EP0777082A2 - Brûleur à prémélange - Google Patents

Brûleur à prémélange Download PDF

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Publication number
EP0777082A2
EP0777082A2 EP96810739A EP96810739A EP0777082A2 EP 0777082 A2 EP0777082 A2 EP 0777082A2 EP 96810739 A EP96810739 A EP 96810739A EP 96810739 A EP96810739 A EP 96810739A EP 0777082 A2 EP0777082 A2 EP 0777082A2
Authority
EP
European Patent Office
Prior art keywords
premix burner
fuel
flow
inflow
air inlet
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.)
Ceased
Application number
EP96810739A
Other languages
German (de)
English (en)
Other versions
EP0777082A3 (fr
Inventor
Hans Peter Knöpfel
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.)
ABB Research Ltd Switzerland
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 EP0777082A2 publication Critical patent/EP0777082A2/fr
Publication of EP0777082A3 publication Critical patent/EP0777082A3/fr
Ceased 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 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/002—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion
    • 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
    • F23C9/006—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber the recirculation taking place in the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details
    • F23D11/40—Mixing tubes; Burner heads
    • F23D11/402—Mixing chambers downstream of the nozzle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details
    • F23D14/62—Mixing devices; Mixing tubes
    • 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 
    • F23C2202/00—Fluegas recirculation
    • F23C2202/30—Premixing fluegas with combustion air
    • 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 premix burner according to the preamble of claim 1.
  • the invention seeks to remedy this.
  • the invention in a premix burner of the type mentioned at the outset, the invention, as characterized in the claims, is based on the task of optimizing the flow conditions which are decisive for eliminating the imperfections and inadequacies mentioned.
  • the main advantage of the invention is that the main body of the premix burner does not undergo any changes; only the introduction of fresh air into the tangential supply channels, which extend upstream from the tangential air inlet slots, is adapted to the optimal flow field for the burner. This is achieved by maintaining the injector planes parallel to the inflow plane of the feed channels mentioned, regardless of how the respective inflow plane runs, while the axes of the individual injector nozzles are adjusted accordingly along the axial course of the inflow plane in the flow direction of the premix burner.
  • This adjustment can take place continuously, ie from an oblique angle Inflow plane, ie at an acute angle with respect to the burner axis in the flow direction, in the area of the head stage of the premix burner this angle assumes an approximately perpendicular position to the burner axis of the premix burner until the outlet of the premix burner. Achieving an optimal flow field has a direct impact on the quality of the backflow zone that forms at the outlet of the premix burner, in such a way that it is stable in position and is no longer negatively influenced by flow-related interferences.
  • FIG. 1 consists of two hollow, conical partial bodies 1, 2, which are nested inside one another offset.
  • the conical shape of the partial bodies 1, 2 shown has a certain fixed angle in the direction of flow.
  • the partial bodies 1, 2 can have a different opening configuration in the flow direction, for example a regularly or irregularly increasing or decreasing cone inclination, approximately in the form of a diffuser or confuser.
  • the last two forms are not included in the drawing, since they are easy to understand for the person skilled in the art. Which form is ultimately chosen depends on the various parameters of the respective combustion.
  • the transfer of the The respective central axis 1b, 2b of the tapered partial bodies 1, 2 to one another creates a tangential air inlet slot 21, 22 (see FIG. 2) and an axial inflow cross section 18 through which the airflow from a fresh air / flue gas mixture is free
  • Existing combustion air 15, 16 flows into the interior 14 of the premix burner 100.
  • the two conical partial bodies 1, 2 each have a cylindrical starting part 1a, 2a, which likewise run offset from one another analogously to the partial bodies 1, 2, so that the tangential air inlet slots 21, 22 are present over the entire length of the premix burner 100.
  • the premix burner 100 can be designed in a purely conical manner, that is to say without cylindrical starting parts 1a, 2a.
  • At least one fuel nozzle 3 is accommodated in this cylindrical starting part 1a, 2a, which is particularly suitable, for example, as a seat for anchoring the entire premix burner 100.
  • a number of injectors 200 are also accommodated there, which provide the axially introduced combustion air 16, which is also composed of fresh air and flue gas.
  • Both partial bodies 1, 2 each have a fuel line 8, 9, which extends in the axial direction and which are provided with a number of nozzles 17.
  • a gaseous fuel 13 is preferably passed through these lines and is added to the combustion air 15 flowing through the nozzles 17 in the region of the tangential air inlet slots 21, 22 (cf. FIG. 2).
  • the premix burner 100 can be operated solely with the fuel supply via the nozzle 3 or via the nozzles 17. Mixed operation is of course possible via the two fuel nozzles 3, 17, in particular when different fuels are supplied via the individual nozzles.
  • the premix burner 100 On the combustion chamber side 11, the premix burner 100 has a collar-shaped plate or front wall 10 which has a number of bores 10a through which dilution or Cooling air is supplied to the front part of the premix burner 100. If a liquid fuel 12 is supplied via the nozzle 3, it is injected at an acute angle into the interior 14 of the premix burner 100 in such a way that the most conical spray pattern 5 is obtained up to the burner outlet level.
  • the fuel injector 4 can be an air-assisted nozzle or a nozzle that works according to a pressure atomization principle.
  • the conical spray pattern 5 is enclosed by tangentially flowing combustion air streams 15 and by the axially brought in further combustion air 16, corresponding to the number of air inlet slots 21, 22.
  • the concentration of the injected fuel 12 is continuously reduced by the combustion air streams 15, 16 mentioned. If a gaseous fuel 13 is introduced, the mixture formation with the combustion air 15 begins in the area of the air inlet slots 21, 22 at most upstream of the same.
  • the optimal, homogeneous fuel concentration across the cross section is achieved in the area of the vortex run, ie in the area of the backflow zone 6 at the end of the premix burner 100.
  • the ignition of the fuel / combustion air mixture begins at the top of the return flow zone 6. Only at this point can a stable flame front 7 arise.
  • the combustion air 15, 16, that is to say the air / flue gas mixture is still preheated, then an accelerated, holistic evaporation of the liquid fuel 12 occurs before the point at the outlet of the premix burner 100 is reached, at which the ignition of the mixture can take place .
  • the degree of evaporation depends on the size of the premix burner 100, the drop size of the fuel 12 and the temperature and the composition of the combustion air streams 15, 16 depending.
  • the minimization of pollutant emissions depends on the degree of flue gas recirculation, which ensures complete evaporation of the fuel before it enters the combustion zone.
  • narrow limits must be observed so that the desired flow field, i.e. the critical swirl number, of the combustion air with its return flow zone 6 in the area of the mouth of the premix burner 100 for flame stabilization sets.
  • the desired flow field i.e. the critical swirl number
  • the once-fixedly fixed backflow zone 6 is inherently position-stable, because the swirl number increases in the direction of flow in the region of the cone shape of the premix burner 100.
  • the flow cross section of the tangential air inlet slots 21, 22 can be made changeable in the flow direction, for example decreasing in the flow direction, in order to make the backflow zone 6 at the outlet of the premix burner 100 more stable.
  • the axial speed of the mixture can also be influenced by the aforementioned axial supply of combustion air 16.
  • the flow cross section there experiences a cross-sectional jump, not shown in the figure, via the front wall 10, the cross section of which forms the flow cross section of at least a first section of the combustion chamber 11.
  • the backflow zone 6 is also formed in this plane.
  • the construction of the premix burner 100 is, given a given structural length of the same that is not to be exceeded, particularly suitable for changing the gap width of the tangential air inlet slots 21, 22 by closing or dividing the partial cone bodies 1, 2 can be moved apart, as a result of which the distance between the two central axes 1b, 2b is reduced resp. enlarged, as can be derived from Fig. 2 well. It is also easily possible to move the tapered partial bodies 1, 2 into one another by means of a rotating movement. It is thus possible, with appropriate precautions, to vary the shape and size of the tangential air inlet slots 21, 22 during operation, which means that the same premix burner 100 can cover a wide range of functions without changing the overall length.
  • the number of partial bodies 1, 2 is not limited to two. A larger number is also readily possible, and is also desirable for certain types of debt collection. If a spiral flow of the combustion air 15 into the interior 14 is sought, it can be easily achieved via a single tangential air inlet slot.
  • the premix burner to be formed by the partial bodies consists of a single connected pipe, then the tangential injections into the interior can be achieved through channel-like bushings through the wall thickness of the same pipe.
  • FIG. 2 is a section approximately in the middle of the premix burner 100, according to section plane II.-II from FIG. 1.
  • the feed channels 25, 26, which are arranged in mirror image tangentially, fulfill the function of a mixing section in which the final mixture formation between fresh air 19 and recirculated flue gas 20 is perfected.
  • the combustion air 15 is processed in an injector system 200; the axially supplied combustion air 16 is also processed in an injector system (see FIG. 1). Upstream of each feed channel 25, 26, which serves as a tangential inflow into the interior 14 of the premix burner 100, the fresh air 19 is distributed uniformly over the entire length of this premix burner via perforated plates 23, 24.
  • perforated plates 23, 24 are perforated at tangential entry slots 21, 22.
  • the perforations fulfill the function of individual injector nozzles 23a, 24a, which exert a suction effect on the surrounding flue gas 20, in such a way that each of these injector nozzles 23a, 24a only sucks in a certain proportion of flue gas 20, whereupon over the entire axial length of the perforated plates 23, 24, which corresponds to the burner length, a uniform flue gas admixture takes place.
  • This configuration ensures that intimate mixing takes place at the point of contact of the two media, i.e.
  • the local injector configuration 200 is distinguished by the fact that the geometry of the premix burner 100, in particular as regards the shape and size of the tangential air inlet slots 21, 22, remains dimensionally stable, that is to say through the uniformly metered distribution of the hot gases 20 along the There are no heat-related distortions over the entire axial length of the premix burner 100.
  • the same injector configuration as that just described here also applies to the axial formation of fresh air / flue gas mixture (see FIG. 1).
  • the inflow cross section 18 (cf. FIG.
  • FIG. 3 is a schematic illustration of the premix burner 100 in the flow direction, in which, in particular, the course of the perforated plates 23, 24 belonging to the injector system is opposite the inflow planes 30 of the feed channels 25, 26 is expressed. This course is parallel, the inflow planes 30 running parallel to the burner axis of the premix burner 100 over the entire burner length.
  • This figure also shows how the injector nozzles 23a, 24a change their inflow angle with respect to the burner axis of the premix burner 100 in the direction of flow. From an initial acute angle in the area of the head stage of the premix burner 100, they gradually straighten up until they are approximately perpendicular to the focal axis in the area of the exit. This measure increases the quality of the mixture in the combustion air and influences the return flow zone in a stable position.
  • FIGS. 4 and 5 show essentially the same configuration according to FIGS. 2 and 3, the perforated plates 26, 27 with the associated injector nozzles 26a, 27a likewise running parallel over the entire burner length to the inflow planes 40 of the feed channels 25, 26. In the meantime, these inflow planes 40 run conically with respect to the burner axis of the premix burner 100.
  • the variable inflow angle of the injector nozzles 26a, 27a also largely corresponds to the configuration according to FIGS. 2 and 3, the gradual erection of these injector nozzles 26a, 27a becoming one vertical inflow in the area of the outlet of the premix burner 100 is primarily directed against the inflow plane 40 of the respective feed channel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
EP96810739A 1995-12-02 1996-11-06 Brûleur à prémélange Ceased EP0777082A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19545036A DE19545036A1 (de) 1995-12-02 1995-12-02 Vormischbrenner
DE19545036 1995-12-02

Publications (2)

Publication Number Publication Date
EP0777082A2 true EP0777082A2 (fr) 1997-06-04
EP0777082A3 EP0777082A3 (fr) 1997-09-24

Family

ID=7779050

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96810739A Ceased EP0777082A3 (fr) 1995-12-02 1996-11-06 Brûleur à prémélange

Country Status (5)

Country Link
US (1) US5727938A (fr)
EP (1) EP0777082A3 (fr)
JP (1) JPH09178123A (fr)
CA (1) CA2190064A1 (fr)
DE (1) DE19545036A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0851176A3 (fr) * 1996-12-30 1999-01-20 Abb Research Ltd. Chaudière pour un générateur de chaleur
EP0908671A1 (fr) * 1997-10-08 1999-04-14 Abb Research Ltd. Procédé de combustion des combustibles gazeux, liquides et combustibles à moyen et bas pouvoir calorifique dans un brûleur
EP0881431A3 (fr) * 1997-05-26 1999-06-30 Abb Research Ltd. Brûleur pour la mise en oeuvre d'une unité pour la génération d'un gaz chaud
WO2003098110A1 (fr) * 2002-05-16 2003-11-27 Alstom Technology Ltd Bruleur a premelange

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19654116A1 (de) * 1996-12-23 1998-06-25 Abb Research Ltd Brenner zum Betrieb einer Brennkammer mit einem flüssigen und/oder gasförmigen Brennstoff
US6383461B1 (en) 1999-10-26 2002-05-07 John Zink Company, Llc Fuel dilution methods and apparatus for NOx reduction
DE10049203A1 (de) * 2000-10-05 2002-05-23 Alstom Switzerland Ltd Verfahren zur Brennstoffeinleitung in einen Vormischbrenner
DE10050248A1 (de) * 2000-10-11 2002-04-18 Alstom Switzerland Ltd Brenner
DE10051221A1 (de) * 2000-10-16 2002-07-11 Alstom Switzerland Ltd Brenner mit gestufter Brennstoff-Eindüsung
US20150285502A1 (en) * 2014-04-08 2015-10-08 General Electric Company Fuel nozzle shroud and method of manufacturing the shroud
CN114353080B (zh) * 2020-09-30 2025-08-22 芜湖美的厨卫电器制造有限公司 火排片、燃烧器组件和热水装置

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0629817A2 (fr) 1993-06-18 1994-12-21 Abb Research Ltd. Foyer

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH680157A5 (fr) * 1989-12-01 1992-06-30 Asea Brown Boveri
DE4309115A1 (de) * 1993-03-23 1994-09-29 Viessmann Werke Kg Verfahren zum Betrieb eines Ölverdampfungsbrenners

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0629817A2 (fr) 1993-06-18 1994-12-21 Abb Research Ltd. Foyer

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0851176A3 (fr) * 1996-12-30 1999-01-20 Abb Research Ltd. Chaudière pour un générateur de chaleur
EP0881431A3 (fr) * 1997-05-26 1999-06-30 Abb Research Ltd. Brûleur pour la mise en oeuvre d'une unité pour la génération d'un gaz chaud
EP0908671A1 (fr) * 1997-10-08 1999-04-14 Abb Research Ltd. Procédé de combustion des combustibles gazeux, liquides et combustibles à moyen et bas pouvoir calorifique dans un brûleur
WO2003098110A1 (fr) * 2002-05-16 2003-11-27 Alstom Technology Ltd Bruleur a premelange
US7013648B2 (en) 2002-05-16 2006-03-21 Alstom Technology Ltd. Premix burner

Also Published As

Publication number Publication date
CA2190064A1 (fr) 1997-06-03
JPH09178123A (ja) 1997-07-11
EP0777082A3 (fr) 1997-09-24
DE19545036A1 (de) 1997-06-05
US5727938A (en) 1998-03-17

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