EP0740108A2 - Brûleur - Google Patents

Brûleur Download PDF

Info

Publication number
EP0740108A2
EP0740108A2 EP96810227A EP96810227A EP0740108A2 EP 0740108 A2 EP0740108 A2 EP 0740108A2 EP 96810227 A EP96810227 A EP 96810227A EP 96810227 A EP96810227 A EP 96810227A EP 0740108 A2 EP0740108 A2 EP 0740108A2
Authority
EP
European Patent Office
Prior art keywords
swirl generator
fuel
flow
burner according
mixing tube
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Withdrawn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
EP96810227A
Other languages
German (de)
English (en)
Inventor
Klaus Dr. Döbbeling
Hans Peter Knöpfel
Wolfgang Dr. Polifke
Peter Dr. Senior
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
ABB Research Ltd Sweden
Original Assignee
ABB Research Ltd Switzerland
ABB Research Ltd Sweden
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, ABB Research Ltd Sweden filed Critical ABB Research Ltd Switzerland
Publication of EP0740108A2 publication Critical patent/EP0740108A2/fr
Withdrawn legal-status Critical Current

Links

Images

Classifications

    • 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, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • 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
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/70—Baffles or like flow-disturbing devices
    • 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
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/007—Mixing tubes, air supply regulation

Definitions

  • the present invention relates to a burner according to the preamble of claim 1.
  • the last nozzles for this gaseous fuel in the direction of flow are very close to the burner outlet and thus close to the flame. Accordingly, the fuel introduced through these nozzles does not mix optimally with the air and tends to lead to higher NOx emissions. If you want to extend the premixing section in order to keep the NOx emissions to a minimum, this requires a complicated transition piece between the burner body and the following part.
  • the flow field that the premix burner generates downstream causes problems in a subsequent pipe either at the edge or in the center because of the low axial velocity. This then leads to reignition and the premix burner cannot be operated optimally in the transient areas.
  • Liquid fuels are preferably introduced here via a central nozzle on the burner head and then evaporate in the cone cavity.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, is based on the object of proposing measures for a burner of the type mentioned at the outset which are able to overcome the disadvantages mentioned above.
  • the premix burner according to the invention consists of a conical swirl generator which is designed with at least two tangentially arranged slots.
  • the combustion air flows here axially into the swirl generator, and then outwards through the tangential slots or channels mentioned, this conical swirl generator being enclosed by a body which is preferably designed as a tube. Since the shape of this body has a great influence on the flow outside and downstream of the swirl generator, it can be changed after the swirl generator by taking suitable precautions.
  • the cross section of the body enclosing the swirl generator can decrease in the flow direction, for example, through a cone or venturi.
  • the introduction of a gaseous fuel can also be achieved here through nozzles which are located in the area of the slots.
  • the burner is operated with a liquid fuel
  • the fuel in the area of the tip of the conical swirl generator is entered into the cross section of the enclosing body. If an MTBU or LBTU gas is introduced, the relatively large amount of this fuel can be introduced directly from the outside into the cross-section of the enclosing body, which also ensures mixing with the swirl flow prevailing there.
  • the main advantages of the invention are the fact that the flow field can be freely modulated after the swirl generator. It should also be emphasized that the injection of a liquid fuel does not lead to wetting of the flow wall of the enclosing body, because the flow cross section is maximized in this plane. This ensures that, thanks to the large spray angle that is possible, it is optimally mixed with the swirled combustion air. The now possible long pre-mixing section downstream of the swirl generator induces a minimization of the NOx emissions from the subsequent combustion. The good accessibility for MBTU or LBTU gases has already been discussed above. It should also be noted. that the burner front of the burner according to the invention can no longer be cooled. Sealing problems between the premix and head stages no longer occur here.
  • a premix burner 1 which consists of a tubular body 2 and a hollow, conical swirl generator 3 integrated therein.
  • the swirl generator 3 has a conical, decreasing contour in the direction of flow.
  • the air 4 flowing into the swirl generator initially flows axially in order to then continue to flow tangentially or quasi-tangentially, as the arrows 5 want to sense, from the inside to the outside, for which purpose tangential channels 6, 7 are provided here, which pass through Nesting of at least two hollow, conical partial bodies 8, 9 is produced, the central axes of these partial bodies 8, 9 being offset from one another. It is not excluded in certain operating constellations that the swirl generator 3 consists of a single spiral.
  • the offset of the respective central axis or longitudinal axis of symmetry of the tapered partial bodies 8, 9 to one another creates the tangential channels 6, 7 through the adjacent wall, through which the combustion air 5 flows from the interior 16 of the swirl generator 3 into the tube 2.
  • the conical shape of the partial bodies 8, 9 shown in the flow direction has a certain fixed angle.
  • the partial bodies 8, 9 can have an increasing or decreasing cone inclination in the direction of flow, that is, in the sense of a diffuser or. Confusors be formed. 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 conical partial bodies 8, 9 each have a fuel line 10, 11, which are arranged along the tangential channels 6, 7 and are provided with injection openings 12, 13, through which a gaseous fuel 14 is preferably injected into the combustion air 5 flowing through there, as shown by the arrows.
  • These fuel lines 10, 11 are preferably arranged in the region of the tangential outflows from the swirl generator 3 and inflow into the pipe 2, which are predetermined by the channels 6, 7, in order to obtain an optimal air / fuel mixture 15.
  • combustion air 5 is additionally preheated or, for example, enriched with a recirculated flue gas or exhaust gas
  • this generally supports the evaporation of the fuel 14, particularly if it is a liquid fuel, the injection of which is also carried out via the fuel lines 10, 11 mentioned can be.
  • the tapered partial body 8, 9 with respect to the cone angle and the width of the tangential channels 6, 7, strict limits per se must be observed so that the desired flow field of the combustion air 5 and. of the mixture 15 at the output of the swirl generator 3 can adjust.
  • the critical Swirl number can also be influenced by making the width of the tangential channels 6, 7 variable in the flow direction. If the width of the channels 6, 7 decreases in the direction of flow, the location of the formation of the return flow zone shifts downstream. As for the formation of the return flow zone, the following is carried out: The actual combustion chamber, which is not shown in more detail here, is located on the outflow side of the tube 2.
  • the tube 2 fulfills the function of a mixing tube, which provides a defined mixing section downstream of the swirl generator 3, in which a perfect premixing takes place, regardless of the fuel injected.
  • This mixing section also enables loss-free flow guidance, so that even in operative connection with the transition geometry that is present here, no backflow zone can initially form, so that an influence on the quality of the mixture for the respective fuel can be exerted over the length of the mixing tube 2.
  • This mixing tube 2 has a further property, which consists in the fact that in the mixing tube 2 itself the axial speed profile has a pronounced maximum on the axis, so that the flame cannot re-ignite from the combustion chamber. However, it is correct that with such a configuration the axial velocity potentially drops towards the wall.
  • the mixing tube 2 can be provided in the flow and circumferential direction with a number of bores of various cross-sections and directions, not shown, through which an amount of air flows into the interior of the mixing tube 2, and along the wall an increase in Trigger speed.
  • Another possibility of achieving the same effect is that the flow cross-section of the mixing tube 2 on the downstream side of the swirl generator 3 experiences a narrowing, which is also not shown in any more detail, as a result of which the overall speed level within the mixing tube 2 is increased. If the chosen precaution when guiding the flow within the mixing tube 2 is an intolerable Should there be a pressure loss, this can be remedied by providing a diffuser (not shown in the figure) at the end of the mixing tube 2.
  • the combustion chamber adjoins the end of the mixing tube 2, a cross-sectional jump being present between the two flow cross-sections. Only here does the central backflow zone form, which has the properties of a flame holder, which is of course disembodied here.
  • the formation of a stable backflow zone also requires a sufficiently high swirl number in the mixing tube 2. If a flow-like edge zone is formed during operation within the cross-sectional jump mentioned, in which vortex detachments occur due to the prevailing negative pressure, this leads to an increased ring stabilization of the return flow zone itself. If a high swirl number is initially undesirable, stable return flow zones can be smaller by the supply swirled air flows at the end of the mixing tube, for example through tangential openings.
  • the required air volume is approximately 5-20% of the total air volume.
  • the design of the swirl generator 3 is excellently suited to make the width of the tangential channels 6, 7 changeable, so that a relatively large operating bandwidth can be detected without interfering with the overall length of the swirl generator 3.
  • the conical partial bodies 8, 9 can also be moved relative to one another in another plane, as a result of which an overlap of the same is even possible. It is also possible to interleave the conical partial bodies 8, 9 in a spiral manner by counter-rotating movement. It can thus be achieved that the shape, size and configuration of the tangential channels 6, 7 can be varied as desired, whereby the swirl generator 3 has a wide operational availability without changing its overall length.
  • FIG. 2 shows the outflow of the combustion air 5 from the interior 16 of the swirl generator 3 into the mixing tube 2, the fuel 14 being injected into the combustion air flow 5 in the region of the tangential channels 6, 7.
  • a gaseous fuel is preferably injected in the region of the tangential channels 6, 7.
  • FIGS. 3 and 4 differ from FIGS. 1 and 2 in that a fuel lance 17 is drawn through the interior of the swirl generator 3, from which fuel injection 18 into the mixing tube 2 takes place in the region of the tip of the swirl generator 3.
  • This nozzle 19 is preferably operated with a liquid fuel 20, although it is not excluded that a different fuel is used.
  • the free cross section in this plane proves to be an advantage insofar as the oil spray cone 21, as the figure shows, can be designed more generously without running the risk that the walls of the mixing tube 2 are wetted. Otherwise, the design of the premix burner 1 corresponds to that of the preceding figures.
  • FIGS. 1 and 2 adopt the configuration from FIGS. 1 and 2 with the difference that the swirl generator 3 additionally allows an annular axial air flow 22.
  • the final purpose of such an air flow is evident from the description in FIG. 1, where it is stated that the formation of the critical swirl number at the right place can be coordinated by an axial injection of an air flow.
  • FIGS. 3 and 4 are based on FIGS. 3 and 4, with means 23 for injecting an MBTU resp. LBTU gas 24 are provided in the mixing tube 2.
  • This type of injection essentially depends on the fact that the introduction of the required large amount of such a gas 24 is difficult to provide via the injection options on the swirl generator 3.
  • the premix burner according to FIGS. 9 and 10 essentially refer to FIGS. 1 and 2, the axial inlet opening 25 of this swirl generator 3 being maximized, i.e. the inlet cross-section 25 of the swirl generator 3 corresponds to the cross-section of the mixing tube 2.
  • the first possible flow of the air stream 5 through the tangential channels 6, 7 is downstream of the inlet cross-section 25.
  • This embodiment is particularly useful where the flow in the outer area is aligned or leaned purely axially shall be.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
  • Spray-Type Burners (AREA)
EP96810227A 1995-04-25 1996-04-12 Brûleur Withdrawn EP0740108A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19515082A DE19515082B4 (de) 1995-04-25 1995-04-25 Vormischbrenner
DE19515082 1995-04-25

Publications (1)

Publication Number Publication Date
EP0740108A2 true EP0740108A2 (fr) 1996-10-30

Family

ID=7760262

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96810227A Withdrawn EP0740108A2 (fr) 1995-04-25 1996-04-12 Brûleur

Country Status (7)

Country Link
US (1) US5738508A (fr)
EP (1) EP0740108A2 (fr)
JP (1) JP3889079B2 (fr)
KR (1) KR960038235A (fr)
CN (1) CN1160143A (fr)
CA (1) CA2168638A1 (fr)
DE (1) DE19515082B4 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0866269A1 (fr) * 1997-03-18 1998-09-23 Abb Research Ltd. Chaudière pour la génération de chaleur

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19859829A1 (de) * 1998-12-23 2000-06-29 Abb Alstom Power Ch Ag Brenner zum Betrieb eines Wärmeerzeugers
US7097448B2 (en) * 2004-05-07 2006-08-29 Peter Chesney Vortex type gas lamp
US7213348B2 (en) * 2004-11-12 2007-05-08 Bsh Home Appliances Corporation Gas burner and air heater assembly for a gas clothes dryer
CA2786597A1 (fr) 2010-01-06 2011-07-14 The Outdoor Greatroom Company LLLP Ensemble brasero
CN101871648B (zh) * 2010-07-09 2012-05-30 郭雅婷 多元燃料工业锅炉及窑炉燃烧器
EP2685161B1 (fr) * 2012-07-10 2018-01-17 Ansaldo Energia Switzerland AG Agencement de chambre de combustion, en particulier pour turbine à gaz
EP2685160B1 (fr) * 2012-07-10 2018-02-21 Ansaldo Energia Switzerland AG Brûleur de prémélange du type multi-cônes destiné à une turbine à gaz
CN106439820B (zh) * 2016-11-28 2018-08-03 无锡市莱达热工工程有限公司 热工炉烧嘴芯体

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE288610C (fr) *
EP0210462B1 (fr) * 1985-07-30 1989-03-15 BBC Brown Boveri AG Chambre de combustion double
CH674561A5 (fr) * 1987-12-21 1990-06-15 Bbc Brown Boveri & Cie
CH680157A5 (fr) * 1989-12-01 1992-06-30 Asea Brown Boveri
US5307634A (en) * 1992-02-26 1994-05-03 United Technologies Corporation Premix gas nozzle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0866269A1 (fr) * 1997-03-18 1998-09-23 Abb Research Ltd. Chaudière pour la génération de chaleur
US5961315A (en) * 1997-03-18 1999-10-05 Abb Research Ltd. Boiler plant for heat generation

Also Published As

Publication number Publication date
CN1160143A (zh) 1997-09-24
CA2168638A1 (fr) 1996-10-26
JP3889079B2 (ja) 2007-03-07
JPH08296820A (ja) 1996-11-12
DE19515082A1 (de) 1996-10-31
DE19515082B4 (de) 2005-02-03
US5738508A (en) 1998-04-14
KR960038235A (ko) 1996-11-21

Similar Documents

Publication Publication Date Title
EP0704657B1 (fr) Brûleur
EP0321809B1 (fr) Procédé pour la combustion de combustible liquide dans un brûleur
EP0387532B1 (fr) Chambre de combustion d'une turbine à gaz
EP0918191B1 (fr) Brûleur pour la mise en oeuvre d'un générateur de chaleur
EP0777081B1 (fr) Brûleur à prémélange
EP0401529B1 (fr) Chambre de combustion d'une turbine à gaz
DE19640198A1 (de) Vormischbrenner
WO2006069861A1 (fr) Bruleur de premelange dote d'un parcours de melange
DE19547913A1 (de) Brenner für einen Wärmeerzeuger
EP0718561B1 (fr) Brûleur
DE19757189B4 (de) Verfahren zum Betrieb eines Brenners eines Wärmeerzeugers
DE19654009B4 (de) Vormischbrenner zum Betrieb einer Brennkammer mit einem flüssigen und/oder gasförmigen Brennstoff
DE19610930A1 (de) Brenner für einen Wärmeerzeuger
EP0394800B1 (fr) Brûleur à mélange préalable pour la génération de gaz chaud
EP0851172B1 (fr) Brûleur et méthode pour la mise en oeuvre d'une chambre de combustion avec un combustible liquide et/ou gazeux
EP0994300B1 (fr) Brûleur pour la conduite d'un générateur de chaleur
EP0742411B1 (fr) Alimentation en air pour une chambre de combustion à prémélange
DE19515082B4 (de) Vormischbrenner
DE19548853A1 (de) Kegelbrenner
EP0903540A1 (fr) Brûleur pour la mise en oeuvre d'un générateur de chaleur
DE19545036A1 (de) Vormischbrenner
EP0730121A2 (fr) Brûleur à prémélange
EP0866268B1 (fr) Procédé de fonctionnement d'un brûleur stabilisé par vortex et brûleur mettant en oeuvre le procédé
EP0786626A1 (fr) Brûleur à prémélange
EP0780628A2 (fr) Brûleur à prémélange pour un générateur de chaleur

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE FR GB IT NL

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

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Withdrawal date: 19980220