EP2314921A2 - Verfahren zum Betrieb eines Heizkessels - Google Patents

Verfahren zum Betrieb eines Heizkessels Download PDF

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Publication number
EP2314921A2
EP2314921A2 EP10188335A EP10188335A EP2314921A2 EP 2314921 A2 EP2314921 A2 EP 2314921A2 EP 10188335 A EP10188335 A EP 10188335A EP 10188335 A EP10188335 A EP 10188335A EP 2314921 A2 EP2314921 A2 EP 2314921A2
Authority
EP
European Patent Office
Prior art keywords
air
nozzles
burners
nozzle
burner
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Withdrawn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
EP10188335A
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English (en)
French (fr)
Other versions
EP2314921A3 (de
Inventor
Jean-Claude Pillard
Patrick Muscat
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.)
Fives Pillard SA
Original Assignee
Fives Pillard SA
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 Fives Pillard SA filed Critical Fives Pillard SA
Publication of EP2314921A2 publication Critical patent/EP2314921A2/de
Publication of EP2314921A3 publication Critical patent/EP2314921A3/de
Withdrawn legal-status Critical Current

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Classifications

    • 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 
    • 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
    • F23C5/32—Disposition of burners to obtain rotating flames, i.e. flames moving helically or spirally
    • 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 
    • F23C6/00—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion
    • F23C6/04—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion in series connection
    • F23C6/045—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion in series connection with staged combustion in a single enclosure
    • 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 
    • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
    • 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
    • F23L7/00—Supplying non-combustible liquids or gases, other than air, to the fire, e.g. oxygen, steam
    • F23L7/002—Supplying water
    • F23L7/005—Evaporated water; Steam
    • 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
    • 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 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/06041—Staged supply of oxidant

Definitions

  • the present invention relates to a method of operating a boiler and a boiler shaped to operate, particularly in rated speed, according to this method.
  • An industrial boiler of the type which comprises at least one liquid and / or gaseous fuel burner disposed in the lower part of the furnace and an additional air injection system with several injection nozzles arranged downstream of the burner.
  • JP 57,207,703 disclose that.
  • the burners 30 operate there stoichiometrically or in the absence of air.
  • the nominal operation of such boilers is typically as follows.
  • the burner operates in lack of air (typically a lack of air of 10 to 35%, which corresponds to a ratio air to stoichiometric air (flow rates) between about 0.9 and 0.65) and the additional air is injected through the nozzles of the additional air injection system (called "OFA” for "Over Firing Air”).
  • OFA Over Firing Air
  • the quantity of air introduced into this post-combustion zone corresponds to an excess of air of 25% to 35% (percentage of excess air in the boiler compared to an air ratio (from the burner and the additional system) on fuel equal to 1).
  • the CO rate is greatly reduced by the additional air injection because of its high reactivity, that of unburnt is only weakly, which ultimately leads to a large production of carbonaceous dust ( in general between 150 and 500 mg / Nm 3 to 3% 0 2 ), well above the European regulation (50 mg / Nm 3 to 3% O 2 ).
  • the need to use a dust collector which is necessarily expensive.
  • the quantity of oxygen released is very important (3 to 5% - relative to the stoichiometry) and the efficiency of the boiler is decreased.
  • the present invention aims to optimize, or even reduce, the rate of nitrogen oxides emitted, while reducing the CO and unburned carbon emissions, and to increase the efficiency of the boiler, that is to say to decrease the "carbon footprint" (the release of CO 2 ).
  • the sum of the values of the axial amount of movement of the air injected by the injection nozzles is greater than or equal to the value of the amount of movement of the ascending fumes produced by the burners.
  • the set of burners will operate globally close to stoichiometry, from a stoichiometric air to air ratio greater than or equal to 0.85 (between 0.85 and 1.05, with uncertainties of measurements, so the set of burners could operate as soon as a substoichiometry, or air defect, of at most 15%), or even in excess of air of at most 5%.
  • the air introduced by the burner and the injection system will represent an excess of air of at most 15%.
  • the boiler 1 may comprise several stages of burners 4, each stage may comprise several burners 4.
  • the burners 4 use liquid and / or gaseous fuels.
  • Each burner 4 can be supplied with air independently of one another or with a common air box for the burners 4.
  • the burners 4 used are burners with a low nitrogen oxide emission, such as, for example, those described in the European patents EP 774 620 , EP 893 651 and EP 1 058 052 .
  • these burners 4 to liquid and / or gaseous fuels comprise a central primary air supply pipe 8, fuel injection means 9, 9a disposed in the central pipe 8, a flame stabilizer 10 disposed at the downstream end of the central air supply pipe 8, and a plurality of secondary air supply pipes 11.
  • the primary air circuit represents at most 60% of the air introduced by the burner (correlatively, the secondary air circuit therefore represents at least 40%).
  • the central air supply duct 8 forms the primary air circuit.
  • the central pipe 8 has a circular cross section. Also preferably it has a conical profile converging in the direction of the air flow (half-angle at the summit less than 5 °). This slight taper improves the quality of the air jet 8a to facilitate the change of direction of the fumes 12.
  • this central pipe 8 projects into the hearth a distance of at least 5 cm from the wall 3 of the boiler 1 carrying the burner 4. The fact of introducing the primary air into the fireplace away from the wall makes it easier to change the direction of the fumes 12 located against this wall 3, thus reducing the swirl at the of the latter and to increase the rate of flue gas recirculated into the flame.
  • the seam is at most 50 cm. Combined with taper, this projection reduces the oxygen content of flue gas recirculation.
  • the secondary air circuit is formed by the different secondary air supply lines 11 which are arranged at the periphery of the central air supply pipe 8 and which are distributed so as to have a homogeneous angular distribution.
  • the secondary air supply lines 11 are grouped in pairs (non-contiguous). This pairing makes it possible, on the one hand, to significantly improve the contact surface between the secondary air and the fumes 12 and, on the other hand, to have recirculation of the fumes in the flame by the two jets d air 13 from the two secondary air supply lines from the same pair. As a result, the flue gas recirculation 12 is improved, the oxygen content in the flame is reduced as is the emission of nitrogen oxides.
  • a burner 4 comprises between four and twelve pairs of secondary pipes 11. In the present example, as illustrated in FIG. figure 2 the burner 4 comprises six pairs.
  • each secondary air supply line 11 has a circular cross section.
  • each of these pipes 11 has a conical profile converging in the direction of air flow (half-angle at the summit less than 5 °). This slight taper improves the quality of the air jet 13.
  • each secondary air supply pipe 11 projects into the hearth of a distance at least 5 cm from the wall 3 of the boiler 1 carrying the burner 2. The introduction of secondary air into the firebox 2 away from the wall 3 facilitates the change of direction of the fumes 12 located against this wall 3, so reduce the swirl at the latter and to increase the rate of flue gas recirculated into the flame.
  • the mesh is not more than 50 cm. Combined with the conicity, this projection reduces the oxygen content of the fumes in recirculation.
  • the air supply of a burner 4, as illustrated in FIG. figure 3 reduces the internal pressure losses of the burner 4.
  • the burner 4 is connected to the box 14 (or the individual supply sheath) by an air inlet 15 to which is associated a main ring 16 movable sliding between a closing position and an open position. In the open position, the air inlet 15 is disengaged and the primary and secondary air circuits are powered. In the closed position, the air inlet 15 is obstructed but allows the passage of the voluntary air leak used for cooling the two circuits.
  • the burner 4 also comprises a separation ferrule 17 which is associated with an orifice 18 made in the primary central air supply pipe 8. This separation ferrule 17 is slidably mounted and allows the ratio of the airfoil to be separated and adjusted.
  • the primary circuit is fed by the portion of the air having passed through the orifice 18, and the secondary circuit by the complementary part.
  • This complementary portion of air is then guided by an annular pipe 19 and then by several boxes 20 (possibly removable) feeding each pair of secondary air ducts 11 (or each pipe 11 if the secondary air ducts 11 are not matched). ).
  • the different boxes 20 could be replaced by a single box forming a conical annular space over the entire periphery and supplying all the secondary air supply lines 11.
  • the low nitrogen oxide emission burner 4 operates in stoichiometry or, preferably, in excess of air of at most 5%.
  • the unburned and CO levels are particularly low and do not come from an excess of fuel.
  • the burners operating in stoichiometry or in excess of air of at most 5%, it is preferable to have an offset of fuel flow between the stages of burners, the fuel flow being all the more important that the burner 4 is at a lower floor.
  • This arrangement makes it possible to obtain optimum reburning of the unburnt products produced in the lowest stage because, on the one hand, the residence time of unburnt products produced in the high temperature zone is the highest, and, on the other hand, On the other hand, the highest stage works in a fairly high excess of air, which encourages the re-burning of these unburnt products produced below.
  • the additional air injection system 5 (usually called “OFA” for "Over Firing Air”) is disposed above all the burners 4, at a distance such that the air does not cause a flame.
  • the air introduced into the boiler 1 by the burners 4 and the additional air injection system 5 represents an excess of air of at most 15% relative to the stoichiometry for the combustion of the fuel introduced by the burners 4.
  • the air introduced by this system 5 represents between 10 and 15% of the air relative to the stoichiometry, depending on the excess air value introduced by the burners 4.
  • the additional air injection system 5 is configured so that the amount of axial movement of the air exiting this system (i.e. the component taken along the exit axis of the air) is greater than or equal to the value of the amount of movement of the rising fumes 22 produced by all the burners 4.
  • the additional air injection system 5 comprises a plurality of injection nozzles 6 which are all supplied with air by the same air supply box.
  • the injection nozzles 6 are arranged, oriented and configured so as to have a homogeneous distribution of the additional air in the sheath 23 in which the fumes produced by the burners 4 flow.
  • the injection nozzles 6 are all arranged at the same level, a level consisting of a horizontal slice of thickness of 1 to 2 meters, so that the air is injected into the same level.
  • the nozzles 6 may be oriented along an axis perpendicular to the walls 3 of the boiler 1 or located through the four corners of the hearth and directed towards the vertical axis of the hearth. This is particularly the case when the boiler 1 is of the tangential heating type with the burners located near the corners of the furnace and oriented so as to generate a rotary flow.
  • the nozzles 6 are carried by the walls, near the corners of the hearth, and oriented towards the vertical axis of the hearth while being offset, so as to promote the rotation of the flames generated by the burners 4.
  • the injection nozzles 6 are arranged on two walls 3 facing each other, these walls being either those carrying the burners 4 or perpendicular to the latter.
  • the air injection system 5 comprises at least two types of nozzle 6, each type of nozzle being characterized by the exit section of the nozzles 6 of this type.
  • the sum of the amounts of axial movement of the air injected by two nozzles carried by two walls 3 facing each other is substantially constant along these walls 3 (the nozzles facing each other may be coaxial or slightly offset).
  • a nozzle 6a of a type faces a nozzle 6b of a second type.
  • the amount of axial movement of the air injected by a nozzle 6a of a first type allows this air to reach the median plane 24 separating the two opposite walls 3 carrying nozzles 6.
  • the amount of axial movement of the air injected by a nozzle 6a of this type is between 500 and 1000 kg.m / s 2 ).
  • the amount of axial movement of the air injected by a nozzle 6b of the second type limits the penetration of this air into the space defined by the wall carrying the nozzle and a plane situated substantially at mid-air. path of this wall 3 and the median plane 24.
  • This type of nozzle 6b allows to introduce air near the walls 3.
  • the injection of air is such that, on the same wall 3, there is an alternation of the nozzles 6a, 6b according to their type.
  • This alternation can be a nozzle of a type then a nozzle of another type, two nozzles of one type then two nozzles of another type, or a nozzle of one type then two nozzles of another type .
  • alternation is 1 to 1.
  • the amount of movement of the nozzles 6 located on one side of the median plane 24, differs slightly from that of the nozzles 6 located on the other side, this to improve the distribution of the air injected into the outlet section 40.
  • This amount of movement is slightly greater for those on the side where the outlet section is closest to the fireplace wall.
  • the design of the system 5 thus complies with the requirement of a total amount of axial axial movement of additional air equal to or greater than the amount of movement of the ascending fumes 22, the requirement of presence of at least two types of nozzle with a amount of axial movement specific to each type of nozzle allowing a clean air penetration for each type to reach a specific plane (the opposite wall if a single wall carries nozzles, the median plane if the two opposite walls carry nozzles , a plane offset from the median plane if the outlet of the furnace of the boiler is off-center with respect to the median plane 24 of the hearth at the burners 4).
  • the ratio of the axial air movement quantities of each nozzle type, the number of nozzles specific to each type, the inter-nozzle distance and the distance separating the two extreme nozzles of the walls perpendicular to that carrying the nozzles are determined in order to have the most homogeneous air distribution downstream of the injection level.
  • the air introduced by the additional injection system 5 makes it possible to very significantly reduce the level of CO emitted by the boiler 1, and to a lesser extent the rate of unburnt carbonaceous.
  • the nozzles 6 are shaped so as to introduce saturated or superheated steam.
  • this steam is introduced by the nozzles of the additional air injection system 5.
  • the steam has the same pressure as that of atomization of the burners (typically between 6 and 14 bars, and between 150 to 300 ° C). Steam promotes the mixing of additional air with fumes by its velocity and expansion, greatly increasing turbulence, and reacts with unburnt carbon by producing carbon monoxide and dihydrogen.
  • the steam injected corresponds to approximately between 3 and 8% of the fuel introduced by the burners.
  • an additional additional air injection system 7 forms a second level of nozzles 6.
  • This additional system 7 comprises a reduced number of nozzles 6c with respect to the main system 5 (Preferably, at most equal to the number of high momentum nozzles 6 of the main system 5).
  • the additional system 7 can be operated without affecting the operating conditions of the first nozzle stage 6 (preferably, each of the nozzles 6c of this system can be sectioned or opened independently of each other).
  • the air injected by the additional injection system 7 is injected at the same level or downstream at a slightly higher level (less than 2.5 m in the middle plane of the main level).
  • the additional system 7 may comprise only one type of nozzle 6c, the arrangement of which preferably follows the rules for disposing the nozzles 6a, 6b of the main system 5.
  • the nozzle axis 6c of the second stage is in a median plane defined by two axes of contiguous nozzles 6a, 6b, as illustrated by the Figures 4 and 5 arranged one below the other.
  • the figure 6 represents a nozzle 6a of the main additional air introduction system 5 of the present embodiment.
  • a nozzle 6 comprises an additional air duct 25 opening to the wall 3 of the boiler 1 (here, flush).
  • the air has an axial flow at the outlet of the nozzle 6, it comprises rectifying members 26 (more precisely, longitudinal flat plates).
  • the pipe 25 comprises a conical convergent zone 27 which is extended downstream by a pipe cylindrical ejection 28 which opens into the furnace 2 and, upstream by a cylindrical air intake pipe 29 in which are arranged the rectifying members 26.
  • the diameter ratio between the intake pipe 29 and the pipe d ejection 28 is 2 or more.
  • the intake pipe 29 comprises an air inlet 30 associated with a ferrule 31 which is slidably mounted. This shell 31 is movable between a closed position in which the air inlet 30 is closed while allowing to pass a minimum amount of cooling air, and an open position in which the air inlet 30 is cleared.
  • the nozzle 6 comprises a steam introducing rod 32 which is disposed close to the axis of the additional air duct 25.
  • each nozzle 6 could also include a second air circuit for introducing air having a rotational flow at the periphery of the axial flow outlet 28 shown in FIG. figure 6 .
  • the jet of air coming from a nozzle would comprise an axial central air flow (with respect to the axis of the nozzle) coming from the central air duct 25 of the nozzle 6, and a flow of tangential component air (relative to the nozzle axis) from a second annular air duct (forming the second air duct of the nozzle) surrounding the central air duct 25.
  • the nozzles 6 are particularly simple. The only adjustment concerns the air flow and it is related to the degree of opening of the shell 31. Preferably, this degree of opening is adjusted according to the speed of the boiler.
  • the air outlet velocity is determined by the pressure difference between the furnace and the air supply box of the nozzles, minus the internal pressure drops that are minimized.
  • the nozzles 6 being fed by the same air box, the air speed at the outlet of the nozzle is substantially identical for all nozzles 6 (typically more than 70 m / s at rated flow with hot air).
  • the air outlet flow rate is imposed by the passage section of the ejection pipe (depending however on the degree of opening of the ferrule).
  • all the nozzles of the same type generate substantially the same air flow.
  • the balancing of the air flow rates for the nozzles of the same type being done by the degree of opening of the ferrule 31.
  • the injection nozzles will then generate a substantially identical air flow.
  • the nozzles 6a, 6b will therefore have different output sections.
  • the angle of rotation is fixed and is not adjustable.
  • the adjustment of the air flow at the outlet of the nozzles can be easily achieved. by the ferrule 31 of each nozzle 6.
  • the adjustment of the air flow of the nozzles 6 according to the speed of the boiler 1 is made taking into account the air flow through each nozzle 6 (flow measured by a conventional sensor) and by changing the ratio between, on the one hand, the sum of the air flow rates passing by the different nozzles 6 and, on the other hand, the air flow of the burners 4 (equal to the difference between the overall air flow of the box and the sum of the flow rates of air passing through the different nozzles 6). This ratio can easily be adjusted by moving the main shell 16 of the burner 4.
  • each burner 4 of the boiler is equipped with fuel injection means 9, 9a whose maximum flow rate is sufficiently high to allow the boiler 1 to operate at its nominal speed with at least a portion of the burners 4 of the upper stage fed only in air (that is, with the fuel supply turned off).

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Of Fluid Fuel (AREA)
EP10188335A 2009-10-21 2010-10-21 Verfahren zum Betrieb eines Heizkessels Withdrawn EP2314921A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0957392A FR2951525B1 (fr) 2009-10-21 2009-10-21 Procede de fonctionnement d'une chaudiere

Publications (2)

Publication Number Publication Date
EP2314921A2 true EP2314921A2 (de) 2011-04-27
EP2314921A3 EP2314921A3 (de) 2011-09-07

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EP10188335A Withdrawn EP2314921A3 (de) 2009-10-21 2010-10-21 Verfahren zum Betrieb eines Heizkessels

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EP (1) EP2314921A3 (de)
KR (1) KR20110043511A (de)
FR (1) FR2951525B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104713064A (zh) * 2015-03-31 2015-06-17 贵州电力试验研究院 一种掺烧焦炉煤气的超临界锅炉的燃烧调整方法

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57207703A (en) 1981-06-16 1982-12-20 Babcock Hitachi Kk Low nox combustion method with improved boiler efficiency
EP0774620A1 (de) 1995-11-14 1997-05-21 ENTREPRISE GENERALE DE CHAUFFAGE INDUSTRIEL PILLARD. Société anonyme dite: Brenner für flüssigen oder gasförmigen Brennstoff mit sehr niedriger Stickoxidemission
EP0893651A1 (de) 1997-07-22 1999-01-27 Entreprise Generale De Chauffage Industriel Pillard Brenner für flüssigen und gasförmigen Brennstoff mit niedriger Stickoxidemission
EP1058052A1 (de) 1999-05-31 2000-12-06 Entreprise Generale De Chauffage Industriel Pillard Brenner für flüssige Brennstoffe mit niedriger NOx- und Staubemission und Düse dafür
EP1797963A1 (de) 2005-12-15 2007-06-20 EGCI Pillard Mischkammer und Sprühvorrichtung mit einer ähnlichen Mischkammer
FR2902350A1 (fr) 2006-06-15 2007-12-21 Egci Pillard Sa Systeme d'injection de liquide reactif atomise pour la reduction d'oxydes d'azote de gaz de combustion

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AU2005229668B2 (en) * 2004-11-04 2008-03-06 Babcock-Hitachi K.K. Overfiring air port, method for manufacturing air port, boiler, boiler facility, method for operating boiler facility and method for improving boiler facility
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Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57207703A (en) 1981-06-16 1982-12-20 Babcock Hitachi Kk Low nox combustion method with improved boiler efficiency
EP0774620A1 (de) 1995-11-14 1997-05-21 ENTREPRISE GENERALE DE CHAUFFAGE INDUSTRIEL PILLARD. Société anonyme dite: Brenner für flüssigen oder gasförmigen Brennstoff mit sehr niedriger Stickoxidemission
EP0893651A1 (de) 1997-07-22 1999-01-27 Entreprise Generale De Chauffage Industriel Pillard Brenner für flüssigen und gasförmigen Brennstoff mit niedriger Stickoxidemission
EP1058052A1 (de) 1999-05-31 2000-12-06 Entreprise Generale De Chauffage Industriel Pillard Brenner für flüssige Brennstoffe mit niedriger NOx- und Staubemission und Düse dafür
EP1797963A1 (de) 2005-12-15 2007-06-20 EGCI Pillard Mischkammer und Sprühvorrichtung mit einer ähnlichen Mischkammer
FR2894854A1 (fr) 2005-12-15 2007-06-22 Egci Pillard Sa Chambre de melange et dispositif de pulverisation comportant une telle chambre
FR2902350A1 (fr) 2006-06-15 2007-12-21 Egci Pillard Sa Systeme d'injection de liquide reactif atomise pour la reduction d'oxydes d'azote de gaz de combustion

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104713064A (zh) * 2015-03-31 2015-06-17 贵州电力试验研究院 一种掺烧焦炉煤气的超临界锅炉的燃烧调整方法

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KR20110043511A (ko) 2011-04-27
FR2951525B1 (fr) 2012-10-26
EP2314921A3 (de) 2011-09-07
FR2951525A1 (fr) 2011-04-22

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