la pression totale d'un ecoulement et procede mettant en oeuvre le dispositif
US20110197831A1 (en) * 2007-04-13 2011-08-18 Babcock-Hitachi Kabushiki Kaisha Pulverized Coal Burning Boiler
US7810400B2 (en) * 2007-07-24 2010-10-12 Cidra Corporate Services Inc. Velocity based method for determining air-fuel ratio of a fluid flow
JP2009079794A (ja) * 2007-09-25 2009-04-16 Babcock Hitachi Kk 固体燃料バーナ、固体燃料バーナを用いた燃焼装置とその運転方法
JP5190509B2 (ja) * 2008-04-10 2013-04-24 バブコック日立株式会社 固体燃料バーナ、固体燃料バーナを用いた燃焼装置とその運転方法
DE102008030650B4 (de) * 2008-06-27 2011-06-16 PROMECON Prozeß- und Meßtechnik Conrads GmbH Einrichtung und Verfahren zur Steuerung des Brennstoff-Luft-Verhältnisses bei der Verbrennung gemahlener Kohle in einer Kohlekraftwerksfeuerungsanlage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012098848A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2679899A4 (de) * 2011-02-22 2018-01-24 Mitsubishi Hitachi Power Systems, Ltd. Verbrennungsvorrichtung

Also Published As

Publication number Publication date
US20130291770A1 (en) 2013-11-07
JPWO2012098848A1 (ja) 2014-06-09
KR20140003558A (ko) 2014-01-09
WO2012098848A1 (ja) 2012-07-26
JP5490924B2 (ja) 2014-05-14

Similar Documents

Publication Publication Date Title
EP2667094A1 (de) Festbrennstoffbrenner und verbrennungsvorrichtung damit
US10712009B2 (en) Burner head of a burner and gas turbine having a burner of this type
US5299930A (en) Low nox burner
CA3081520C (en) Methods and systems for minimizing nox and co emissions in natural draft heaters
US5145359A (en) Burner for thermic generators
US20140202443A1 (en) Fuel/Air Furnace Mixer
US6702571B2 (en) Flex-flame burner and self-optimizing combustion system
US20150113998A1 (en) Gas Turbine Combustor and Gas Turbine Combustor Control Method
US20160334134A1 (en) Burner With Flow Distribution Member
JP6577717B2 (ja) 流体バッファ容積装置を備えるシステム及び対応する方法
KR101582729B1 (ko) 연소 장치
US10088157B2 (en) Multi-sensor probe for monitoring combustion in a conduit
CN114930082A (zh) 用于固体燃料燃烧器的喷嘴组件和操作用于固体燃料燃烧器的喷嘴组件的方法
US11415317B2 (en) Combustion head with low emission of NOx for burners and burner comprising such a head
EP2831506A1 (de) Verbesserte lochanordnung von auskleidungen einer brennkammer eines gasturbinenmotors mit niedriger verbrennungsdynamik und niedrigen emissionen
KR20200065049A (ko) 발전소 노 시스템 내 연소 과정 제어 장치
CN108204603A (zh) 燃烧器组件、包括其的燃气涡轮设备和操作此设备的方法
CN210662857U (zh) 一种用于工业窑炉的燃烧结构
BG63410B1 (bg) Горивна уредба
JP5392319B2 (ja) コークス炉の燃料ガス用混合装置
US20160161117A1 (en) Method for operating a multi-burner system by means of combustion air pressure measurement and regulation
JP2011202841A (ja) バーナ及び該バーナを備えたボイラ
CN114870662B (zh) 烟气混合器
RU2746144C1 (ru) Скоростная горелка
JP3137711B2 (ja) 燃焼用空気供給装置

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20130729

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MITSUBISHI HITACHI POWER SYSTEMS, LTD.

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: MITSUBISHI HITACHI POWER SYSTEMS, LTD.

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Effective date: 20170214