EP0834040A1 - BRULEUR ET PROCEDE DE FONCTIONNEMENT D'UN BRULEUR DESTINE A UNE COMBUSTION PAUVRE EN NO x? ET EN CO - Google Patents

BRULEUR ET PROCEDE DE FONCTIONNEMENT D'UN BRULEUR DESTINE A UNE COMBUSTION PAUVRE EN NO x? ET EN CO

Info

Publication number
EP0834040A1
EP0834040A1 EP97924865A EP97924865A EP0834040A1 EP 0834040 A1 EP0834040 A1 EP 0834040A1 EP 97924865 A EP97924865 A EP 97924865A EP 97924865 A EP97924865 A EP 97924865A EP 0834040 A1 EP0834040 A1 EP 0834040A1
Authority
EP
European Patent Office
Prior art keywords
combustion
fuel
combustion air
nozzles
distribution body
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
EP97924865A
Other languages
German (de)
English (en)
Other versions
EP0834040B1 (fr
Inventor
Ahmad Al-Halbouni
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.)
WALTER BRINKMANN GMBH
Original Assignee
Joh Vaillant GmbH and Co
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 Joh Vaillant GmbH and Co filed Critical Joh Vaillant GmbH and Co
Publication of EP0834040A1 publication Critical patent/EP0834040A1/fr
Application granted granted Critical
Publication of EP0834040B1 publication Critical patent/EP0834040B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at 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 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • 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 
    • F23C2201/00—Staged combustion
    • F23C2201/20—Burner staging
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2205/00—Assemblies of two or more burners, irrespective of fuel type

Definitions

  • the invention relates to a burner device and a corresponding method for an NO x - and CO-combustion with predominantly separate supply of fuel and combustion air to the combustion chamber, wherein all or most of the combustion air at a plurality of points in space continuously promoted and the combustion chamber is supplied.
  • Fuel is to be understood here to mean substances which react exothermically with oxygen and which are in gaseous or vapor form at ambient temperature and / or when fed into the combustion chamber. Fuel should also be understood to mean liquid or dusty substances with air, steam and / or exhaust gas as carrier gas. Combustion air here is to be understood as meaning gases and / or vapors with an oxygen content which ensures stable combustion with respect to the selected fuel that the combustion air can also contain exhaust gas.
  • the combustion zone is to be understood here as the area in which the combustion takes place
  • the combustion air is usually introduced coaxially with the introduction of the fuel.
  • a fuel jet is generated in the area of the burner mouth.
  • the combustion air is supplied on the outside of the fuel jet and outside the flame area via a mostly ring-shaped distributor, which is positioned near the fuel nozzle, usually coaxially to the fuel nozzle. Because of the considerable spatial distance of the combustion air distributor from the flame area, especially from the flame core, it becomes practical Operation with such burners a uniform mixing of fuel and combustion air or a staged mixture taking place according to predetermined proportions is not achieved.
  • the combustion air is divided into primary and secondary air, so that locally limited Peak values of the oxygen concentration can be reduced and the stochiometric conditions during combustion can be regulated somewhat better.
  • the fundamental disadvantage of this type of burner namely the unsatisfactory controllability of the stochiometric ratios of fuel and combustion air, which are decisive for the formation of pollutants such as nitrogen oxides and carbon monoxide
  • pollutants such as nitrogen oxides and carbon monoxide
  • it can only be reduced with a relatively high outlay.
  • a burner operated by such a method is described, for example, in DE OS 4 142 401.
  • the burner which in this case works with premixing, is operated in a strongly sub-stoichiometric manner.
  • the oxygen that is missing for combustion is only supplied at a significant distance from the burner mouth at one or more points, whereby the direction of the oxygen injection must not be parallel to the main flow direction of the combustion gases.
  • This process provides for the operation of large-format industrial ovens such as rotary kilns and.
  • this method has the general disadvantage that the Combustion air is introduced essentially selectively into areas of the combustion zone with a relatively high flame temperature
  • the length of the diffuser cannot be increased arbitrarily, because otherwise the diffuser would shield the flame too much, which would result in heat emission to the furnace or boiler wall impaired Since the flame length at higher heating outputs can significantly exceed the diffuser length, this means that, especially at higher heating outputs, the area of the flame tip is insufficiently supplied with secondary combustion air has an adverse effect on the pollutant emissions of the burner
  • the multi-stage spatial air grading provides a sub-stoichiometric mixing in the foot area, which gradually changes to superstoichiometry with increasing air ratio, no control of the mixing ratios can be guaranteed with the double-walled burner structure of this state of the art, since the double-walled enclosed space of the cylinder ring quickly becomes complete Mixing of fuel and combustion air sets before ignition occurs at the openings in the outer wall. Combustion also has the disadvantages of premixed flames. The reduction effect important for reducing nitrogen oxide emissions is therefore not given
  • Another way to improve the mixing state is to connect an additional mixing chamber upstream of the combustion chamber, which creates a burner with larger dimensions, which now also has the disadvantages of this type of burner as a burner with premixing.
  • a burner with a very intensive premixing is for example in DE OS 3 915 704, which, however, has an extremely complex construction.
  • the multi-part mixing channels used there require a high amount of energy in order to compensate for the pressure loss caused by them.
  • the mixing channels are also difficult to access and therefore difficult to clean
  • the invention is therefore based on the object x with the aim of NO - and CO-lean combustion, and an intensification of heat transfer between the flame / gas and the wall of the heat sink, a structurally simple and suitable for a compact structure in burner means with predominantly separate supply of fuel and combustion air to create the combustion chamber in which the combustion air is fed in as many stages as possible into larger flame areas.
  • This task results in the following subtasks in particular
  • this object is achieved by a burner device according to the characterizing part of claims 1 and 13 and by an associated method for operating this burner device according to independent method claim 1 1
  • the basic concept of the invention which also relates to the claimed method for operating the burner device, consists in the following Ca 70 to 100 vol% of the total amount of combustion air supplied is by means of one or more combustion air distribution body in a mainly radial direction in the space filled by the flame between the outer wall of the combustion chamber and the contour of the combustion air distribution body fed along the entire or large part of the flame length.
  • the fuel is fed into the combustion zone exclusively in the area of the combustion air Distributor located flame base by means of one or more rows of nozzles arranged around the combustion air distributor
  • the advantages of this concept are that the combustion is initially sub-stoichiometric and, with a gradually increasing air supply, it changes to stoichiometry or over-stoichiometry shortly before the flame tip, where complete burnout is achieved x and CO) drastically reduced
  • This type of feeding the combustion air also has the advantageous effect that the flame is blown away from the combustion air distributor body, so that no direct combustion takes place on the surface of this combustion air distributor body. This lowers the thermal load on the combustion air distributor body , especially since they are additionally cooled by the combustion air flowing through them
  • combustion air supply according to the invention in particular in the case of large-area combustion air distribution bodies, is that they simultaneously lead to cooling the flame, thereby reducing the formation of NO x .
  • the geometry of the combustion zone is largely determined by the geometry of this combustion air distribution body.
  • a function of the combustion air distribution body that is essential to the invention is therefore seen in that the size of the combustion chamber is decisively influenced by the choice of its dimensions.
  • combustion air distribution body There is a large variety of variants for the design of the contour of the combustion air distribution body. Depending on the furnace or boiler room geometry, the choice of a suitable form of combustion air distribution body can optimize the NO x and CO emissions and heat transfer
  • FIG. 1 Further advantageous embodiments of the invention relate to the configuration of the nozzle rows for the fuel supply. It has proven to be particularly effective for optimally maintaining predetermined value ranges of the air ratio ⁇ if the jet direction of the fuel nozzles within the same nozzle row and / or the jet direction of the fuel nozzles of adjacent nozzle rows over different length ranges aim the combustion air distribution body In order to give the fuel flow an additional twist, the jet directions mentioned are at least partially skewed. Furthermore, the combustion air distribution body and / or the fuel nozzles can be designed to be interchangeable in order to optimally adapt their parameters to a predetermined burner output
  • 1 a is a schematic representation of a first variant of a low-CO and NO x burner device with a conical combustion air distribution body for heating purposes
  • 1 b is a schematic representation of a second variant of a low-CO and NO x burner device with a conical combustion air distribution body for industrial purposes
  • 2 a is a schematic representation of a selection of different geometrical
  • Variants of the combustion air distribution body in side view and top view, 2 b is a schematic representation of the interchangeability of the combustion air distribution body
  • 3 a is a schematic representation of variants of the jet directions of the fuel nozzles
  • 3 b is a schematic representation of the interchangeability of the fuel nozzles
  • 3 c is a schematic representation of the oblique fuel holes
  • 3 d is a schematic representation of the fuel annular gap with an internal swirl generator
  • 4 a is a graphical representation of the dependence of the NO x emission values in the exhaust gas on the burner output for a selected variant of a combustion air distribution body, with no premixing of combustion air to the fuel,
  • 4 b is a graphical representation of the dependence of the NO x emission values in the exhaust gas on the burner output for a selected variant of a combustion air distribution body, with premixing of combustion air to the fuel being used (increased fuel nozzle pulse),
  • 5 a is a graphical representation of the dependency of the CO emission values in the exhaust gas on the burner output for a selected variant of a combustion air distribution body, work being carried out without premixing combustion air to the fuel,
  • FIG. 5 b shows a graphical representation of the dependence of the CO emission values in the exhaust gas on the burner output for a selected variant of a combustion air distribution body, with premixing of combustion air to the fuel being used (increased fuel nozzle pulse).
  • a cylindrical fire or combustion chamber (2) with a longitudinal central axis (34) of a burner device is delimited by a conical combustion air distribution body (7) and an outer wall (3) enclosing steel.
  • the outer wall (3) consists of a cylindrical one Shell wall (3a), a top wall (3b) and a bottom wall (3c)
  • combustion chamber details such as viewing openings for visual observation of the flame development in the combustion chamber, openings for the ignition of the gas-air mixture and for temperature measurement in the Lower part of the combustion chamber
  • a UV probe for monitoring the flame
  • a suction probe for exhaust gas extraction to carry out the concentration analysis of the exhaust gas emerging at the exhaust gas outlet (6).
  • the exhaust gas outlet (6) is arranged in the cover wall (3b) of the combustion chamber Fire or combustion chamber (2) can also be polygonal as a prism, has he always has a horizontal or vertical longitudinal central axis (34)
  • This empty space (1) is the part of the combustion chamber (2) that lies below an imaginary level (10) , which sits on the end of the head part (9) of the frustoconical combustion air distribution body (7), the base (15) of which lies on the lower bottom wall (3c) of the combustion chamber (2)
  • the heat is removed from the outer wall (3) via cooling water, which flows around the outer wall (3) either in coils (16) and / or in water chambers (17)
  • the combustion air distribution body (7) consists of simple sheet steel with a large number of openings (1 1) for the exit of the combustion air into the combustion zone. While the almost horizontal head part (9) of the combustion air distribution body is closed, its foot part (8) remains open and is screwed into the air supply pipe (18) The entire combustion air or most of it (> 70 vol% of the total combustion air throughput required for the combustion of 100%) is via the inner pipe (18) of a coaxial pipe into the interior of the combustion air distribution body (7) by means of a blower (19) provided with a motor (20) The lower end of the inner tube (18) of the coaxial tube flows into the combustion air supply (5)
  • the entire fuel is separated or with the remaining part of the combustion air ( ⁇ 30 vol% of the total combustion air throughput of 100%) via a cylinder ring (21) arranged perpendicular to the longitudinal central axis (34) between the inner tube (18) and outer tube (22) of the coaxial tube Combustion zone fed The lower end of the outer tube (22) of the coaxial tube flows into the fuel feed (4).
  • This admixture of the combustion air throughput to the fuel takes place in particular to increase the fuel's momentum
  • the cylinder ring (21) is provided directly at the foot of the combustion air distribution body (7) with a row of nozzles (12).
  • This row of nozzles (12) has a large number of fuel nozzles (13) arranged around the combustion air distribution body (7) for distribution of the fuel into the combustion zone in jet directions (14) which can be set as desired in two mutually perpendicular planes crossing the longitudinal center axis (34) (see FIGS. 3a-3d)
  • the burner output was at relatively small combustion air distribution bodies (length 25-30 cm, width at the foot part 2-3 cm and at the head part 0-10 cm, with a length of the fire or combustion chamber of 80 cm) to values between 10 and 22 kW set and the air ratio varies between 1, 1 and 1, 5 This does not represent a fundamental limitation.
  • the contour of the combustion air distribution body did not glow and remained relatively cold (below 300 ° C.) in all designs according to FIG. 2 a.
  • the exhaust gas analysis showed, in particular, as the measurement data in FIGS. 4 a, 4 b, 5 a and 5 b show with an increased fuel nozzle pulse, extremely low NO x and CO emission values, which are far below the legal limit values for industrial burners and even fall short of the proposed revision of the limit values for boiler furnaces
  • a major advantage of the invention is therefore the possibility of building an energy-saving and environmentally friendly incinerator with a compact burner and combustion chamber shape, which is used for generating heat at smaller outputs up to 100 kW (such as in household appliances, wall-mounted heaters and boilers) medium outputs,> 100 kW to 1 MW (such as in heating centers, thermal power stations and biomass combustion) and also with larger outputs> 1 MW (such as in power plant furnaces and rotary kilns) is suitable.
  • the combustion chamber of such systems will be compared to the previously usual Significantly reduce the combustion space due to the better heat transfer conditions to the hot material and the short burn-out distance.
  • the new burner device is more ecological and economical than conventional firing technology
  • FIG 1b shows a schematic arrangement of several burner devices for industrial purposes in power plant technology.
  • the combustion chamber (2) has a square cross section, the burner devices shown have the same features as in FIG 1 a and are installed on the lower wall (3c), as explained above.
  • the heat is dissipated via the water pipes (23) installed in the outer wall and via the evaporator and superheater heating surfaces (24) and (25) Air preheater, which preheats the combustion air of the burner, reached in the exhaust duct, which is not shown in the schematic drawing
  • Fig. 2 a shows a schematic representation of different geometric variants of the combustion air distribution body. These can have a square, cylindrical, cone, polygon prism or pyramid shape or their contour can be ellipsoidal or hyperbolic. Further geometric designs are possible.
  • all combustion air has - Distribution body an internal cavity for the supply of the combustion air, a thin perforated or porous wall surrounding the cavity, a closed head part and an open foot part on The dimensions of the combustion air distribution body and the number and geometry of the openings on their circumference should be chosen so that they ensure a controlled combustion process around the combustion air distribution body.
  • the air delivery to the combustion area depending on the burner output according to the specific requirements of an Fe The control process is to be controlled in such a way that substochiometric combustion takes place over a larger combustion area and full burnout is only completed near the top of the combustion air distribution body. Measurements showed that different dimensions of the combustion air distribution body are required for different burner outputs. Therefore, the combustion air distribution body is for To make certain load ranges separately and to design them interchangeably, this can be done as follows, as schematically illustrated in FIG. 2b.
  • the foot part (8) of the combustion air distribution body (7) is connected to an external thread (26) and the air supply pipe (18) at the pipe outlet provided with an internal thread
  • the combustion air distribution body (7) is screwed into the air supply pipe (18)
  • the measurements have confirmed that, in order to achieve a stable, low-pollution and perfect combustion, the following data on the combustion air distribution body should be adjusted (see Fig. 1 a)
  • the length (A) of the combustion air distribution body (7) is> 40 - 85% of the combustion chamber length (B), the diameter (C) of the combustion air distribution body (7) at the foot part (8) is> 10% of the combustion chamber diameter (D), and the porosity of the combustion air distribution body is ⁇ 20%
  • FIG. 3 a shows a schematic representation of variants of the jet directions of the fuel nozzles (13), which are positioned in a row of nozzles (12) or several rows of nozzles at the foot part of the combustion air distribution body (7) and are arranged around them.
  • a row of nozzles (12) contains a large number of nozzles, the jet direction (14) of which can be changed both in the longitudinal central axis and at an angle to it.On the one hand, this allows the fuel to be distributed over different contour areas of the combustion air distribution body, which contributes to the targeted control of the mixing ratios and favors the ignition a fuel swirl is generated in the jet direction, which leads to more intensive mixing of fuel and combustion air and to the longer residence time of the fuel particles in the flame area.
  • the rows of nozzles are to be manufactured for different load ranges and should be interchangeable, this can be done, for example, as shown in FIG. 3 b.
  • the coaxial ring 21 is closed directly before the fuel enters the combustion chamber and is connected to the fuel supply by connecting channels (32) provide the combustion chamber, the channels (32) have internal threads (33) and the fuel nozzles (13) have external threads (28).
  • the fuel nozzles (13) are screwed into the connecting channels (32)
  • oblique bores (29) or an annular gap (30) with an inner swirl generator (31) can be used, as shown in FIGS. 3 c and 3 d
  • the graphs in FIGS. 4 a and 5 a show the NO x and CO emission values measured in the exhaust gas as a function of the burner output at different air ratios for the variant shown in FIG. 1 a with the conical combustion air distribution body.
  • Natural gas H was fed in as fuel by means of a single row of nozzles, the nozzles being set in such a way that every second nozzle was provided with a weak swirl. While the burner output for the relatively small pilot plant was varied between 10 and 22 kW, the air figures for that in combustion plants are The usual and interesting range from 1.2 to 1.5 has been set.
  • the NO x and CO emission values shown have been converted to 3 vol% O 2 in the exhaust gas so that a comparison with the limit values of the TA-Luft is possible
  • the decisive factor for the further reduction of the NO x emission values is the influence of the increase in momentum through the fuel nozzles, so a slight addition of air with the fuel leads to strong turbulence and a better mixture between fuel and combustion air.
  • the ignition limit is rather reached.
  • the flame becomes thinner, larger and burns in the present example with an admixture of approx. 20% Combustion air to the fuel hardly or not visible
  • Fig. 4 b shows an admixture of approx. 20% combustion air to the fuel and otherwise the same settings as in Fig. 4 a extremely low NO x emission values for all air ratios and for all examined load ranges
  • the axial and tangential setting of the fuel nozzles has a special influence on the NO x and CO formation, but depending on the combustion air distribution body used there are different optimal angular positions

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Incineration Of Waste (AREA)
EP97924865A 1996-04-20 1997-04-18 Foyer avec un dispositif de brûleur et procédé de fonctionnement d'un foyer Expired - Lifetime EP0834040B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19615761 1996-04-20
DE19615761 1996-04-20
PCT/DE1997/000817 WO1997040315A1 (fr) 1996-04-20 1997-04-18 BRULEUR ET PROCEDE DE FONCTIONNEMENT D'UN BRULEUR DESTINE A UNE COMBUSTION PAUVRE EN NOx ET EN CO

Publications (2)

Publication Number Publication Date
EP0834040A1 true EP0834040A1 (fr) 1998-04-08
EP0834040B1 EP0834040B1 (fr) 2000-08-09

Family

ID=7791926

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97924865A Expired - Lifetime EP0834040B1 (fr) 1996-04-20 1997-04-18 Foyer avec un dispositif de brûleur et procédé de fonctionnement d'un foyer

Country Status (6)

Country Link
US (1) US6419480B2 (fr)
EP (1) EP0834040B1 (fr)
AT (1) ATE195367T1 (fr)
DE (2) DE59702133D1 (fr)
ES (1) ES2151273T3 (fr)
WO (1) WO1997040315A1 (fr)

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CN108757944B (zh) * 2018-08-07 2023-12-19 深圳众诚联合能源科技有限公司 一种基于气流运动姿态调整技术的回转空预器密封装置
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CN118221362B (zh) * 2024-05-24 2024-08-02 合肥水泥研究设计院有限公司 一种窑炉燃料分配器及其使用方法

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Also Published As

Publication number Publication date
ES2151273T3 (es) 2000-12-16
EP0834040B1 (fr) 2000-08-09
WO1997040315A1 (fr) 1997-10-30
DE59702133D1 (de) 2000-09-14
US6419480B2 (en) 2002-07-16
US20010018171A1 (en) 2001-08-30
ATE195367T1 (de) 2000-08-15
DE19717721A1 (de) 1997-10-30

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