EP0394911B1 - Feuerungsanlage - Google Patents

Feuerungsanlage Download PDF

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Publication number
EP0394911B1
EP0394911B1 EP90107645A EP90107645A EP0394911B1 EP 0394911 B1 EP0394911 B1 EP 0394911B1 EP 90107645 A EP90107645 A EP 90107645A EP 90107645 A EP90107645 A EP 90107645A EP 0394911 B1 EP0394911 B1 EP 0394911B1
Authority
EP
European Patent Office
Prior art keywords
burner
fuel
combustion
combustion installation
installation 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
EP90107645A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0394911A1 (de
Inventor
Thomas Dr. Sattelmayer
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 Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0394911A1 publication Critical patent/EP0394911A1/de
Application granted granted Critical
Publication of EP0394911B1 publication Critical patent/EP0394911B1/de
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
    • 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 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/02—Disposition of air supply not passing through burner
    • F23C7/06—Disposition of air supply not passing through burner for heating the incoming 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 
    • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
    • F23C9/08—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber for reducing temperature in combustion chamber, e.g. for protecting walls of combustion chamber
    • 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 furnace according to the preamble of claim 1. It also relates to a method for operating such a furnace.
  • the fuel in combustion plants is injected into a combustion chamber via a nozzle and burned there with the supply of combustion air (see, for example, FR-A-2 370 235).
  • combustion air see, for example, FR-A-2 370 235.
  • the operation of such combustion plants is possible using a gaseous or liquid fuel.
  • a liquid fuel the weak point with regard to clean combustion in terms of NO x , CO, UHC emissions is primarily the necessary extensive atomization (gasification) of the fuel, its degree of mixing with the combustion air and combustion at the lowest possible temperatures .
  • Premix burners are known which are operated with 100% excess air, so that the flame is operated shortly before the point of extinguishing.
  • a maximum of 15% excess air is allowed in combustion plants. Accordingly, the use of such burners in atmospheric combustion plants with the permitted excess air does not result in optimal operation.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, is based on the object of minimizing the pollutant emissions in firing systems of the type mentioned, both when operating with liquid and with gaseous fuels, and in a mixed operation.
  • the main advantage of the invention is that the excess air for the premix burner is replaced by exhaust gas. By adding recirculated exhaust gases to the combustion air, the flame temperature in the combustion chamber is affected in such a way that the combustion takes place at lower temperatures.
  • a heat-treated exhaust gas / fresh air mixture ensures that a completely vaporized fuel / combustion air mixture can be fed to the combustion.
  • This caused by the exhaust gas recirculation improvement causes the fuel vaporizing and lowering the temperature in the combustor chamber that first, the liquid fuel such as a gaseous fuel is burned, and secondly that the x for the NO formation responsible high flame temperatures can not occur more.
  • the firing system is operated with a gaseous fuel, there is already a gasified mixture, but the flame temperature is also positively influenced by the exhaust gas recirculation mentioned. In a mixed operation, all advantages come into play at the same time.
  • Another advantage of the invention lies in a preferred embodiment of the burner. Despite the simplest geometric design, there is no danger of reignition the flame from the combustion chamber into the burner is feared.
  • the furnace N consists of a burner A, which will be discussed in more detail later, which is followed by a flame tube P in the direction of flow, which in turn extends over the entire combustion chamber 11.
  • a concentric pipe Q which is part of a heat exchanger M, is located between the outer casing of the combustion system N and the flame pipe P.
  • the concentric tube Q has an end cover in the flow direction, which has one or more bypass devices. These each consist of an opening L with an associated bypass flap K.
  • a line coming from the outside leads the liquid fuel 12 to a nozzle 3 in the burner A.
  • a burner A is preceded by a regulation for creating an air / flue gas mixture H:
  • the flue gases C from the chimney and the fresh air D from the environment flow through a metering device E and F and are here in the desired ratio to a mixture H of approx 50 - 100 ° C temperature, before it is fed into the combustion system N by a fan G.
  • the blower G initially requests the mixture to a heat exchanger M integrated in the flame tube P, which is designed, for example, as a tube ribbed on both sides or in one side, in which the mixture H is heated to the desired temperature. This temperature can be brought to the desired setpoint by means of the bypass flaps K mentioned above.
  • blowers G, Heat exchanger M and burner A can be installed together in a single housing, which, like conventional burners, is flanged to boiler B.
  • the type of operation described above and the type of burner described below also make it possible to recirculate a large amount of exhaust gas C, which not only has a positive effect on the temperature of the air / exhaust gas mixture, but also has the effect that the flame temperature can be reduced as far as possible , which counteracts the formation of NO x . So there are no problems with the surface temperature of the burner.
  • the circuit described here has a number of other advantages, for example that the degree of recirculation of the exhaust gas C and the preheating temperature of the processed mixture 15 can be set easily and in a defined manner. Because the blower G does not come into contact with heating gases, the lowest possible blower output is required. In addition, normal design solutions with common materials can be provided for this. Furthermore, the present circuit proves to be advantageous in that good dynamics can be determined when the burner is started, which enables the target air temperature to be reached quickly.
  • FIG. 3-5 In order to better understand the structure of the burner A, it is advantageous if the reader simultaneously uses the individual sections according to FIG. 3-5 for FIG. Furthermore, in order not to make FIG. 2 unnecessarily confusing, the baffles 21a, 21b shown schematically in FIGS. 3-5 have only been hinted at. In the following, the rest of Fig. 3-5 is also optionally referred to in the description of Fig. 2 as required.
  • the burner A according to FIG. 2, which is a premix burner that can be used in atmospheric combustion plants, consists of two half-hollow partial cone bodies 1, 2, which are offset from one another.
  • the offset of the respective central axis 1b, 2b of the partial cone bodies 1, 2 to one another creates a tangential one on both sides in a mirror-image arrangement Air inlet slot 19, 20 free (Fig. 3-5), through which the processed mixture 15 (preheated exhaust gas / fresh air mixture) flows into the interior of the burner A, ie into the cone cavity 14.
  • the two partial cone bodies 1, 2 each have a cylindrical initial part 1a, 2a, which likewise run offset to one another analogously to the partial cone bodies 1, 2, so that the tangential air inlet slots 19, 20 are present from the beginning.
  • a nozzle 3 is accommodated in this cylindrical starting part 1a, 2a, the fuel injection 4 of which coincides with the narrowest cross section of the conical cavity 14 formed by the two partial cone bodies 1, 2.
  • the burner A can be made purely conical, that is to say without cylindrical starting parts 1a, 2a.
  • Both partial cone bodies 1, 2 optionally each have a fuel line 8, 9, which are provided with fuel nozzles 17 through which a gaseous fuel 13, to which the processed mixture 15 flowing through the tangential air inlet slots 19, 20 can be mixed.
  • the position of these fuel lines 8, 9 is shown schematically in FIGS.
  • the fuel lines 8, 9 are attached to the end of the tangential air inlet slots 19, 20, so that the admixture 16 of the gaseous fuel 14 with the inflowing prepared mixture 15 is also there takes place. Mixed operation with both types of fuel is of course possible.
  • the burner A On the combustion chamber side 22, the burner A has an end wall 10 which forms the beginning of the combustion chamber 11.
  • the liquid fuel 12 flowing through the nozzle 3 is injected into the cone cavity 14 at an acute angle such that a cone-shaped fuel spray which is as homogeneous as possible is obtained in the burner outlet plane.
  • the fuel injector 4 can be an air-assisted nozzle or a pressure atomizer.
  • the conical liquid fuel profile 5 is surrounded by a tangentially flowing rotating mixture stream 15.
  • the concentration of the liquid fuel 12 is continuously reduced by the mixed-in combustion air 15. If gaseous fuel 13 is injected 16, the mixture formation with the prepared "combustion air” 15 occurs directly at the end of the air inlet slots 19, 20.
  • the optimal, homogeneous fuel concentration over the cross section is achieved in the area of the vortex run-up, that is to say in the area of the return flow zone 6, in that the fuel droplets generated by the oil nozzle are forced onto a rotational speed component by the vortex flow receive. The centrifugal force generated thereby drives the droplets of the liquid fuel 12 radially outwards. At the same time, however, the evaporation acts.
  • the backflow zone 6, which is once geometrically fixed, is inherently position-stable, because the swirl number increases in the direction of flow in the region of the cone shape of the burner A.
  • the design of the burner A is particularly suitable, given the given length of the burner, of changing the size of the tangential air inlet slots 19, 20 by fixing the partial cone bodies 1, 2 to the wall 10, for example using a releasable connection that is not shown in the figure.
  • the distance between the two central axes 1b, 2b (FIG. 3-5) decreases or increases as a result of radial displacement of the two partial cone bodies 1, 2 to and from one another, and the gap size of the tangential air inlets 19, 20 changes accordingly, as shown in FIG Fig.
  • the partial cone bodies 1, 2 can also be displaced relative to one another in another plane, as a result of which even an overlap thereof can be controlled. Yes, it is even possible to move the partial cone bodies 1, 2 spirally into one another by means of a counter-rotating movement. It is therefore in your hand to vary the shape and size of the tangential air inlets 19, 20 as desired, with which the burner A can be individually adapted without changing its overall length.
  • the position of the guide plates 21a, 21b can also be seen from FIGS. 3-5. They have flow introduction functions, with the respective end of the partial cone body 1 depending on their length and 2 extend in the flow direction of the combustion air 15.
  • the channeling of the combustion air into the cone cavity 14 can be optimized by opening or closing the guide plates 21a, 21b about the pivot point 23, in particular this is necessary if the original gap size of the tangential air inlet slots 19, 20 is changed.
  • burner A can also be operated without baffles 21a, 21b.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Combustion Of Fluid Fuel (AREA)
EP90107645A 1989-04-27 1990-04-23 Feuerungsanlage Expired - Lifetime EP0394911B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1612/89A CH680816A5 (enrdf_load_stackoverflow) 1989-04-27 1989-04-27
CH1612/89 1989-04-27

Publications (2)

Publication Number Publication Date
EP0394911A1 EP0394911A1 (de) 1990-10-31
EP0394911B1 true EP0394911B1 (de) 1994-03-30

Family

ID=4214508

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90107645A Expired - Lifetime EP0394911B1 (de) 1989-04-27 1990-04-23 Feuerungsanlage

Country Status (5)

Country Link
US (1) US5118283A (enrdf_load_stackoverflow)
EP (1) EP0394911B1 (enrdf_load_stackoverflow)
JP (1) JP2957225B2 (enrdf_load_stackoverflow)
CH (1) CH680816A5 (enrdf_load_stackoverflow)
DE (1) DE59005152D1 (enrdf_load_stackoverflow)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006000174A1 (de) * 2006-04-13 2007-10-18 Honeywell Technologies Sarl Öl-Vormischbrenner und Betriebsverfahren dafür
DE102011012493A1 (de) * 2011-02-25 2012-08-30 Robert Bosch Gmbh Ölvormischbrenner
CN104373961A (zh) * 2013-08-16 2015-02-25 阿尔斯通技术有限公司 喷燃器布置及用于操作喷燃器布置的方法

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH680157A5 (enrdf_load_stackoverflow) * 1989-12-01 1992-06-30 Asea Brown Boveri
US5388409A (en) * 1993-05-14 1995-02-14 Stirling Thermal Motors, Inc. Stirling engine with integrated gas combustor
DE4404389A1 (de) * 1994-02-11 1995-08-17 Abb Research Ltd Brennkammer mit Selbstzündung
DE4411624A1 (de) * 1994-04-02 1995-10-05 Abb Management Ag Brennkammer mit Vormischbrennern
DE4422535A1 (de) * 1994-06-28 1996-01-04 Abb Research Ltd Verfahren zum Betrieb einer Feuerungsanlage
DE4441641A1 (de) * 1994-11-23 1996-05-30 Abb Management Ag Brennkammer mit Vormischbrennern
DE19523094A1 (de) * 1995-06-26 1997-01-02 Abb Management Ag Brennkammer
DE19545309A1 (de) * 1995-12-05 1997-06-12 Asea Brown Boveri Vormischbrenner
DE10040869A1 (de) * 2000-08-21 2002-03-07 Alstom Power Nv Verfahren und Vorrichtung zur Unterdrückung von Strömungswirbeln innerhalb einer Strömungskraftmaschine
DE10050248A1 (de) * 2000-10-11 2002-04-18 Alstom Switzerland Ltd Brenner
EP1510755B1 (de) * 2003-09-01 2016-09-28 General Electric Technology GmbH Brenner mit Brennerlanze und gestufter Brennstoffeindüsung
EP2413031B1 (de) * 2010-07-26 2014-05-07 Hovalwerk AG Vormischende Verbrennungseinrichtung
CA2846969C (en) * 2013-03-15 2022-08-30 Luc Laforest Liquefied fuel combustor with integrated evaporator device and associated method
CN106152141B (zh) * 2016-08-16 2018-10-30 李川凌 一种燃油加氢混合燃烧设备

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3174526A (en) * 1960-08-23 1965-03-23 Linde Robert Albert Von Atomizing burner unit
US3258052A (en) * 1963-01-18 1966-06-28 Colt Ventilation & Heating Ltd Heat generators
DE2650660A1 (de) * 1976-11-05 1978-05-11 Interliz Anstalt Heizkessel mit einem heissgasgenerator fuer fluessige oder gasfoermige brennstoffe
US4380429A (en) * 1979-11-02 1983-04-19 Hague International Recirculating burner
DE3662462D1 (en) * 1985-07-30 1989-04-20 Bbc Brown Boveri & Cie Dual combustor
DE3770425D1 (de) * 1986-12-11 1991-07-04 Dreizler Walter Heizkesselanlage mit externer abgasrueckfuehrung.
CH674561A5 (enrdf_load_stackoverflow) * 1987-12-21 1990-06-15 Bbc Brown Boveri & Cie

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006000174A1 (de) * 2006-04-13 2007-10-18 Honeywell Technologies Sarl Öl-Vormischbrenner und Betriebsverfahren dafür
DE102006000174B4 (de) * 2006-04-13 2008-06-26 Honeywell Technologies Sarl Öl-Vormischbrenner und Betriebsverfahren dafür
DE102006000174B9 (de) * 2006-04-13 2009-04-16 Honeywell Technologies Sarl Öl-Vormischbrenner und Betriebsverfahren dafür
DE102011012493A1 (de) * 2011-02-25 2012-08-30 Robert Bosch Gmbh Ölvormischbrenner
DE102011012493B4 (de) * 2011-02-25 2012-09-20 Robert Bosch Gmbh Ölvormischbrenner
CN104373961A (zh) * 2013-08-16 2015-02-25 阿尔斯通技术有限公司 喷燃器布置及用于操作喷燃器布置的方法
CN104373961B (zh) * 2013-08-16 2018-10-02 安萨尔多能源瑞士股份公司 喷燃器布置及用于操作喷燃器布置的方法

Also Published As

Publication number Publication date
DE59005152D1 (de) 1994-05-05
EP0394911A1 (de) 1990-10-31
JPH02298702A (ja) 1990-12-11
CH680816A5 (enrdf_load_stackoverflow) 1992-11-13
JP2957225B2 (ja) 1999-10-04
US5118283A (en) 1992-06-02

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