EP0809070B1 - Brûleur avec recirculation des gaz d'échappement - Google Patents

Brûleur avec recirculation des gaz d'échappement Download PDF

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Publication number
EP0809070B1
EP0809070B1 EP96107956A EP96107956A EP0809070B1 EP 0809070 B1 EP0809070 B1 EP 0809070B1 EP 96107956 A EP96107956 A EP 96107956A EP 96107956 A EP96107956 A EP 96107956A EP 0809070 B1 EP0809070 B1 EP 0809070B1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
gas recirculation
mixing duct
burner
burner according
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
EP96107956A
Other languages
German (de)
English (en)
Other versions
EP0809070A1 (fr
Inventor
Jakob Keller
Bruno Zumstein
Ulrich Leemann
Philipp Hanimann
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.)
Oertli Technique Thermique
Original Assignee
Oertli Technique Thermique
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 Oertli Technique Thermique filed Critical Oertli Technique Thermique
Priority to EP96107956A priority Critical patent/EP0809070B1/fr
Priority to DE59607583T priority patent/DE59607583D1/de
Priority to AT96107956T priority patent/ATE204972T1/de
Publication of EP0809070A1 publication Critical patent/EP0809070A1/fr
Application granted granted Critical
Publication of EP0809070B1 publication Critical patent/EP0809070B1/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 
    • 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, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D17/00—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel
    • F23D17/002—Burners for combustion conjointly or alternatively 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

Definitions

  • the invention relates to a burner with exhaust gas recirculation according to Preamble of claim 1.
  • EP-A-0 430 011 and EP-491 079 are burners known in which exhaust gas into the primary combustion zone by means of air nozzles is returned. In these cases, the mixing of fresh air and Exhaust and primary combustion take place in the same area. It is also over EP-A-0 394 800 a burner is known which consists of partial cone bodies there are tangential combustion air inlet channels, in which air and recirculated exhaust gas mixed before the actual combustion process become. After mixing incoming air with recirculated exhaust gas finds a premix of liquid or in a conical cavity gaseous fuel with the previously generated exhaust gas-air mixture instead. A A sufficiently high temperature of the exhaust gas / air mixture also enables Pre-evaporation of the liquid fuel. The latter property is for the blue color of the flame when the burner is operating with liquid fuel responsible.
  • a furnace is also described also has a device for recycling exhaust gases.
  • nozzles At the Inside the burner tube are nozzles to accelerate the Combustion air or formation of a low pressure behind the said nozzles intended.
  • In the wall of the burner tube there are openings for Injection of combustion products in the low pressure range and one Baffle plate is provided for swirling the primary air.
  • the gas mixture had a swirl around the burner axis To give.
  • the invention is based on the object constructively a burner of the type mentioned at the beginning simplify and expand to pollutant emissions and the need for external energy for each company minimize this both when operating with liquid as well as with gaseous fuels. According to the invention this is due to the features listed in claim 1 reached.
  • Burners are a major advantage of the invention to see that a particularly intimate mixture of exhaust gas and air even before the fuel injection takes place. It will also be an excellent one Pre-evaporation and premixing of the fuel achieved.
  • the construction of the present invention significantly simpler than, for example, that from EP-A-0 394,800 known.
  • Another advantage of the invention lies in the good efficiency of the annular jet pump, which exhaust gases are entrained by the fresh air flow. Man can improve this efficiency even more by using the Fresh air entering the mixing duct in a number of separate Splits inlet openings. Thanks to its high Jet pump efficiency and its low back pressure after the jet pump can the burner proposed here operated with a conventional single-stage blower become. In addition, if necessary, the otherwise at Exhaust gas recirculation burners do not have the usual start-up measures become.
  • Another advantage of the invention lies in the possibility of special flame stabilization. If the outer shell closes after the narrowing a suitably dimensioned diffuser, can the flame front in the one generated by the jet pump Do not migrate the vortex flow back to the fuel injection. This will not only be the desired premix and pre-evaporation achieved, but it also succeeds in that Fuel injection before sooting and overheating protect. This property contributes to the susceptibility to failure to reduce the burner.
  • Possible exemplary embodiments are in the figures 1, 2, 3 and 4 are shown schematically. Like the figures 1, 3 and 4 clarify, there is the burner body from an essentially rotationally symmetrical outer shell 1 and an inner shell arranged concentrically to it 2.
  • the outer shell 1 has a striking narrowing 3 and a diffuser part 4.
  • a mixing channel 5 is of a part 6 of the outer shell 1 and a part 7 of the Inner shell 2 limited, the course of the shell parts 6 and 7 is chosen so that the cross-sectional area the jet pump mixing section 5 via a in the main flow direction (i.e. parallel to the burner axis) Length of at least two times the radial gap width of the Mixing section remains largely constant. It starts the mixing channel 5 immediately after the merger of Air and exhaust gas.
  • the mixing channel 5 preferably cylindrical.
  • a fuel nozzle 8 ensures the supply of liquid fuel 9, a spray cone 11 through a central atomizing bore 10 is generated.
  • Distributor ring 13 fed gaseous fuel 14.
  • the gaseous fuel passes from the distributor ring 13 14 through a regular arrangement of gas injection holes 15, which preferably radially outwards are directed to the entrance of the jet pump mixing section 5.
  • burner configurations can be made For reasons of space, an axial gas injection (not shown) to be favoured.
  • the fresh air 16 passes through a annular arrangement of air holes 17 in the mixing room 5 a, the axes of the air holes 17 in the case a cylindrical mixing chamber 5 preferably skewed should lie to burner axis A.
  • the air holes chosen in case of a non-cylindrical mixing room 5 would be the alignment the air holes chosen so that their axes with a slight adjustment in the circumferential direction and parallel run to the middle surface of the mixing chamber.
  • a easy adjustment of the axes of the air holes 17 in tangential direction creates a vortex flow at which the flow around the inner shell 2 and Stabilization of the flame 18 guaranteed.
  • Exhaust gas is in the Case of the embodiment shown in Fig. 1 through an annular and regular arrangement of exhaust gas inlet openings 19 sucked into the mixing chamber 5.
  • Guide vanes 20 issue the incoming exhaust gas flow 21 a twist, which together with that of the oblique oriented air holes 17 caused air swirl a swirl of the exhaust gas-air mixture in and after the Mixing section 5 generated.
  • it can be either air swirl or exhaust gas swirl to be dispensed with.
  • the ideal exhaust gas recirculation rate is about 40% up to 70%, based on the fresh air mass flow.
  • the exhaust gas recirculation rate is chosen so that the adiabatic combustion temperature in the flame zone 18 at about 1350 Degrees Celsius. This can reduce both the NOx emissions as well as the CO and UHC emissions kept low become.
  • the jet pump efficiency must be sufficiently high.
  • the recirculated exhaust gas 21 should the highest possible axial speed component be torn into the mixing section 5.
  • FIG. 3 shows an exemplary embodiment, its feeding geometry is special enables high jet pump efficiency.
  • the narrowing 3 of the outer shell should be relative be small so that the back pressure that the Jet pump must overcome, kept as low as possible can be.
  • the returned occurs Exhaust gas 21 swirled into the mixing channel 5, and the Twisting of the gas mixture is caused either by the Fresh air flow or through (not shown) guide vanes generated in the mixing channel.
  • the cross-sectional area of all air holes 17 should preferably be about 10% to 20% of the Cross-sectional area of the mixing room 5. All burner parts, which is on the right side of the boiler wall 22 and thus located inside the boiler are natural exposed to high thermal stress.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)

Claims (10)

  1. Brûleur avec recirculation des gaz d'échappement pour produire du gaz chaud, comprenant des conduites pour des combustibles liquides et/ou gazeux, un canal de mélange (5) délimité par deux enveloppes (1, 2) concentriques et à symétrie de révolution par rapport à l'axe du brûleur pour mélanger les gaz d'échappement recirculés avec de l'air frais avant l'injection du combustible, sachant que le canal de mélange (5) est réalisé sous forme d'éjecteur annulaire, que les gaz d'échappement sont aspirés à travers le canal d'arrivée d'air frais et que l'enveloppe intérieure (2) se termine, vu dans le sens de circulation principal, avant un rétrécissement de l'enveloppe extérieure (1), caractérisé en ce que le canal de mélange (5) présente des moyens pour faire tourbillonner autour de l'axe du brûleur (A) le mélange gazeux se déplaçant dans une direction principale parallèle à l'axe du brûleur (A).
  2. Brûleur avec recirculation des gaz d'échappement selon la revendication 1, caractérisé en ce que l'enveloppe extérieure (1) s'élargit après le rétrécissement (3) pour former un diffuseur (4).
  3. Brûleur avec recirculation des gaz d'échappement selon la revendication 1 ou 2, caractérisé par plusieurs ouvertures (17) pour faire entrer de l'air frais (16) dans le canal de mélange (5), qui sont réalisées pour former plusieurs éjecteurs distincts pour recirculer les gaz d'échappement (21).
  4. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce que le canal de mélange (5) présente une longueur correspondant au moins au double de la largeur moyenne de son passage annulaire.
  5. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce que le canal de mélange (5) présente une section transversale de circulation essentiellement constante.
  6. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications 3 à 5, caractérisé en ce que les orifices d'entrée (17) pour faire pénétrer l'air frais (16) dans le canal de mélange (5) présentent des moyens pour faire tourbillonner le flux dans le canal de mélange (5).
  7. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce que les orifices d'entrée (19) pour faire pénétrer les gaz d'échappement (21) dans le canal de mélange (5) présentent des moyens (20) pour faire tourbillonner le flux dans le canal de mélange (5).
  8. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications précédentes, caractérisé par une ou plusieurs buses de pulvérisation (8) pour du combustible liquide (9) situées après le canal de mélange (5) par rapport au sens de circulation principal.
  9. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications précédentes, caractérisé par une conduite d'amenée (12) qui est prévue pour introduire du combustible gazeux (14) dans le canal de mélange (5) au travers de plusieurs perçages (15) disposés en cercle.
  10. Brûleur avec recirculation des gaz d'échappement selon l'une des revendications précédentes, caractérisé par un étranglement réglable pour commander le flux de gaz d'échappement (21) pénétrant dans le canal de mélange (5) en fonction de la géométrie du foyer et/ou de l'état de fonctionnement du brûleur.
EP96107956A 1996-05-19 1996-05-19 Brûleur avec recirculation des gaz d'échappement Expired - Lifetime EP0809070B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP96107956A EP0809070B1 (fr) 1996-05-19 1996-05-19 Brûleur avec recirculation des gaz d'échappement
DE59607583T DE59607583D1 (de) 1996-05-19 1996-05-19 Brenner mit Abgasrückführung
AT96107956T ATE204972T1 (de) 1996-05-19 1996-05-19 Brenner mit abgasrückführung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP96107956A EP0809070B1 (fr) 1996-05-19 1996-05-19 Brûleur avec recirculation des gaz d'échappement

Publications (2)

Publication Number Publication Date
EP0809070A1 EP0809070A1 (fr) 1997-11-26
EP0809070B1 true EP0809070B1 (fr) 2001-08-29

Family

ID=8222794

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96107956A Expired - Lifetime EP0809070B1 (fr) 1996-05-19 1996-05-19 Brûleur avec recirculation des gaz d'échappement

Country Status (3)

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EP (1) EP0809070B1 (fr)
AT (1) ATE204972T1 (fr)
DE (1) DE59607583D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11187408B2 (en) 2019-04-25 2021-11-30 Fives North American Combustion, Inc. Apparatus and method for variable mode mixing of combustion reactants

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100478085B1 (ko) * 1999-12-22 2005-03-24 주식회사 포스코 산소부화 가스버너
DE102006049875A1 (de) * 2006-10-23 2008-04-24 Robert Bosch Gmbh Gemischbildungseinrichtung
DE102012110506B4 (de) * 2012-11-02 2017-04-27 Webasto SE Hochdruckzerstäubungsbrenneranordnung
DE102016001893A1 (de) 2016-02-17 2017-08-17 Eisenmann Se Brennereinheit und Vorrichtung zum Temperieren von Gegenständen

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3822004A1 (de) * 1988-06-30 1990-01-04 Babcock Werke Ag Brenner
CH678100A5 (fr) * 1989-03-10 1991-07-31 Oertli Waermetechnik Ag
DE8909288U1 (de) * 1989-07-14 1989-11-30 Electro-Oil GmbH, 2057 Reinbek Feuerung mit einer Einrichtung zum Rückführen von Verbrennungsprodukten
EP0483520A3 (en) * 1990-10-02 1992-10-14 Vereinigte Aluminium-Werke Aktiengesellschaft Method and apparatus for the combustion of gaseous and liquid fuels generating a low emission of noxious products
DE9213737U1 (de) * 1992-10-12 1992-12-10 MEKU Metallverarbeitungs-GmbH, 7735 Dauchingen Vorrichtung zur Montage eines Brenners an einem Heizkessel
DE4238529C2 (de) * 1992-11-14 1999-02-04 Deutsch Zentr Luft & Raumfahrt Brenner zur Heißgaserzeugung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11187408B2 (en) 2019-04-25 2021-11-30 Fives North American Combustion, Inc. Apparatus and method for variable mode mixing of combustion reactants

Also Published As

Publication number Publication date
EP0809070A1 (fr) 1997-11-26
ATE204972T1 (de) 2001-09-15
DE59607583D1 (de) 2001-10-04

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