EP0690263B1 - Procédé pour le fonctionnement d'une installation de combustion - Google Patents

Procédé pour le fonctionnement d'une installation de combustion Download PDF

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Publication number
EP0690263B1
EP0690263B1 EP95810376A EP95810376A EP0690263B1 EP 0690263 B1 EP0690263 B1 EP 0690263B1 EP 95810376 A EP95810376 A EP 95810376A EP 95810376 A EP95810376 A EP 95810376A EP 0690263 B1 EP0690263 B1 EP 0690263B1
Authority
EP
European Patent Office
Prior art keywords
combustion
combustion stage
stage
fuel
air
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.)
Expired - Lifetime
Application number
EP95810376A
Other languages
German (de)
English (en)
Other versions
EP0690263A2 (fr
EP0690263A3 (fr
Inventor
Peter Dr. Jansohn
Tino-Martin Marling
Thomas Dr. Sattelmayer
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.)
General Electric Switzerland GmbH
Original Assignee
ABB Research Ltd Switzerland
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 ABB Research Ltd Switzerland filed Critical ABB Research Ltd Switzerland
Publication of EP0690263A2 publication Critical patent/EP0690263A2/fr
Publication of EP0690263A3 publication Critical patent/EP0690263A3/fr
Application granted granted Critical
Publication of EP0690263B1 publication Critical patent/EP0690263B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 
    • 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
    • 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
    • F23D—BURNERS
    • F23D17/00—Burners for combustion simultaneously or alternately of gaseous or liquid or pulverulent fuel
    • F23D17/002—Burners for combustion simultaneously or alternately of gaseous or liquid or pulverulent fuel gaseous or liquid fuel
    • 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
    • F23C2201/102—Furnace staging in horizontal direction
    • 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
    • F23C2201/30—Staged fuel supply
    • 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
    • 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
    • F23C2900/07002—Premix burners with air inlet slots obtained between offset curved wall surfaces, e.g. double cone 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 
    • F23C2900/00—Special features of, or arrangements for combustion apparatus using fluid fuels or solid fuels suspended in air; Combustion processes therefor
    • F23C2900/09002—Specific devices inducing or forcing flue gas recirculation

Definitions

  • the present invention relates to a method according to the preamble of claim 1. It also concerns a furnace to carry out the procedure.
  • the fuel is used in conventional combustion plants injected into a combustion chamber via a nozzle and under there Supply of combustion air burned. Basically is the operation of such combustion plants with a gaseous one and / or liquid fuel possible.
  • UHC unsaturated coal-water substances
  • the invention seeks to remedy this.
  • the invention how it is characterized in the claims, the task lies on the basis of a process and a firing system of type mentioned the pollutant emissions, in particular to minimize this as far as NOx emissions are concerned both when using a liquid fuel, a gaseous Fuel, as well as with a mixed operation named fuels.
  • the underlying idea of the invention differs from the classic principles in that the grading is exclusive in the excess air area by adding twice the fuel and is carried out with recirculated flue gas.
  • the first stage is the combustion air via a heat exchanger an aerodynamically stabilized premix burner fed.
  • the combustion air can be preheated to approx. 400 ° C, which at the combustion of oil to a very good pre-evaporation leads.
  • the combustion air ratio in this so-called Lean level is about 2.1, corresponding to about 11% residual oxygen, whereby at flame temperatures of approx. 1300 ° C the NOx emissions, in the atmospheric case, are below 1 vppm.
  • the main advantage of the invention is that that the arrangement of the injection openings of the fuel / flue gas mixture a timing offset of the ignition control in the combustion chamber and thus the oxygen content influence during the burnout, in such a way that with optimal Trim the system the expected NOx emissions, with complete burnout, lie between 5-8 vppm. To Today's knowledge marks this value theoretically lower limit for near stoichiometric combustion fossil fuels.
  • Another advantage of the invention is that the combustion air of the first stage calorically conditioned Flue gas can be supplied to the preheating temperature to influence and on the other hand the residual oxygen content If necessary, continue to lower after the second stage to be able to.
  • Fig. 1 shows a boiler system, which in a lean stage 1 and a near-stoichiometric level 2 is divided.
  • the lean stage 1 essentially consists of a premix burner 100 with a downstream combustion chamber 122, in which one Flame temperature of approx. 1300 ° C prevails.
  • the premix burner 100 comes with a liquid 112 and / or gaseous Fuel 113 operated.
  • the combustion air 115 for the Premix burner 100 is a mixture 6 that consists of Fresh air 3 and from recirculated, calorically conditioned Flue gas 4 is composed.
  • the degree of mixing is on the air side maintained by a controllable throttle valve 7, this air 3 unconditioned, that is at ambient temperature arises.
  • the flue gas 4 comes from a flue gas distributor 8, of the flue gases 9 from the near stoichiometric Level 2 comes. These smoke gases 9 fall with one Temperature of about 300 ° C and they are mentioned in the Flue gas distributor 8 through a heat exchange system 10 to approx. Cooled down to 260 ° C. This cooled smoke 4 and the Fresh air 3 is mixed upstream of the premix burner 100 and compressed in a compressor 11 acting there, the temperature of this compressed air / flue gas mixture is approx. 260 ° C. This mixture is then 6 by another induced by the wall of the combustion chamber 122 Heat exchange symbolized by arrow 16 is further processed, calorically, in such a way that the combustion air 115 for the premix burner 100 at approx.
  • annular chamber 12 Located on the outflow side of the combustion chamber 122 there is an annular chamber 12, which is already close to stoichiometric Level 2 is heard. In this annular chamber 12 flow slightly cooled hot gases from lean stage 1, which with Combustion air 115 is operated at approximately 11% 02, whereby NOx emissions at a flame temperature of approx. 1300 ° C in the atmospheric case are below 1 vppm. Furthermore is this annular chamber 12 with a number of injection holes 13 perforated through which a fuel / flue gas mixture 14 flows in. This mixture 14 consists of a portion Flue gas 4 from the flue gas distributor 8 and from another Share of fuel 15, which is preferably a gaseous fuel is.
  • the flue gases 9 After leaving of the boiler furnace 17, the flue gases 9 still have one Temperature of about 300 ° C, part of which, as already explained above, introduced into the flue gas distributor 8 become.
  • the non-branched flue gases 18 are via a Blow off chimney 19 at the lowest temperature.
  • the expected NOx emissions are between 5-8 vppm, which according to the current state of knowledge is a lower one Limit for near-stoichiometric combustion of fossil fuels Represents fuels.
  • FIG. 2 The following is the description of FIG. 2 as needed referred to the remaining figures 3-5.
  • the premix burner 100 consists of two hollow ones conical partial bodies 101, 102 which are offset from one another are nested.
  • the transfer of the respective Center axis or longitudinal axis of symmetry 201b, 202b of the conical Partial body 101, 102 creates each other on both sides, in mirror image arrangement, each with a tangential air inlet slot 119, 120 free (Fig. 3-5), through which the Combustion air 115 in the interior of the premix burner 100, i.e. flows into the cone cavity 114.
  • the cone shape of the one shown Partial body 101, 102 has a flow direction certain fixed angle.
  • the partial body 101, 102 in the direction of flow have an increasing or decreasing taper similar to a trumpet or Tulip.
  • the latter two Shapes are not included in the drawing as they are for the expert can be easily understood.
  • the two tapered partial bodies 101, 102 each have a cylindrical Initial part 101a, 102a, which also, analogous to the tapered Partial bodies 101, 102, offset from one another, so that the tangential air inlet slots 119, 120 via the entire length of the premix burner 100 are present.
  • a nozzle 103 is accommodated in the cylindrical starting part, the injection 104 of approximately the narrowest cross section that formed by the tapered body 101, 102 Cone cavity 114 coincides.
  • this nozzle 103 depends on the given Parameters of the respective premix burner 100.
  • the premix burner can be purely conical, i.e. without cylindrical starting parts 101a, 102a.
  • the conical partial bodies 101, 102 each have one Fuel line 108, 109 on which along the tangential Entry slots 119, 120 arranged and with injection openings 117 are provided, by which preferably a gaseous fuel 113 into the one flowing through there Combustion air 115 is injected, as shown by arrows 116 want to symbolize.
  • These fuel lines 108, 109 are preferably at the latest at the end of the tangential inflow, before entering the cone cavity 114, placed, this to get an optimal air / fuel mixture.
  • the outlet opening of the premix burner is on the combustion chamber side 122 100 into a front wall 110, in which a number Bores 110a are present.
  • the latter occur in function when needed, and ensure that dilution air or cooling air 110b the front part of the combustion chamber 122 is fed.
  • this air supply ensures flame stabilization at the outlet of the premix burner 100. This flame stabilization becomes important when it is is about the compactness of the flame due to a radial To support flattening.
  • Fuel is a liquid fuel 112, which is enriched at most with a recirculated exhaust gas can be. This fuel 112 is under one acute angle injected into the cone cavity 114.
  • the Nozzle 103 From the Nozzle 103 thus forms a conical fuel profile 105, the rotating combustion air flowing in tangentially 115 is enclosed. In the axial direction the concentration of fuel 112 continuously through the incoming combustion air 115 for optimal mixing reduced. If the premix burner 100 has a gaseous one Operated fuel 113, this is preferably done via opening nozzles 117, the formation of this Fuel / air mixture directly at the end of the air inlet slots 119, 120 comes about. When injecting the Fuel 112 through the nozzle 103 is in the area of the vortex burst, thus in the area of the backflow zone 106 at the end of the premix burner 100, the optimal, homogeneous fuel concentration reached across the cross section. The ignition takes place at the top of the backflow zone 106.
  • the tapered Partial body 101, 102 with respect to the cone angle and width of the Tangential air inlet slots 119, 120 are narrow limits to adhere to the desired flow field of the combustion air 115 with the flow zone 106 at the exit of the Premix burner 100 can adjust.
  • a reduction in the cross-section of the tangential Air inlet slots 119, 120 continue the backflow zone 106 upstream, which then causes the mixture comes to ignition earlier.
  • the backflow zone 106 once fixed is positionally stable is because the swirl number increases in the direction of flow in the area the conical shape of the premix burner 100.
  • the axial speed can pass through within the premix burner 100 a corresponding supply, not shown, of an axial Change the combustion air flow.
  • the construction of the premix burner 100 is also an excellent choice Size of the tangential air inlet slots 119, 120 to change, without changing the length of the premix burner 100 recorded a relatively large operational range can be.
  • the Baffles 121a, 121b have a flow initiation function these, according to their length, the respective End of the tapered partial body 101, 102 in the direction of flow extend towards the combustion air 115.
  • the Channeling the combustion air 115 into the cone cavity 114 can by opening or closing the guide plates 121a, 121b by one in the area of the entry of this channel into the Cone cavity 114 placed pivot point 123 can be optimized, this is particularly necessary if the original gap size the tangential air inlet slots 119, 120 changed becomes.
  • these can be dynamic arrangements can also be provided statically, as required Baffles are an integral part with the tapered partial bodies 101, 102 form.
  • the premix burner can also be used 100 can also be operated without baffles, or others can Aids for this are provided.

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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)

Claims (9)

  1. Procédé pour le fonctionnement d'une installation de combustion, laquelle se compose essentiellement d'un premier étage de combustion pouvant fonctionner avec un brûleur et d'un deuxième étage de combustion branché en aval de celui-ci, l'air de combustion (115) destiné au premier étage de combustion (1) étant un mélange (6) d'air (3) et de gaz de combustion recirculés (4) qui se diffuse dans le brûleur (100), caractérisé par le fait que les gaz chauds de ce premier étage de combustion (1) sont refroidis par échange thermique avant de pénétrer dans le deuxième étage de combustion (2), qu'un mélange (14) de combustible (15) et de gaz de combustion recirculés (4) est injecté dans les gaz chauds du côté de l'entrée du deuxième étage de combustion (2), et que la combustion dans ce deuxième étage de combustion (2) est déclenchée par auto-allumage.
  2. Procédé selon la revendication 1, caractérisé par le fait que les gaz chauds recirculés (4) à destination du premier et du deuxième étage de combustion (1, 2) subissent une réduction calorifique avant d'être mélangés avec d'autres fluides (3, 15).
  3. Procédé selon la revendication 1, caractérisé par le fait que le premier étage de combustion (1) fonctionne comme un étage pauvre avec une teneur en oxygène de 9 à 13 % et que le deuxième étage de combustion (2) fonctionne comme un étage presque stoechiométrique avec une teneur en oxygène de 2 à 4 %.
  4. Installation de combustion destinée à mettre en oeuvre le procédé selon la revendication 1, l'installation de combustion se composant essentiellement d'un premier étage de combustion pouvant fonctionner avec un brûleur et d'un deuxième étage de combustion branché en aval de celui-ci et ladite installation de combustion étant munie de moyens pour faire recirculer une certaine quantité de gaz de combustion (9) issus du deuxième étage de combustion (2) dans un air de combustion (3), caractérisée par le fait qu'une paroi du premier étage de combustion est configurée comme échangeur thermique entre les gaz chauds du premier étage de combustion et l'air de combustion (6), qu'en aval du premier étage de combustion (1) se trouve une chambre annulaire (12) du côté de l'entrée du deuxième étage de combustion (2), que la paroi de la chambre annulaire (12) présente des orifices (13) pour l'injection d'un mélange (14) composé de gaz de combustion recirculés (4) et de combustible (15), et que le brûleur (100) fonctionne avec un air de combustion (115) comprimé.
  5. Installation de combustion selon la revendication 4, caractérisée par le fait que le brûleur (100) se compose d'au moins deux corps partiels (101, 102) creux, coniques, emboítés l'un dans l'autre dans le sens de l'écoulement, et dont les axes de symétrie longitudinale respectifs (lOlb, 102b) sont décalés l'un par rapport à l'autre, que les parois voisines des corps partiels (101, 102) forment des canaux tangentiels (119, 120) pour un courant d'air de combustion (115) dans leur extension longitudinale, qu'au moins une buse à combustible (103) soit présente dans l'espace creux conique (114) formé par les corps partiels (101, 102).
  6. Dispositif selon la revendication 5, caractérisé par le fait que des buses à combustible supplémentaires (117) sont disposées dans la zone des canaux tangentiels (119, 120) dans leur extension longitudinale.
  7. Dispositif selon la revendication 5, caractérisé par le fait que les corps partiels (101, 102) s'étendent en forme de cône dans le sens de l'écoulement sous un angle fixe.
  8. Dispositif selon la revendication 5, caractérisé par le fait que les corps partiels (101, 102) présentent une inclinaison croissante du cône dans le sens de l'écoulement.
  9. Dispositif selon la revendication 5, caractérisé par le fait que les corps partiels (101, 102) présentent une inclinaison décroissante du cône dans le sens de l'écoulement.
EP95810376A 1994-06-28 1995-06-08 Procédé pour le fonctionnement d'une installation de combustion Expired - Lifetime EP0690263B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4422535A DE4422535A1 (de) 1994-06-28 1994-06-28 Verfahren zum Betrieb einer Feuerungsanlage
DE4422535 1994-06-28

Publications (3)

Publication Number Publication Date
EP0690263A2 EP0690263A2 (fr) 1996-01-03
EP0690263A3 EP0690263A3 (fr) 1996-07-17
EP0690263B1 true EP0690263B1 (fr) 2000-03-01

Family

ID=6521662

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95810376A Expired - Lifetime EP0690263B1 (fr) 1994-06-28 1995-06-08 Procédé pour le fonctionnement d'une installation de combustion

Country Status (4)

Country Link
US (1) US5545032A (fr)
EP (1) EP0690263B1 (fr)
JP (1) JPH08166108A (fr)
DE (2) DE4422535A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109595548A (zh) * 2018-12-04 2019-04-09 清华大学 浓淡返混式旋流煤粉燃烧器

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB9425691D0 (en) * 1994-12-20 1995-02-22 Boc Group Plc A combustion apparatus
DE19542644B4 (de) * 1995-11-17 2008-12-11 Alstom Vormischverbrennung
DE59702928D1 (de) * 1997-03-18 2001-02-22 Alstom Power Schweiz Ag Baden Verfahren zum Betrieb eines drallstabilisierten Brenners sowie Brenner zur Durchführung des Verfahrens
EP1262714A1 (fr) 2001-06-01 2002-12-04 ALSTOM (Switzerland) Ltd Brûleur avec recirculation des gaz de combustion
US7074033B2 (en) * 2003-03-22 2006-07-11 David Lloyd Neary Partially-open fired heater cycle providing high thermal efficiencies and ultra-low emissions
DE102006000174B9 (de) * 2006-04-13 2009-04-16 Honeywell Technologies Sarl Öl-Vormischbrenner und Betriebsverfahren dafür
US20170114717A1 (en) * 2014-06-26 2017-04-27 Siemens Energy, Inc. Axial stage combustion system with exhaust gas recirculation
EP3650753B1 (fr) * 2018-11-12 2022-11-09 WS Wärmeprozesstechnik GmbH Procédé et dispositif de combustion étagée sans inflammation

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US4395223A (en) * 1978-06-09 1983-07-26 Hitachi Shipbuilding & Engineering Co., Ltd. Multi-stage combustion method for inhibiting formation of nitrogen oxides
GB2116308B (en) * 1982-03-08 1985-11-13 Westinghouse Electric Corp Improved low-nox, rich-lean combustor
DE3545524C2 (de) * 1985-12-20 1996-02-29 Siemens Ag Mehrstufenbrennkammer für die Verbrennung von stickstoffhaltigem Gas mit verringerter NO¶x¶-Emission und Verfahren zu ihrem Betrieb
DE3707773C2 (de) * 1987-03-11 1996-09-05 Bbc Brown Boveri & Cie Einrichtung zur Prozesswärmeerzeugung
AT391185B (de) * 1988-02-08 1990-08-27 Vaillant Gmbh Einrichtung zur stufenweisen verbrennung eines brennstoff-luftgemisches
CH678568A5 (fr) * 1989-03-15 1991-09-30 Asea Brown Boveri
CH679692A5 (fr) * 1989-04-24 1992-03-31 Asea Brown Boveri
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US5201650A (en) * 1992-04-09 1993-04-13 Shell Oil Company Premixed/high-velocity fuel jet low no burner
DE4242003A1 (de) * 1992-12-12 1994-06-16 Abb Research Ltd Prozesswärmeerzeuger
DE4320212A1 (de) * 1993-06-18 1994-12-22 Abb Research Ltd Feuerungsanlage

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109595548A (zh) * 2018-12-04 2019-04-09 清华大学 浓淡返混式旋流煤粉燃烧器

Also Published As

Publication number Publication date
EP0690263A2 (fr) 1996-01-03
JPH08166108A (ja) 1996-06-25
US5545032A (en) 1996-08-13
DE4422535A1 (de) 1996-01-04
EP0690263A3 (fr) 1996-07-17
DE59507869D1 (de) 2000-04-06

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