EP0690263A2 - 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
EP0690263A2
EP0690263A2 EP95810376A EP95810376A EP0690263A2 EP 0690263 A2 EP0690263 A2 EP 0690263A2 EP 95810376 A EP95810376 A EP 95810376A EP 95810376 A EP95810376 A EP 95810376A EP 0690263 A2 EP0690263 A2 EP 0690263A2
Authority
EP
European Patent Office
Prior art keywords
combustion
combustion stage
stage
fuel
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.)
Granted
Application number
EP95810376A
Other languages
German (de)
English (en)
Other versions
EP0690263A3 (fr
EP0690263B1 (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 relates to a furnace for carrying out the method.
  • the invention seeks to remedy this.
  • the invention is based on the object of minimizing the pollutant emissions, in particular as far as the NOx emissions are concerned, in a method and a furnace of the type mentioned both when using a liquid fuel, a gaseous fuel, and in a mixed operation with the fuels mentioned.
  • the underlying idea of the invention differs from the classic principles in that the grading is carried out exclusively in the excess air area by double addition of fuel and with recirculated flue gas.
  • the combustion air is fed to an aerodynamically stabilized premix burner via a heat exchanger.
  • the combustion air can be preheated to approx. 400 ° C, which leads to very good pre-evaporation when burning oil.
  • the combustion air ratio in this so-called lean stage is approx. 2.1, corresponding to approx. 11% residual oxygen, which means that at flame temperatures of approx. 1300 ° C the NOx emissions, in the atmospheric case, are below 1 vppm.
  • a further fuel / flue gas mixture is preferably injected axially offset there via an annular chamber until a residual oxygen content of approximately 3% is reached in the exhaust gas.
  • the injected mixture is ignited by the hot flue gases from the first stage.
  • the complete burnout then takes place in the combustion chamber at a temperature of approx. 1400 ° C.
  • the main advantage of the invention can be seen in the fact that the arrangement of the injection openings of the fuel / flue gas mixture control a time offset of the ignition in the combustion chamber and thus influence the oxygen content during the burnout, in such a way that, with optimal trimming of the system, the expected NOx -Emissions, when burned out completely, are between 5-8 vppm. According to current knowledge, this value marks the theoretical one lower limit for the near-stoichiometric combustion of fossil fuels.
  • combustion air of the first stage can be supplied with calorically conditioned flue gas, on the one hand to influence the preheating temperature and on the other hand to be able to further reduce the residual oxygen content after the second stage if necessary.
  • Fig. 1 shows a boiler system, which is divided into a lean stage 1 and a near-stoichiometric stage 2.
  • the lean stage 1 essentially consists of a premix burner 100 with a downstream combustion chamber 122, in which a flame temperature of approximately 1300 ° C. prevails.
  • the premix burner 100 is operated with a liquid 112 and / or gaseous fuel 113.
  • the combustion air 115 for the premix burner 100 is a mixture 6 which is composed of fresh air 3 and of recirculated, calorically conditioned flue gas 4.
  • the degree of mixing is maintained on the air side by a controllable throttle valve 7, this air 3 being unconditioned, that is to say at ambient temperature.
  • the flue gas 4 comes from a flue gas distributor 8, which comes from the flue gases 9 from the near-stoichiometric stage 2. These flue gases 9 occur at a temperature of approximately 300 ° C. and are cooled to approximately 260 ° C. in the flue gas distributor 8 mentioned by a heat exchange system 10. These cooled flue gases 4 and the fresh air 3 are mixed upstream of the premix burner 100 and compressed in a compressor 11 acting there, the temperature of this compressed air / flue gas mixture being approximately 260 ° C.
  • This mixture 6 is then further calorically processed by a further heat exchange induced by the wall of the combustion chamber 122, which is symbolized by the arrow 16, in such a way that the combustion air 115 for the premix burner 100 flows in there at approximately 400 ° C.
  • the slightly cooled hot gases from the lean stage 1, which is operated with combustion air 115 at approx. 11% O2 flow into this annular chamber 12, so that at a flame temperature of approx. 1300 ° C. the NOx emissions in the atmospheric case are below 1 vppm.
  • This annular chamber 12 Furthermore is perforated this annular chamber 12 with a number of injection holes 13 through which a fuel / flue gas mixture 14 flows.
  • This mixture 14 is composed of a portion of flue gas 4 from the flue gas distributor 8 and a further portion of fuel 15, which is preferably a gaseous fuel.
  • fuel 15 which is preferably a gaseous fuel.
  • heat is extracted from the hot gases provided in the lean stage 1 by the already mentioned heat exchange 16, so that a temperature of approximately 1000 ° C. still prevails when entering the annular chamber 12.
  • the fuel / flue gas mixture 14 injected into the annular chamber 12 by axial displacement reduces the residual oxygen content of the conditioned hot gases from the lean stage 1 to approximately 3%.
  • the mixture 14 injected into the annular chamber 12 experiences self-ignition due to the hot gases of approximately 1000 ° C., the complete burnout then taking place in the boiler furnace 17 at a temperature of approximately 1400 ° C.
  • the flue gases 9 still have a temperature of approximately 300 ° C., a part of which, as already explained above, is introduced into the flue gas distributor 8.
  • the non-branched flue gases 18 are blown into the open at a low temperature via a chimney 19.
  • the expected NOx emissions are between 5-8 vppm, which, according to current knowledge, represents a lower limit for the near-stoichiometric combustion of fossil fuels.
  • FIG. 2 In the description of FIG. 2, reference is made below to the remaining FIGS. 3-5 as required.
  • the premix burner 100 consists of two hollow, conical partial bodies 101, 102 which are nested in one another in a staggered manner.
  • the offset of the respective central axis or longitudinal axis of symmetry 201b, 202b of the conical partial bodies 101, 102 to one another creates a tangential air inlet slot 119, 120 on both sides, in a mirror-image arrangement (FIGS. 3-5), through which the combustion air 115 enters the interior of the Premix burner 100, ie flows into the cone cavity 114.
  • the conical shape of the partial bodies 101, 102 shown in the flow direction has a specific fixed angle.
  • the partial bodies 101, 102 can have an increasing or decreasing cone inclination in the direction of flow, similar to a trumpet or. Tulip.
  • the last two forms are not included in the drawing, since they can be easily understood by a person skilled in the art.
  • the two tapered partial bodies 101, 102 each have a cylindrical starting part 101a, 102a, which, similarly to the tapered partial bodies 101, 102, also run offset from one another, so that the tangential air inlet slots 119, 120 are present over the entire length of the premix burner 100.
  • a nozzle 103 is accommodated, the injection 104 of which coincides approximately with the narrowest cross section of the conical cavity 114 formed by the conical partial bodies 101, 102.
  • the injection capacity and the type of this nozzle 103 depend on the specified parameters of the respective premix burner 100.
  • the premix burner can be of a purely conical design, that is to say without cylindrical starting parts 101a, 102a.
  • the tapered partial bodies 101, 102 further each have a fuel line 108, 109, which are arranged along the tangential inlet slots 119, 120 and are provided with injection openings 117, through which preferably a gaseous fuel 113 is injected into the combustion air 115 flowing through there, as is shown by the arrows 116.
  • These fuel lines 108, 109 are preferably placed at the latest at the end of the tangential inflow, before entering the cone cavity 114, in order to obtain an optimal air / fuel mixture.
  • the outlet opening of the premix burner 100 merges into a front wall 110, in which a number of bores 110a are provided.
  • the latter come into operation when necessary and ensure that dilution air or cooling air 110b is supplied to the front part of the combustion chamber 122.
  • this air supply ensures flame stabilization at the outlet of the premix burner 100. This flame stabilization becomes important when it comes to supporting the compactness of the flame due to a radial flattening.
  • the fuel brought in through the nozzle 103 is a liquid fuel 112, which can be enriched with a recirculated exhaust gas at most. This fuel 112 is injected into the cone cavity 114 at an acute angle.
  • a conical fuel profile 105 is thus formed from the nozzle 103 and is enclosed by the rotating combustion air 115 flowing in tangentially.
  • the concentration of the fuel 112 is continuously reduced to an optimal mixing by the incoming combustion air 115.
  • the premix burner 100 is operated with a gaseous fuel 113, this is preferably done via opening nozzles 117, the formation of this fuel / air mixture taking place directly at the end of the air inlet slots 119, 120.
  • the optimal, homogeneous fuel concentration over the cross section is achieved in the region of the vortex run, that is to say in the region of the backflow zone 106 at the end of the premix burner 100.
  • the ignition takes place at the tip of the backflow zone 106. Only at this point can a stable flame front 107 arise.
  • the combustion air 115 is additionally preheated or enriched with a recirculated exhaust gas, this supports the evaporation of the liquid fuel 112 before the combustion zone is reached.
  • liquid fuels are supplied via the lines 108, 109.
  • the backflow zone 106 shifts the backflow zone 106 further upstream, which, however, then causes the mixture to ignite earlier. At least it must be determined that the backflow zone 106, once fixed, is positionally stable, because the swirl number increases in the direction of flow in the region of the cone shape of the premix burner 100.
  • the axial speed within the premix burner 100 can be changed by a corresponding supply, not shown, of an axial combustion air flow.
  • the design of the premix burner 100 is furthermore excellently suitable for changing the size of the tangential air inlet slots 119, 120, with which a relatively large operating range can be recorded without changing the overall length of the premix burner 100.
  • the guide plates 121a, 121b have a flow introduction function, which, depending on their length, extend the respective end of the tapered partial bodies 101, 102 in the direction of flow relative to the combustion air 115.
  • the Channeling the combustion air 115 into the cone cavity 114 can be optimized by opening or closing the guide plates 121a, 121b about a pivot point 123 located in the region of the entry of this channel into the cone cavity 114, in particular this is necessary if the original gap size of the tangential air inlet slots 119 , 120 is changed.
  • these dynamic arrangements can also be provided statically, in that guide baffles as required form a fixed component with the tapered partial bodies 101, 102.
  • the premix burner 100 can also be operated without baffles, or other aids can be provided for this.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Of Fluid Fuel (AREA)
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
DE4422535 1994-06-28
DE4422535A DE4422535A1 (de) 1994-06-28 1994-06-28 Verfahren zum Betrieb einer Feuerungsanlage

Publications (3)

Publication Number Publication Date
EP0690263A2 true EP0690263A2 (fr) 1996-01-03
EP0690263A3 EP0690263A3 (fr) 1996-07-17
EP0690263B1 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 (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6672863B2 (en) 2001-06-01 2004-01-06 Alstom Technology Ltd Burner with exhaust gas recirculation
EP1845307A1 (fr) * 2006-04-13 2007-10-17 Honeywell Technologies Sarl Brûleur à prémélange d'huile et son procédé de fonctionnement

Families Citing this family (7)

* 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
US7074033B2 (en) * 2003-03-22 2006-07-11 David Lloyd Neary Partially-open fired heater cycle providing high thermal efficiencies and ultra-low emissions
JP6437018B2 (ja) * 2014-06-26 2018-12-12 シーメンス エナジー インコーポレイテッド 排気再循環を伴う軸方向段構造燃焼システム
EP3650753B1 (fr) * 2018-11-12 2022-11-09 WS Wärmeprozesstechnik GmbH Procédé et dispositif de combustion étagée sans inflammation
CN109595548B (zh) * 2018-12-04 2020-05-01 清华大学 浓淡返混式旋流煤粉燃烧器

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Publication number Priority date Publication date Assignee Title
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
CH680816A5 (fr) * 1989-04-27 1992-11-13 Asea Brown Boveri
DE4034008A1 (de) * 1989-11-07 1991-05-08 Siemens Ag Zwei- oder mehrstufige kesselfeuerung mit geringer, no(pfeil abwaerts)x(pfeil abwaerts)-emission und entsprechende verfahren
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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6672863B2 (en) 2001-06-01 2004-01-06 Alstom Technology Ltd Burner with exhaust gas recirculation
EP1845307A1 (fr) * 2006-04-13 2007-10-17 Honeywell Technologies Sarl Brûleur à prémélange d'huile et son procédé de fonctionnement

Also Published As

Publication number Publication date
JPH08166108A (ja) 1996-06-25
US5545032A (en) 1996-08-13
DE59507869D1 (de) 2000-04-06
EP0690263A3 (fr) 1996-07-17
DE4422535A1 (de) 1996-01-04
EP0690263B1 (fr) 2000-03-01

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