EP1807656B1 - Bruleur a premelange - Google Patents

Bruleur a premelange Download PDF

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Publication number
EP1807656B1
EP1807656B1 EP05803397.8A EP05803397A EP1807656B1 EP 1807656 B1 EP1807656 B1 EP 1807656B1 EP 05803397 A EP05803397 A EP 05803397A EP 1807656 B1 EP1807656 B1 EP 1807656B1
Authority
EP
European Patent Office
Prior art keywords
burner
swirl
flow
premix burner
premix
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.)
Not-in-force
Application number
EP05803397.8A
Other languages
German (de)
English (en)
Other versions
EP1807656A1 (fr
Inventor
Hans Peter Knoepfel
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.)
Ansaldo Energia IP UK Ltd
Original Assignee
Ansaldo Energia IP UK Ltd
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Publication of EP1807656A1 publication Critical patent/EP1807656A1/fr
Application granted granted Critical
Publication of EP1807656B1 publication Critical patent/EP1807656B1/fr
Not-in-force 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
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • 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

Definitions

  • the invention relates to a premix burner for a heat generator with complementary to a swirler Operakegelschalen that span a conically expanding swirl space and mutually limit tangential air inlet slots and with feeds for gaseous and / or liquid fuel, of which at least one along the air inlet slots to the Part cone shells and at least one other along a swirl space centrally passing through the burner axis are arranged.
  • Vormischbrenner be successfully used for firing combustion chambers for driving gas turbine plants for many years and represent largely mature components in terms of their burner properties. Depending on the use and desired burner performance generic Vormischbrenner are available both in terms of burner performance and in terms of reduced pollutant emission are optimized.
  • the EP 0 321 809 B1 Such a premix burner can be seen, which consists essentially of two hollow, conical, nested in the flow direction part bodies whose respective L Lucasssymmetrieachsen offset from each other, so that the adjacent walls of the body part in the longitudinal direction tangential slots for a Form combustion air flow.
  • liquid fuel is injected into the swirl space enclosed by the part bodies via a central nozzle, while gaseous fuel is introduced via the further nozzles provided in the region of the tangential air inlet slots in the longitudinal extent.
  • the burner concept of the premix burner mentioned above is based on the generation of a closed swirl flow within the conically expanding swirl space.
  • the swirl flow becomes unstable and changes into an annular swirl flow with a backflow zone in the flow core.
  • the location at which the swirl flow passes by bursting into an annular swirl flow with backflow zone is essentially determined by the cone angle inscribed by the sub-cone shells and the slot width of the air inlet slots.
  • narrow limits are set in the choice for dimensioning the slit width and the cone angle, which ultimately determines the overall length of the burner, so that a desired flow field is established, which leads to the formation of a swirl flow, forming an annular swirl flow in the burner throat region a spatially stable remindströmzone bursts, ignites in the fuel-air mixture to form a spatially stable flame.
  • a reduction of the air inlet slots leads to an upstream displacement of the remindströmzone, whereby then, however, the mixture of fuel and air in time and spatially earlier comes to the ignition.
  • a swirling flow continuing mixing section is provided in the form of a mixing tube, as for example.
  • a swirling flow continuing mixing section is provided in the form of a mixing tube, as for example.
  • transition channels extending in the flow direction between the swirl body and the mixing section are provided, which serve to transfer the swirl flow formed in the swirl body into the mixing section downstream of the transition channels.
  • the publication EP 076 133 A describes a ⁇ lverdampfungsbrenner a different to the registration object genus, wherein also the described oil vaporization burner according to the embodiments in Fig. 1 to 5 provides a kind of premix burner with cylindrically shaped baffles, which represents a departure from the burner concept according to the application.
  • the publication DE 195 27 453 A1 can be taken only the indication that downstream of the swirl generator for purposes of improved mixing and associated reduction of NOX emissions, a vortex generator, preferably in the form of a Venturi nozzle is provided.
  • the feed of liquid fuel also exerts a decisive influence on the flow dynamics of the swirl flow forming inside the swirl body as well as the return flow zone which forms as stable a space as possible downstream of the swirl body.
  • a rich fuel-air mixture forming along the burner axis in particular for premix burners of larger design, whereby the risk of so-called flashback in the area of the swirl space increases.
  • such reignitions inevitably lead to increased NOx emissions, since this does not burn completely mixed fuel / air mixture fractions.
  • re-ignition phenomena are especially dangerous and must be avoided, as they can lead to thermal and mechanical stresses and as a result to irreversible damage to the structure of the premix burner.
  • the invention has for its object to provide a premix burner for a heat generator, in particular for firing a combustion chamber for driving a gas turbine plant with complementary to a swirler part cone shells, which span a conically expanding swirl space and limit each other tangential air inlet slots, and with feeds for gaseous and / or liquid fuel, of which at least one along the air inlet slots on the partial cone shells and at least one other along the swirl space centrally passing burner axis are arranged, such that its use is possible even with larger-sized gas turbine plants, which require a larger burner load without to change the structural design of the premix burner significantly.
  • it is important to keep the emission of pollutants caused by the burner as low as possible despite the measures maximizing the burner performance.
  • Another desirable aspect concerns the size of such a premix burner, which is to be kept as compact and small as possible.
  • the invention is based on the idea of increasing the absorption capacity of a pre-mixing burner which is known per se and optimized for a corresponding burner output without changing the dimensions of geometry, such as the length and diameter of the premix burner, which determine the size of the premix burner.
  • a premix burner according to the features of the preamble of claim 1 is characterized in that at least n partial cone shells surround the swirl space, which limit n air inlet slots, that at least five partial cone shells surround the swirl space and the same number of air inlet slots surround the swirl space in order to increase the intake capacity of the premix burner wherein the premix burner has both the same length, the same inner diameter and the same outer Vormischbrenner carefullymesser as a Vormischbrenner with less than five Ambikegelschalen and the slot width of the air inlet slots is at least as large as in the Vormischbrenner with less than five Operakegelschalen.
  • the compact burner design can basically be kept unchanged and at the same time circumvents the problem of increased fuel distribution by the central diessigbrennscherindüsung in the burner center, especially the speed the air flows flowing through the premix burner increases to the same extent, with which the air throughput and thus the absorption capacity of the premix burner is also increased. This is also the reason that the risk of backfire can be significantly reduced despite greater burner performance.
  • an increase in the so-called burner nominal speed leads to the formation of a spatially stable return flow zone downstream of the burner and the associated flame stabilization being affected.
  • the inner contour of the mixing tube is designed as a diffuser in the flow direction, ie, in a preferred embodiment, the inner contour of the mixing tube expands with a suitably predetermined cone angle ⁇ relative to the flow axis.
  • FIG. 1 a longitudinal section through a burner assembly is shown, which has substantially three sub-components; a cone-shaped premix burner 1, a transition piece 2 and a mixing section 3, which is formed in the form of a tubular mixing element 4.
  • FIG. 2 A cross-sectional representation of such a known swirl generator 1 is shown in FIG FIG. 2 shown. From this illustration, clearly the four an inner swirl chamber 6 spanning partial cone shells 5 emerge.
  • the four air inlet slots 7 define an outer premix burner diameter Da and a size Further, the cross-sectional view is according to FIG. 2 the respective mutual spatial offset of the partial cone shells with respect to their Teiikegelschalenstoffmay, which are indicated in each case by a cross, to remove.
  • Through the respective air inlet slots 7 passes both air L, indicated by the respective large arrows, and preferably gaseous fuel B, which are provided by corresponding supply lines 8, which are provided at the leading edges of the Operakegelschalen 5, in the interior of the swirl generator 1.
  • Inside the Swirl generator 1 forms a swirl flow, which is axially along the burner axis A (see FIG. 1 ) spreads downstream.
  • the downstream in the flow direction in the premix burner 1 transition piece 2 serves a largely lossless transfer of forming inside the swirler 1 swirl flow in the downstream subsequent mixing section 3.
  • transitional channels 9 are provided in the transition piece, which are formed for a corresponding flow transfer.
  • the burner nominal velocity ie the flow velocity
  • the burner nominal velocity ie the flow velocity
  • the fuel-air mixture forming in the interior of the swirl generator is able to spread axially relative to the burner axis A
  • the burner nominal velocity ie the flow velocity
  • the burner nominal velocity ie the flow velocity
  • the fuel-air mixture forming in the interior of the swirl generator is able to spread axially relative to the burner axis A
  • FIG. 1 bottom partial longitudinal section view of a tubular mixing element 4, which provides a flow in the flow direction with the angles ⁇ expanding flow cross-sectional contour and thus acts as a diffuser, whereby the axial velocity of the flow is reduced.
  • transition channels for transferring the swirl flow in the mixing section 3 are also provided in the transition piece.
  • AEV burner Advanced Environmental Vortex Burner
  • EV burner Environmental Vortex burner
  • Premix burners are designed in a manner known per se as a double-cone shell burner, ie the swirl space of the swirl generator is surrounded only by two partial cone shells, the total of only two Limit air intake slots.
  • the swallowing capacity of such an EV premix burner can also be increased in this case, without the burner dimensions being related to change length and diameter.

Landscapes

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

Claims (4)

  1. Brûleur à pré-mélange pour un générateur de chaleur avec des coques partiellement coniques (5) complétées par un générateur de turbulences, qui entourent une chambre de turbulences (6) s'élargissant de manière conique et délimitent des fentes d'entrée d'air (7) tangentes entre elles ainsi qu'avec des conduites d'alimentation pour un carburant gazeux et/ou liquide, dont au moins une est disposée le long des fentes d'entrée d'air (7) au niveau des coques partiellement coniques (5) et au moins une est disposée le long d'un axe de brûleur (A) traversant au centre la chambre de turbulences (6),
    caractérisé en ce que, pour l'augmentation de la capacité d'absorption du brûleur à pré-mélange, au moins cinq coques partiellement coniques (5) entourent la chambre de turbulences (6) et le même nombre de fentes d'entrée d'air délimitent la chambre de turbulences (6).
  2. Brûleur à pré-mélange selon la revendication 1,
    caractérisé en ce que, en aval du générateur de turbulences, un trajet de mélange (3) est prévu sous la forme d'un élément de mélange tubulaire (4) et
    en ce que, entre le générateur de turbulences et le trajet de mélange (3), un élément de transition (2) avec n canaux de transition (9), est prévu pour le transfert d'un écoulement formé dans le générateur de turbulences vers la section de débit du trajet de mélange (3) disposée en aval des canaux de transition (9).
  3. Brûleur à pré-mélange selon la revendication 2,
    caractérisé en ce que l'élément de mélange tubulaire (10) est conçu, dans la direction d'écoulement, au moins partiellement sous la forme d'un diffuseur.
  4. Brûleur à pré-mélange selon la revendication 3,
    caractérisé en ce que l'élément de mélange (4) comprend, immédiatement après l'élément de transition (2), une première zone d'écoulement avec une section d'écoulement constante et
    en aval de la première zone d'écoulement, se trouve une deuxième zone d'écoulement avec une section de débit s'élargissant de manière conique dans la direction de l'écoulement selon un angle α.
EP05803397.8A 2004-11-03 2005-10-27 Bruleur a premelange Not-in-force EP1807656B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH18142004 2004-11-03
PCT/EP2005/055612 WO2006048405A1 (fr) 2004-11-03 2005-10-27 Bruleur a premelange

Publications (2)

Publication Number Publication Date
EP1807656A1 EP1807656A1 (fr) 2007-07-18
EP1807656B1 true EP1807656B1 (fr) 2019-07-03

Family

ID=34974062

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05803397.8A Not-in-force EP1807656B1 (fr) 2004-11-03 2005-10-27 Bruleur a premelange

Country Status (5)

Country Link
US (1) US7491056B2 (fr)
EP (1) EP1807656B1 (fr)
JP (2) JP2008519237A (fr)
CN (1) CN101095012B (fr)
WO (1) WO2006048405A1 (fr)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1807656B1 (fr) 2004-11-03 2019-07-03 Ansaldo Energia IP UK Limited Bruleur a premelange
NZ573156A (en) * 2006-10-24 2012-03-30 Warren Saul Gillespie Induction and fuel delivery system for piston engine using a cyclone to generate vortex mixing of fuel and air mixture before entering the cylinder
EP1975506A1 (fr) * 2007-03-30 2008-10-01 Siemens Aktiengesellschaft Pré-chambre de combustion
EP2257736B1 (fr) 2008-03-07 2015-11-25 Alstom Technology Ltd Procédé de production de gaz chaud
JP5453322B2 (ja) 2008-03-07 2014-03-26 アルストム テクノロジー リミテッド バーナ装置並びにバーナ装置の使用
EP2230455B1 (fr) * 2009-03-16 2012-04-18 Alstom Technology Ltd Brûleur pour une turbine à gaz et procédé de refroidissement local d'un flux de gaz chauds passant par un brûleur
JP5462526B2 (ja) * 2009-05-19 2014-04-02 大阪瓦斯株式会社 管状火炎バーナ
CA2896436C (fr) 2009-07-17 2017-02-07 World Energy Systems Incorporated Procede et appareil pour un generateur de gaz de fond de trou
BR112012022826A2 (pt) 2010-03-08 2018-05-15 Worldenergy Systems Incorporated gerador de vapor de fundo de poço e método de utilização
CN102537959B (zh) * 2012-02-28 2014-08-27 东方电气集团东方锅炉股份有限公司 一种旋流、直流结合型式的气体燃烧器
EP2685163B1 (fr) * 2012-07-10 2020-03-25 Ansaldo Energia Switzerland AG Brûleur de prémélange du type multi-cônes destiné à une turbine à gaz
JP5584260B2 (ja) * 2012-08-08 2014-09-03 日野自動車株式会社 排気浄化装置用バーナー
EP2796789B1 (fr) * 2013-04-26 2017-03-01 General Electric Technology GmbH Chambre de combustion à tubes pour un agencement de chambre de combustion annulaire dans une turbine à gaz
KR102083928B1 (ko) * 2014-01-24 2020-03-03 한화에어로스페이스 주식회사 연소기
DE102014205203B3 (de) * 2014-03-20 2015-05-21 Kba-Metalprint Gmbh Vorrichtung zur thermischen Nachverbrennung von Abluft
DE102014205198A1 (de) 2014-03-20 2015-09-24 Kba-Metalprint Gmbh Brenner und Vorrichtung zur thermischen Nachverbrennung von Abluft
DE102014205200B3 (de) * 2014-03-20 2015-06-11 Kba-Metalprint Gmbh Vorrichtung zur thermischen Nachverbrennung von Abluft
CN108443912B (zh) * 2018-02-08 2023-10-03 中国船舶重工集团公司第七0三研究所 一种自吸式空气辅助雾化双燃料喷嘴

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EP0747635B1 (fr) * 1995-06-05 2003-01-15 Rolls-Royce Corporation Brûleur à prémélange pauvre avec faible production de NOx pour turbines à gaz industrielles
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EP1807656B1 (fr) 2004-11-03 2019-07-03 Ansaldo Energia IP UK Limited Bruleur a premelange

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Also Published As

Publication number Publication date
CN101095012A (zh) 2007-12-26
US20070202453A1 (en) 2007-08-30
US7491056B2 (en) 2009-02-17
JP2012037234A (ja) 2012-02-23
JP5399462B2 (ja) 2014-01-29
WO2006048405A1 (fr) 2006-05-11
EP1807656A1 (fr) 2007-07-18
CN101095012B (zh) 2010-11-10
JP2008519237A (ja) 2008-06-05

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