EP0809070A1 - Brûleur avec recirculation des gaz d'échappement - Google Patents

Brûleur avec recirculation des gaz d'échappement Download PDF

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Publication number
EP0809070A1
EP0809070A1 EP96107956A EP96107956A EP0809070A1 EP 0809070 A1 EP0809070 A1 EP 0809070A1 EP 96107956 A EP96107956 A EP 96107956A EP 96107956 A EP96107956 A EP 96107956A EP 0809070 A1 EP0809070 A1 EP 0809070A1
Authority
EP
European Patent Office
Prior art keywords
exhaust gas
mixing channel
gas recirculation
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.)
Granted
Application number
EP96107956A
Other languages
German (de)
English (en)
Other versions
EP0809070B1 (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 AT96107956T priority Critical patent/ATE204972T1/de
Priority to DE59607583T priority patent/DE59607583D1/de
Priority to EP96107956A priority patent/EP0809070B1/fr
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 the preamble of claim 1.
  • Burners are known from documents EP-A-0 430 011 and EP-491 079, in which exhaust gas is returned to the primary combustion zone by means of air nozzles. In these cases, the mixing of fresh air and exhaust gas and the primary combustion take place in the same area.
  • a burner has become known from EP-A-0 394 800, which consists of partial cone bodies with tangential combustion air inlet channels, in which air and recirculated exhaust gas are mixed before the actual combustion process. After the mixing of incoming air with recirculated exhaust gas, a premixing of liquid or gaseous fuel with the previously generated exhaust gas / air mixture takes place in a conical cavity. A sufficiently high temperature of the exhaust gas / air mixture also enables the liquid fuel to be pre-evaporated. The latter property is responsible for the blue color of the flame when the burner is operating with liquid fuel.
  • the advantages of a burner with exhaust gas recirculation are that the highest possible combustion temperature, with good mixing of air and exhaust gas before combustion and with sufficient cooling of the recirculated exhaust gas, is greatly reduced. As a direct consequence of the lowering of the maximum combustion temperature, the emission of nitrogen oxides (NOx) is reduced. With good pre-evaporation and premixing, the combustion temperature also very uniform. At the same time, emissions of carbon monoxide (CO) and unburned hydrocarbons (UHC) can be kept low. Finally, soot can be avoided thanks to good pre-evaporation and premixing.
  • NOx nitrogen oxides
  • CO carbon monoxide
  • UHC unburned hydrocarbons
  • the object of the invention is to simplify and expand the design of a burner of the type mentioned at the outset in order to minimize the pollutant emissions and the need for external energy in each operation, both when operating with liquid and with gaseous fuels. According to the invention, this is achieved by the features listed in claim 1.
  • an important advantage of the invention is that particularly intimate mixing of exhaust gas and air takes place before the fuel is injected. Excellent pre-evaporation and premixing of the fuel are also achieved in this way.
  • the construction of the present invention is significantly simpler than, for example, that known from EP-A-0 394 800.
  • Another advantage of the invention is the good efficiency of the annular jet pump, which entrains exhaust gases through the fresh air flow. This efficiency can be improved even further by dividing the fresh air inlet into the mixing duct into a number of separate inlet openings. Thanks to its high jet pump efficiency and its low back pressure after the jet pump, the burner proposed here can be operated with a conventional single-stage fan. In addition, it may be possible to dispense with the start-up measures that are otherwise customary in exhaust gas recirculation burners.
  • the increased temperature of the exhaust gas / air mixture in combination with the flame stabilization in the area of the burner outlet ensures that a mixture of Fresh air, exhaust gas and pre-evaporated fuel is supplied to the combustion.
  • the optimization of the mixture achieved due to the exhaust gas recirculation also influences the flame temperature in the combustion chamber in such a way that no local temperature peaks can occur there, which would lead to increased NOx formation.
  • the premixing of the fuel avoids the occurrence of flame zones with too low a temperature, which would lead to increased CO and UHC emissions.
  • Another advantage of the invention lies in the possibility of special flame stabilization. If, after the narrowing, the outer shell widens to a suitably dimensioned diffuser, the flame front in the vortex flow generated by the jet pump cannot migrate back to the fuel injection. This not only achieves the desired premixing and pre-evaporation, it also succeeds in protecting the fuel injection from soot and overheating. This property helps to reduce the burner's susceptibility to failure.
  • the burner body consists of an essentially rotationally symmetrical outer shell 1 and an inner shell 2 arranged concentrically therewith.
  • the outer shell 1 has a striking narrowing 3 and a diffuser part 4.
  • a mixing channel 5 is delimited by a part 6 of the outer shell 1 and a part 7 of the inner shell 2, the course of the shell parts 6 and 7 being selected such that the cross-sectional area of the jet pump mixing path 5 is measured over a length measured in the main flow direction (ie parallel to the burner axis) of at least twice the radial gap width of the mixing section remains largely constant.
  • the mixing duct 5 begins immediately after the air and exhaust gas have been brought together.
  • the mixing channel 5 is preferably of cylindrical design. In certain cases, however, it is conceivable to use a conical mixing section, for example, for reasons of space.
  • a fuel nozzle 8 ensures the supply of the liquid fuel 9, a spray cone 11 being generated through a central atomizing bore 10.
  • Gaseous fuel 14 is fed to a distributor ring 13 via a feed line 12. The gaseous fuel 14 passes from the distributor ring 13 through a regular arrangement of gas injection bores 15, which are preferably radially outward are directed to the inlet of the jet pump mixing section 5. In certain burner configurations, however, axial gas injection (not shown) may be preferred for reasons of space.
  • the fresh air 16 enters the mixing chamber 5 through an annular arrangement of air bores 17, the axes of the air bores 17 in the case of a cylindrical mixing chamber 5 preferably being skewed to the burner axis A.
  • the alignment of the air bores would be chosen such that their axes run with a slight inclination in the circumferential direction and parallel to the central surface of the mixing chamber.
  • a slight adjustment of the axes of the air bores 17 in the tangential direction contributes to the generation of a vortex flow, which guarantees the flow around the inner shell 2 and stabilization of the flame 18.
  • exhaust gas is sucked into the mixing chamber 5 through an annular and regular arrangement of exhaust gas inlet openings 19.
  • Guide vanes 20 impart a swirl to the incoming exhaust gas flow 21, which together with the air swirl caused by the obliquely oriented air bores 17 generates a swirl of the exhaust gas / air mixture in and after the mixing section 5.
  • air swirl or exhaust gas swirl can be dispensed with in some cases.
  • the ideal exhaust gas recirculation rate is approximately 40% to 70%, based on the fresh air mass flow.
  • the exhaust gas recirculation rate is selected such that the adiabatic combustion temperature in the flame zone 18 is approximately 1350 degrees Celsius. This allows the NOx emissions as well as the CO and UHC emissions to be kept low.
  • the jet pump efficiency must be sufficiently high.
  • the recirculated exhaust gas 21 should the highest possible axial speed component are torn into the mixing section 5.
  • FIG. 3 shows an exemplary embodiment, the feed geometry of which enables a particularly high jet pump efficiency.
  • the constriction 3 of the outer shell should be of relatively small dimensions so that the counterpressure which the jet pump has to overcome can be kept as low as possible.
  • the recirculated exhaust gas 21 enters the mixing channel 5 without swirling, and the swirling of the gas mixture is generated either by the fresh air flow or by guide vanes (not shown) in the mixing channel.
  • the cross-sectional area of all air bores 17 should preferably be approximately 10% to 20% of the cross-sectional area of the mixing chamber 5. All burner parts, which are located on the right side of the boiler wall 22 and thus inside the boiler, are naturally exposed to a high thermal load.
  • FIG. 1 shows a further possibility in which part of the fresh air is led through a deflection duct into the part of the mixing duct lying downstream and thereby cools the inner contour .
  • the embodiment variant shown in FIG. 1 shows a further possibility in which part of the fresh air is led through a deflection duct into the part of the mixing duct lying downstream and thereby cools the inner contour .

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
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
AT96107956T ATE204972T1 (de) 1996-05-19 1996-05-19 Brenner mit abgasrückführung
DE59607583T DE59607583D1 (de) 1996-05-19 1996-05-19 Brenner mit Abgasrückführung
EP96107956A EP0809070B1 (fr) 1996-05-19 1996-05-19 Brûleur avec recirculation des gaz d'échappement

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 true EP0809070A1 (fr) 1997-11-26
EP0809070B1 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)

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

Cited By (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
WO2008049757A1 (fr) * 2006-10-23 2008-05-02 Robert Bosch Gmbh Dispositif de formation d'un mélange destiné à mélanger un premier gaz, un deuxième gaz et un fluide, en particulier un liquide combustible, de préférence pour former un gaz de synthèse pour véhicule automobile ou similaires
DE102012110506A1 (de) * 2012-11-02 2014-05-08 Webasto SE Hochdruckzerstäubungsbrenneranordnung
DE102016001893A1 (de) * 2016-02-17 2017-08-17 Eisenmann Se Brennereinheit und Vorrichtung zum Temperieren von Gegenständen

Families Citing this family (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

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE8909288U1 (de) * 1989-07-14 1989-11-30 Electro-Oil GmbH, 2057 Reinbek Feuerung mit einer Einrichtung zum Rückführen von Verbrennungsprodukten
EP0348646A2 (fr) * 1988-06-30 1990-01-03 Deutsche Babcock Energie- Und Umwelttechnik Aktiengesellschaft Brûleur
EP0386732A2 (fr) * 1989-03-10 1990-09-12 Oertli Wärmetechnik Ag Dispositif de combustion pour brûleur à deux combustibles
EP0483520A2 (fr) * 1990-10-02 1992-05-06 VAW Aluminium AG Procédé et dispositif pour la combustion des combustibles gazeux et liquided avec génération réduite des substances nocives
DE9213737U1 (de) * 1992-10-12 1992-12-10 MEKU Metallverarbeitungs-GmbH, 7735 Dauchingen Vorrichtung zur Montage eines Brenners an einem Heizkessel
DE4238529A1 (de) * 1992-11-14 1994-05-19 Deutsche Forsch Luft Raumfahrt Brenner zur Heißgaserzeugung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0348646A2 (fr) * 1988-06-30 1990-01-03 Deutsche Babcock Energie- Und Umwelttechnik Aktiengesellschaft Brûleur
EP0386732A2 (fr) * 1989-03-10 1990-09-12 Oertli Wärmetechnik Ag Dispositif de combustion pour brûleur à deux combustibles
DE8909288U1 (de) * 1989-07-14 1989-11-30 Electro-Oil GmbH, 2057 Reinbek Feuerung mit einer Einrichtung zum Rückführen von Verbrennungsprodukten
EP0483520A2 (fr) * 1990-10-02 1992-05-06 VAW Aluminium AG Procédé et dispositif pour la combustion des combustibles gazeux et liquided avec génération réduite des substances nocives
DE9213737U1 (de) * 1992-10-12 1992-12-10 MEKU Metallverarbeitungs-GmbH, 7735 Dauchingen Vorrichtung zur Montage eines Brenners an einem Heizkessel
DE4238529A1 (de) * 1992-11-14 1994-05-19 Deutsche Forsch Luft Raumfahrt Brenner zur Heißgaserzeugung

Cited By (6)

* 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
WO2008049757A1 (fr) * 2006-10-23 2008-05-02 Robert Bosch Gmbh Dispositif de formation d'un mélange destiné à mélanger un premier gaz, un deuxième gaz et un fluide, en particulier un liquide combustible, de préférence pour former un gaz de synthèse pour véhicule automobile ou similaires
DE102012110506A1 (de) * 2012-11-02 2014-05-08 Webasto SE Hochdruckzerstäubungsbrenneranordnung
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
US10928134B2 (en) 2016-02-17 2021-02-23 Eisenmann Se Burner unit and device for the temperature control of objects

Also Published As

Publication number Publication date
EP0809070B1 (fr) 2001-08-29
DE59607583D1 (de) 2001-10-04
ATE204972T1 (de) 2001-09-15

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