EP3717832B1 - Doppelbrennstoff-brenneranordnung und verfahren zum betrieb einer doppelbrennstoff-brenneranordnung - Google Patents

Doppelbrennstoff-brenneranordnung und verfahren zum betrieb einer doppelbrennstoff-brenneranordnung Download PDF

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Publication number
EP3717832B1
EP3717832B1 EP17808415.8A EP17808415A EP3717832B1 EP 3717832 B1 EP3717832 B1 EP 3717832B1 EP 17808415 A EP17808415 A EP 17808415A EP 3717832 B1 EP3717832 B1 EP 3717832B1
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EP
European Patent Office
Prior art keywords
flow channel
fuel
damper
swirl
burner assembly
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EP17808415.8A
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English (en)
French (fr)
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EP3717832A1 (de
Inventor
Odd Ivar LINDLØV
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Waertsilae Moss As
Wartsila Moss AS
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Waertsilae Moss As
Wartsila Moss AS
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Publication of EP3717832A1 publication Critical patent/EP3717832A1/de
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Classifications

    • 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
    • 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
    • F23C7/004—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion using vanes
    • 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
    • F23C7/004—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion using vanes
    • F23C7/006—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion using vanes adjustable
    • 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
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • 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
    • F23R—GENERATING COMBUSTION PRODUCTS OF HIGH PRESSURE OR HIGH VELOCITY, e.g. GAS-TURBINE COMBUSTION CHAMBERS
    • F23R3/00—Continuous combustion chambers using liquid or gaseous fuel
    • F23R3/02—Continuous combustion chambers using liquid or gaseous fuel characterised by the air-flow or gas-flow configuration
    • F23R3/04—Air inlet arrangements
    • F23R3/10—Air inlet arrangements for primary air
    • F23R3/12—Air inlet arrangements for primary air inducing a vortex
    • F23R3/14—Air inlet arrangements for primary air inducing a vortex by using swirl vanes
    • 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
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2201/00—Staged combustion
    • F23C2201/30—Staged fuel 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
    • F23C2201/30—Staged fuel supply
    • F23C2201/301—Staged fuel supply with different fuels in stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2204/00—Burners adapted for simultaneous or alternative combustion having more than one fuel supply
    • F23D2204/10—Burners adapted for simultaneous or alternative combustion having more than one fuel supply gaseous and liquid fuel

Definitions

  • the present invention relates to a dual fuel burner assembly according to the preamble of claim 1.
  • the invention relates also method of operating to a dual fuel burner assembly.
  • NOx nitrogen, or NOx
  • NO2 nitrogen dioxide
  • nitric oxide an understanding of how NO is generated is important.
  • the fuel NO mechanism prompt NO mechanisms; and the "thermal NO”.
  • the fuel to be combusted can be premixed to the combustion air or it can be introduced into the air immediately prior to combustion.
  • Swirling flows have been used to stabilize combustion in a variety of burners, both premixed and non-premixed. Swirl in these burners is generally created either by generating tangential flow motion in a cylindrical chamber, as in cyclone combustion chambers, or swirling a co-axial air flow. In both cases, the function of the swirl is to create a toroidal recirculation zone.
  • US patent 5879148 discloses a mechanical swirler for generating diverging flow in lean premixed burners.
  • the swirler includes a central passage with an entrance for accepting a feed gas, a flow balancing insert that introduces additional pressure drop beyond that occurring in the central passage in the absence of the flow balancing insert, and an exit aligned to direct the feed gas into a combustor.
  • the swirler also has an annular passage about the central passage and including one or more vanes oriented to impart angular momentum to feed gas exiting the annular passage.
  • the diverging flow generated by the swirler stabilizes lean combustion thus allowing for lower production of pollutants, particularly oxides of nitrogen.
  • This kind of a burner needs to have the fuel and oxidizer mixed prior to burner entry (i.e. entry of vane swirler).
  • the mixing zone design is critical in such respect as it determines the flame profile and turn-down ratio i.e. the ratio of the maximum capacity to minimum capacity.
  • US5240410 discloses a structure of a burner which can be fuelled with gas fuel or oil fuel.
  • the main features includes: a specially designed swirl generator; an annular hollow gas gun; an oil gun received in the gas gun where the gas jets of the gas gun and the oil jets of the oil gun have a predetermined angle with respect to the centerline.
  • a swirling air flow can be generated with a low pressure drop and low turbulences, which is beneficial to flame stability, reducing flame temperature, and delaying the mixing of air and fuel, thus inhibiting the formation of NOx.
  • Staging air and flue gas recirculation are available for further reduction of nitrogen oxides.
  • the gas gun and the oil gun are detachable and their positions are adjustable, whereby an operating person can adjust the fuel supply.
  • An object of the invention is to provide a dual fuel burner in which the NO emissions can be maintained considerable low during operating the burner either by gaseous or liquid fuel.
  • a dual fuel burner assembly comprises a duct part arranged into the burner, a combustion air inlet opening in a first end of the duct part, an outlet at the second end of the duct part and a second fuel inlet and a first fuel inlet.
  • the duct part is provided with a swirl section between the air inlet and the outlet of the burner assembly, and the swirl section comprises an annular outer flow channel and a central flow channel radially enclosed by the outer flow channel, and the annular flow channel is provided with vanes arranged to provide a tangential component to a gas flowing through the annular flow channel when in use.
  • the central flow channel is provided with a damper configured to adjust flow resistance of the central flow channel, and that the first fuel inlet is arranged coaxially with annular flow channel of the swirl section in the vicinity of the outlet of the burner.
  • the burner can be set to operation as a dual fuel burner for combusting gaseous fuel and liquid fuel alternatively.
  • the damper in the central flow channel comprises a first screen member and a second screen member arranged consecutively into the central flow channel, which screen members are provided with openings which can be aligned or at least partially misaligned with each other depending on the mutual rotational positions of the first screen member and the second screen member.
  • the damper in the central flow channel comprises a first screen member provided with openings and a second screen member provided with openings, arranged consecutively into the central flow channel, and that the screen members are arranged movable in respect to each other such that their mutual axial distance is arranged adjustable.
  • the damper in the central flow channel is a multi-plate butterfly damper.
  • the damper in the central flow channel is a vane damper provided with multiple radial vanes.
  • the first fuel inlet comprises a feed pipe arranged coaxially with annularflow channel of the swirl section which feed pipe extends longitudinally through the duct part, into which feed pipe the first fuel inlet is arranged.
  • first fuel inlet comprises a central feed pipe arranged rotatably in respect to its longitudinal axis and the first screen member is fixed to a body of the swirl section and the second screen member is fixed to the feed pipe such the second screen member is rotatably by the central feed pipe in respect to the first screen member.
  • the burner comprises a mixing part arranged between the air inlet and the swirl section arranged for mixing the second fuel and combustion air prior to introduction into the swirl section.
  • Invention provides several advantages. By means of the dual fuel burner according to the invention it is possible to combust either gaseous fuel or liquid fuel alternatively which simultaneously provide adequately low CO and NOx emissions with both fuels.
  • the burner assembly is simple and technically straight forward and it is provides reliable operation and long service life.
  • Figure 1 depicts schematically a dual fuel burner assembly 10 according to an embodiment of the invention which is configured to combust alternatively liquid fuel, such as a light fuel oil, and gaseous fuel, such as LNG, LPG, etc.
  • Figure 2 depicts schematically a dual fuel burner assembly 10 according to another embodiment of the invention which is configured to combust alternatively liquid fuel, such as a light fuel oil, and gaseous fuel, such as LNG, LPG, etc.
  • the dual fuel burner assembly 10 is referred to as a burner 10 for sake of simplicity.
  • the burner 10 comprises a duct part 12 via which the air needed for combustion of fuel is introduced into a combustion section 16 functionally attached to the burner 10.
  • the combustion section 16 is shown here only indicatively since it may be an integral part of the burner or it at may structurally belong to a combustor, such as a refractory lining, where the burner is attached to.
  • the combustion section 16 is also an outlet of the duct part 12.
  • the duct part 12 is generally of circular cross section having a longitudinal center axis 14. In the figures 1 and 2 the duct part is substantially of constant diameter, but that is not essential to the operation of the burner.
  • the duct part 12 comprises an inlet section or a first end of the duct part 12.1 and a head section 12.2 via which air or a mixture of the air and gaseous fuel is fed to and through the burner 10 depending on the mode of operation.
  • the inlet section 12.1 is primarily an air inlet 15.
  • the burner 10 is a dual fuel burner and therefore it comprises means for introducing a first and a second fuel into the burner 10.
  • the means for introducing the first fuel comprises a first fuel inlet 19 for liquid fuel and the means for introducing the second fuel comprises the inlet 15 of the inlet section 12.1, which is a common inlet for the combustion air and the fuel i.e. the second fuel is gaseous fuel and it has been admitted into the air prior to introduction of the mixture to the burner 10.
  • the burner 10 is provided also with a second fuel inlet 17 for introducing the second fuel, which is gaseous fuel.
  • the first inlet 15 serves for introduction of the air only, and the burner is provided with a separate gas admission valve, i.e. a second fuel inlet 17 in connection with the inlet section 12.1 for introducing the second fuel into the combustion air.
  • the duct part 12 comprises a transition and mixing part 18 by means of which the change of the angle between the inlet section 12.1 and the head section 12.2 is accomplished i.e. the change of direction of the sections and simultaneously the mixing of the gaseous fuel into the combustion air is finalized.
  • the mixing of the second fuel and air may be realized by any feasible manner, other than shown here, or in addition to the mixing part 18 shown in the figures 1 and 2 .
  • the angle need not to be exactly a right angle, but the angle of more than 45 degrees would suffice.
  • the transition part 18 comprises a set of guide vanes 20 which facilitates smooth change of flow direction of the air.
  • the guide vanes 20 has their leading edge in the direction of the first section 14.1 of the longitudinal center axis 14 and their trailing edge in the direction of the second section 14.2 of the longitudinal center axis 14.
  • the set of guide vanes 20 forms a grid which covers the whole face area of the duct part.
  • the first fuel inlet 19 is arranged at an end of a feed pipe 22, which is arranged into the head section 12.12 of burner 10. More particularly, the feed pipe 22 is mainly comprised of an elongated tube 23 arranged coaxially with the longitudinal center axis 14.1 of the burner 10 and with the annular flow channel of the swirl section.
  • the feed pipe 22 extends longitudinally through the head section 12.2 of the duct part 12 and further through a wall 12.1' of the inlet section 12.1.
  • the duct part 12 comprises a lead through and a support sleeve 24 to facilitate rotatable support of the body part 23 to the wall 12.1'.
  • the burner 10 is provided with a swirl section 30 arranged to the duct part 12, more particularly to the head section 12.2 of the duct part.
  • the swirl section 30 is arranged between the air inlet 15 and the outlet 16 of the burner 10.
  • the mixing part 18 is arranged between the air inlet 15 and the swirl section 30 for mixing the second fuel and combustion air prior to introduction into the swirl section 30.
  • the swirl section 30 comprises an annular outer flow channel 32 and a central flow channel 34 which is enclosed by the annular flow channel 32.
  • the outer flow channel 32 and the central flow channel 32 are coaxial with the body part 23 of the feed pipe 22.
  • the central flow channel 34 is formed inside the cylindrical intermediate wall 36.
  • the annular flow channel is provided with vanes 38 which are configured to provide a tangential component, i.e. a swirl, to the gas flowing through the annular flow channel, when in use as a burner.
  • the central flow channel 34 has a length in the direction of the center axis 14.
  • the central flow channel 34 is provided with a flow damper 40 which is configured to adjust gas flow resistance of the central flow channel.
  • the damper 40 is usually located at the inlet or outlet of the central flow channel 34, but it can be also located at any axial position of the channel 34 as long as it provides a desired damping effect.
  • the first fuel inlet 19 is arranged coaxially with the annular flow channel 38 of the swirl section 30 in the vicinity of the outlet 16 of the burner.
  • the damper 40 is configured to control the flow of combustion air (or the mixture of the air and the second fuel) between the central flow channel 34 and the annular flow channel 32 depending on the prevailing mode of operation of the burner 10.
  • the damper 40 together with the means for introducing first and second fuel into the burner 15,17,19 and the swirl section provide a contribution to operate the burner assembly alternatively in two different manners.
  • the swirl section splits the reactants present in the combustion process i.e. the mixture of gaseous fuel and oxidizer (air) in two channels by means of which the unswirled flow is taken place in the central channel which prevents vortex breakdown i.e. minimizes formation of a recirculation zone in the combustion process and the vanes induce swirling motion in the annulus.
  • the damper controls the unswirled and swirled flow division and the interaction of the flow split, i.e. unswirled and swirled, forms a divergent flow field upon burner 10.
  • the first fuel which is liquid fuel
  • the burner 10 is set for the operation by closing the damper 40 in the central flow channel 34.
  • this mode of operation it is refrained from the introduction of the second fuel 17 and the combustion air is led solely through the annular flow channel 32.
  • the first fuel is introduced coaxially with the annular flow channel into the swirl of combustion air and is combusted. Since practically all the combustion air is led through the annular flow channel 32 a strong swirl motion is generated.
  • the strong swirl stabilizes the flame at the outlet 16 i.e. the combustion section, which is conical of its form.
  • the flow of the air and combustion gases at the combustion section form an internal recirculation zone, which may also be referred to as a toroidal vortex core, which internal recirculation zone provides turbulent mixing of oxidizer and air.
  • This ensures a low CO content in the flue gas.
  • NOx formation can be reduced to required level, say below 10 ppm.
  • Other optional way to reduce NOx emissions are using water injection into the flame which reduces the peak temperatures and thus formation of so called thermal NOx. Also selective catalytic reduction methods are usable for the purpose.
  • the burner 10 is operated by combusting the second fuel which is gaseous fuel.
  • the damper 40 in the central flow channel is maintained open, which cause the combustion air to flow through both the central flow channel 34 and the annular flow channel 32.
  • the second fuel which is in gaseous form, is introduced into the combustion air upstream the swirl section 30 of the duct part 12 and premixed with the air prior to combustion. In this mode of operation it is refrained from the introduction of the first fuel.
  • the damper 40 is at a position which results in that a first portion of the fuel-air mixture is led through the central flow channel and a second portion of the fuel-air mixture through the annular flow channel and only the second portion is subjected into tangential swirl prior to combustion of the second fuel. Therefore the swirl is only provided to the first portion and therefore only a moderate swirl rate is generated.
  • gaseous fuel such as methane
  • the second mode of operation proves very low ( ⁇ 10 ppm) CO and NOx emissions practically without a need for any additional emission reduction means.
  • the swirl section 30 itself has a great deal of influence on the operation of the burner 10.
  • the swirl section 30 needs to serve both the first mode of operation and the second mode of operation.
  • the damper 40 i.e. the position of the damper rules the gas flow rate flowing through the annular outer flow channel 32, which effects on the swirl rate generated into the flame. This way the vanes 38 can be designed to be usable for both of the operational modes.
  • the damper 40 in the central flow channel 34 of the swirl section is configured to open or close or control the flow resistance of the flow path through the central flow channel 34.
  • the damper 40 comprises a first screen member 41 and a second screen member 42.
  • the screen members 41, 42 are arranged consecutively in the direction of the center axis 14 into the central flow channel 34 substantially face to face to each other.
  • the screen members 41, 42 are provided with openings 44, which can be aligned or misaligned depending on the mutual rotational positions of the first screen member and the second screen member.
  • the openings 43 through the plate are at equal positions, which is not however essential.
  • the screen member 41,42 are positioned in the figures 1 and 2 such that the openings 43 are aligned with each other and the damper 40 is therefore open.
  • the damper may be comprised of more than two screen members with suitable openings.
  • the central feed pipe 22 of the first fuel inlet 19 is arranged rotatably in respect to its longitudinal axis. Since the feed pipe 22 extends out from the head section 12.2 of the burner 10 it can be rotated by applying torque to the portion outside the burner.
  • the feed pipe 22 may be provided with a mechanical actuator for rotating it suitably.
  • the first screen member is releasably fixed to a body of the swirl section 30, more particularly to the intermediate wall 36 and the second screen member is releasably fixed to the feed pipe 22 such the second screen member 42 is rotatably by means of the central feed pipe 22. Thus if the feed pipe 22 is rotated the second screen member 42 rotates respectively.
  • a so-called swirl number, S is the primary design parameter
  • the burner assembly according to the invention is dimensioned so that the swirl number S is between 0,40 and 0,55.
  • the vane angle is between 30° - 42° when low hydrogen or hydrocarbon fuel, such as methane is used. If the fuel is hydrogen rich, such as pure hydrogen, the vane angle is advantageously between 30° - 35°. This results in stable and reliable operation. It has also been found that the ratio R is advantageously 0,5 - 0,7.
  • Figure 3 discloses two different embodiments of the swirl section 30 and the damper 40 shown from the direction II as is depicted by the arrow in the figure 1 .
  • the first screen member is shown by a solid line and the second screen member 42 by a dotted line.
  • the openings 43 in the screen members 41,42 in the figure 2a are non-circular indicating that the actual form of the opening may be selected to be of various forms.
  • the damper 40 in the figure 2a is such that it can be totally closed i.e. the openings in the first one of the screen members can be rotated to be between openings in the second one of the screen members.
  • the openings 43 in the screen members 41,42 in the figure 2b are circular.
  • the damper 40 in the figure 2a is such that it cannot be totally closed i.e. the amount, size and or positioning of the openings in the first one of the screen members is such that there are, independently from the rotationally position of the first screen member, always openings which are at least partially overlapping with the openings in the second one of the screen members.
  • the damper in the 2b can only adjust the flow resistance of the damper but not close it totally.
  • FIG 4 shows an embodiment of the invention in which the damper 40 in the central flow channel 34 comprises a first screen member 41 provided with openings 43 and a second screen member 42 provided with openings 43.
  • the screens may be for example substantially similar to those discussed above, but the control of the operation of the damper is different.
  • the screen members are arranged consecutively into the central flow channel 34, and the flow resistance of the central flow channel 34 is controllable so that the screen members 41, 42 are arranged movable in respect to each other such that their mutual axial distance is arranged adjustable.
  • the screen members 41, 42 are provided with openings 43 which are axially misaligned with each other.
  • FIG. 5 shows various embodiments of the swirl section 30 according to the invention.
  • Figure 5a illustrates an embodiment where the damper 40 in the central flow channel is a multi-plate butterfly damper in which more than one damper plates 40' are arranged rotatably in respect to its central axis 39'. The damper plates are supported by shaft which can be rotated with suitable actuators (not shown).
  • Figure 5b illustrates another embodiment where the damper 40 in the central flow channel is a vane damper provided with multiple radial vanes 40" are arranged rotatably in respect to its radially extending axis 39'.
  • the damper plates i.e. the radial vanes are supported by suitable shafts, which in turn can be rotated with suitable actuators, which are not shown here.

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

Claims (11)

  1. Dualbrennstoffbrenneranordnung (10), umfassend einen Kanalteil (12) zum Einführen von Verbrennungsluft, einen Einlass (15) des Kanalteils (12) an seinem ersten Ende, einen Auslass (16) des Kanalteils an seinem zweiten Ende und Mittel zum Einführen von einem ersten und einem zweiten Brennstoff in den Brenner (15, 17, 19), wobei der Kanalteil (12) mit einem Drallabschnitt (30) zwischen dem Einlass (15) und dem Auslass (16) versehen ist und der Drallabschnitt (30) des Kanalteils (12) einen ringförmigen äußeren Strömungskanal (32) umfasst, der mit Leitblechen (38) versehen ist, die derart angeordnet sind, dass sie ein Gas, das durch den ringförmigen Strömungskanal strömt, im Betrieb mit einer tangentialen Komponente versehen, und die Mittel zum Einführen von Brennstoff in den Brenner (15, 17, 19) einen ersten Brennstoffeinlass (19) umfassen, der zu dem ringförmigen Strömungskanal (32) des Drallabschnitts in der Nähe des Auslasses (16) des Brenners koaxial angeordnet ist, dadurch gekennzeichnet, dass der Drallabschnitt des Kanalteils zum Einführen von Verbrennungsluft einen zentralen Strömungskanal (34) umfasst, der von dem äußeren Strömungskanal (32) radial umschlossen ist, und der zentrale Strömungskanal (34) des Kanalteils (12) mit einer Klappe (40) versehen ist, die konfiguriert ist, den Strömungswiderstand des zentralen Strömungskanals (34) anzupassen.
  2. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass die Klappe (40) in dem zentralen Strömungskanal (34) ein erstes Siebelement (41) und ein zweites Siebelement (42) umfasst, die in dem zentralen Strömungskanal nacheinander angeordnet sind, wobei die Siebelemente (41, 42) mit Öffnungen (43) versehen sind, die abhängig von den gegenseitigen Drehpositionen des ersten Siebelements (41) und des zweiten Siebelements (42) zueinander ausgerichtet oder mindestens teilweise unausgerichtet sein können.
  3. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass der Dämpfer (40) in dem zentralen Strömungskanal (34) ein mit Öffnungen (43) versehenes erstes Siebelement (41) und ein mit Öffnungen (43) versehenes zweites Siebelement (42) umfasst, die in dem zentralen Strömungskanal (34) nacheinander angeordnet sind, und dass die Siebelemente (41, 42) in Bezug zueinander beweglich angeordnet sind, sodass ihr gegenseitiger axialer Abstand anpassbar angeordnet ist.
  4. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass die Klappe (40) in dem zentralen Strömungskanal eine Mehrplattendrosselklappe (40') ist.
  5. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass die Klappe (40) in dem zentralen Strömungskanal eine Leitblechklappe ist, die mit mehreren radialen Leitblechen (40") versehen ist.
  6. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass der erste Brennstoffeinlass (19) ein zu dem ringförmigen Strömungskanal (32) des Drallabschnitts koaxial angeordnetes Zuführungsrohr (22) umfasst, wobei sich das Zuführungsrohr (22) in Längsrichtung durch den Kanalteil (12) erstreckt und in das Zuführungsrohr hinein der erste Brennstoffeinlass (19) angeordnet ist.
  7. Dualbrennstoffbrenneranordnung nach Anspruch 6, dadurch gekennzeichnet, dass der erste Brennstoffeinlass (19) ein zentrales Zuführungsrohr (22) umfasst, das in Bezug auf seine Längsachse (14) drehbar angeordnet ist, und dass das erste Siebelement (41) an einem Körper des Drallabschnitts (30) befestigt ist und das zweite Siebelement (42) an dem Zuführungsrohr (22) befestigt ist, sodass das zweite Siebelement (42) mittels des zentralen Zuführungsrohrs in Bezug auf das erste Siebelement (41) drehbar ist.
  8. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass der Brenner einen zwischen dem Einlass (15) und dem Drallabschnitt (30) angeordneten Mischteil (18) umfasst, der zum Mischen von einem zweiten Brennstoff und Verbrennungsluft vor der Einführung in den Drallabschnitt (30) ausgeführt ist.
  9. Dualbrennstoffbrenneranordnung nach Anspruch 1, dadurch gekennzeichnet, dass die Brenneranordnung (10) derart dimensioniert ist, dass eine Drallzahl (S), die definiert ist durch die Funktion S = 2 3 tan   α 1 − R 3 1 − R 2 + m 2 1 R 2 − 1 2 R 2
    Figure imgb0016
    wobei
    α = Leitblechwinkel am hinteren Ende in Bezug auf die Längsachse (°) m = m c / m S
    Figure imgb0017
    mc = Massendurchsatz durch den zentralen Strömungskanal
    ms = Massendurchsatz durch den ringförmigen Strömungskanal
    R = R b / R B
    Figure imgb0018
    RB = Brennerkanalteilradius
    Rb = zentraler Strömungskanalradius,
    zwischen 0,4 und 0,55 liegt, wenn der Leitblechwinkel zwischen 30° und 42° liegt und das Verhältnis R 0,5 bis 0,7 beträgt.
  10. Verfahren zum Betreiben einer Dualbrennstoffbrenneranordnung (10) nach Anspruch 1 durch abwechselndes Verbrennen eines ersten Brennstoffs und eines zweiten Brennstoffs, gekennzeichnet durch Verbrennen des zweiten Brennstoffs durch Aufrechterhalten der Klappe (40) in einer ersten offenen Position in dem zentralen Strömungskanal, Einleiten des zweiten Brennstoffs in die Verbrennungsluft zuströmseitig des Drallabschnitts (30) des Kanalteils, während von der Einleitung des ersten Brennstoffs abgesehen wird, und Leiten des ersten Teils des Brennstoff-Luft-Gemischs durch den zentralen Strömungskanal (34) und eines zweiten Teils des Brennstoff-Luft-Gemischs durch den ringförmigen Strömungskanal (32) und daher Unterwerfen des zweiten Teils gegenüber einer tangentialen Verwirbelung vor der Verbrennung des zweiten Brennstoffs, und durch Verbrennen des ersten Brennstoffs, indem die Klappe (40) in dem zentralen Strömungskanal in einer zweiten offenen Position aufrechterhalten wird oder indem die Klappe in dem zentralen Strömungskanal geschlossen wird, während von der Einleitung des zweiten Brennstoffs abgesehen wird, und Leiten der Verbrennungsluft durch den ringförmigen Strömungskanal und Unterwerfen der Verbrennungsluft gegenüber einer tangentialen Verwirbelung und Einleiten des ersten Brennstoffs koaxial mit dem ringförmigen Strömungskanal (32).
  11. Verfahren zum Betreiben einer Dualbrennstoffbrenneranordnung nach Anspruch 10, dadurch gekennzeichnet, dass während der Verbrennung des zweiten Brennstoffs die Klappe derart angepasst wird, dass eine Drallzahl (S), die definiert ist durch die Funktion S = 2 3 tan   α 1 − R 3 1 − R 2 + m 2 1 R 2 − 1 2 R 2
    Figure imgb0019
    wobei
    α = Leitblechwinkel am hinteren Ende in Bezug auf die Längsachse (°) m = m c / m S
    Figure imgb0020
    mc = Massendurchsatz durch den zentralen Strömungskanal
    ms = Massendurchsatz durch den ringförmigen Strömungskanal
    R = R b / R B
    Figure imgb0021
    RB = Brennerkanalteilradius
    Rb = zentraler Strömungskanalradius,
    zwischen 0,4 und 0,55 liegt, wenn der Leitblechwinkel zwischen 30° und 42° liegt und das Verhältnis R 0,5 bis 0,7 beträgt.
EP17808415.8A 2017-11-29 2017-11-29 Doppelbrennstoff-brenneranordnung und verfahren zum betrieb einer doppelbrennstoff-brenneranordnung Active EP3717832B1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4206712A (en) * 1978-06-29 1980-06-10 Foster Wheeler Energy Corporation Fuel-staging coal burner
IT1133435B (it) * 1980-06-06 1986-07-09 Italimpianti Bruciatore a volta radiante
US5269678A (en) * 1990-09-07 1993-12-14 Koch Engineering Company, Inc. Methods and apparatus for burning fuel with low NOx formation
GB2262981B (en) 1991-12-30 1995-08-09 Ind Tech Res Inst Dual fuel low nox burner
DE4217879A1 (de) * 1992-05-29 1993-12-02 Babcock Energie Umwelt Brenner für staubförmigen Brennstoff
US5879148A (en) 1993-03-19 1999-03-09 The Regents Of The University Of California Mechanical swirler for a low-NOx, weak-swirl burner
DE102014105166B3 (de) * 2014-03-12 2015-08-06 Max Weishaupt Gmbh Drallerzeuger für einen Brenner sowie damit versehene Mischeinrichtung und damit versehener Brenner

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