Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23D—BURNERS
  • F23D1/00—Burners for combustion of pulverulent fuel
  • F23D1/02—Vortex burners, e.g. for cyclone-type combustion apparatus
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23D—BURNERS
  • F23D2201/00—Burners adapted for particulate solid or pulverulent fuels
  • F23D2201/20—Fuel flow guiding devices

Definitions

• the invention relates to a burner and a method for the combustion of dusty fuel, in particular ⁇ dusty and ballast-rich coal.
• Burners for the combustion of dusty fuel are known, for example from the publication "Development of low-emission dust-firing systems" from VGB Kraftwerkstechnik 76 (1996), No. 5.
• Jet burners usually consist of a dust nozzle through which the dusty fuel is introduced into the combustion chamber for combustion by means of a carrier gas, which can be primary air or primary gas is and from an upper and lower air nozzle, which adjoin above and below the dust nozzle and is introduced through the secondary air into the combustion chamber.
• the respective nozzles are formed with rectangular cross sections.
• jet burners have several dust nozzles, and z was two to four dust nozzles open. In such a case, the upper and lower air nozzles lying in the vertical direction between two dust nozzles can be combined to form an intermediate air nozzle.
• the lignite When such jet burners are used to burn lignite, the lignite is usually ground in beater wheel mills, dried with hot smoke gases extracted or drawn back from the combustion chamber or the combustion chamber and conveyed to the dust nozzles of the burners by the ventilation action of the beater wheel mill.
• the secondary air emerges from the upper, lower and, if necessary, intermediate air nozzles.
• Core air pipes are usually integrated within the rectangular dust nozzle, through which a small part of the combustion air exits.
• the ignition zone of such a jet burner is generally at a certain distance from the burner outlet, specifically in the area in which there is contact between the secondary air jets and the dust jet.
• the dust jet is first heated to the ignition temperature and pyrolyzed using hot flue gas drawn in from the combustion chamber. Due to the geometrical arrangement of the dust and air nozzles, the recirculated, hot flue gas is mainly sucked in by the dust jet on the side surfaces of the rectangular dust nozzle. The dust jet cannot be heated and pyrolyzed on the upper and lower surface of the jet, since these surfaces are covered by the secondary air jets.
• the rectangular jet burner described above is a design for the majority of the lignite types available worldwide with regard to ignition stability and optimal with regard to the NOx emission level and the slagging behavior of the combustion chamber.
• lignites which have an extremely high ballast content due to a very high water and / or ash content
• a further increase in ignition stability by design measures on the burner is desirable as an alternative or in addition to the vapor separation usually used for these fuels.
• a disadvantage of the jet burner described above is that, due to the geometrical arrangement, the entire circumference of the dust jet from the dust nozzle cannot be used to draw in hot flue gases, and thus the dust jet cannot be fully heated.
• the priority for the firing operation can be to increase the reaction density on the burner, e.g. to ensure sufficient burnout in small fireboxes.
• jet burners have lower reaction densities than swirl or round burners due to the flow conditions.
• circular burners which have a central, round dust or Have primary mixture pipe and a secondary air pipe concentric to it, which surrounds the central dust pipe and forms an annular cross-section between the two pipes.
• the fuel is introduced into the combustion chamber together with primary air or primary gas and secondary air via the annular cross section of the secondary air tube.
• these round burners in most cases both the secondary air and the dust jet are swirled.
• core air tubes can also be integrated in the circular dust tube, through which a small part of the combustion air can escape into the combustion chamber.
• the geometric arrangement with the central dust tube and the concentric secondary air tube also shows disadvantageously that the dust flow only has contact with the hot flue gas of the combustion chamber through internal recirculation of the flue gas into the flame root of the burner flame, but the entire outer circumference of the dust flow has no direct contact has to the hot flue gas of the combustion chamber, so that hot flue gas from the combustion chamber can only be mixed in over the relatively cold secondary air. This prevents premature heating and pyrolysis of the dust flow.
• a coal dust burner is known from the publication "Patent Abstracts of Japan, Publication number 5801 1308 A", which provides an air supply in a central air supply pipe and provides the coal dust supply in an annular channel, which is formed by the inner air supply pipe and a surrounding, external coal dust supply pipe Due to the oblique and eccentric introduction of the abrasive or erosive coal dust flow into the burner longitudinal axis in very expensive and maintenance-intensive ceramic linings on the inner wall of the coal dust feed pipe and on the outer wall of the air feed pipe are necessary to keep the service life of the coal dust burner in reasonable areas.
• the object of the invention is now to provide a burner which is more efficient and less expensive than the prior art and which is particularly suitable for the combustion of dusty and ballast-rich coal, and to provide a method for operating such a burner.
• the primary mixture or dust jet emerging from the primary mixture or dust tube into the combustion chamber has direct contact over its entire circumference the hot smoke gases in the combustion chamber, which can be sucked in unhindered and can heat up the dust jet.
• the flow stability area located upstream of the secondary air pipe on the primary mixture flow side causes the primary mixture flow to be introduced axially into the burner, thereby achieving a uniform distribution of the solid over the cross section and a lower pressure loss in the system.
• the axial introduction of the primary mixture flow into the burner is ultimately also made possible by the secondary air being brought into the invention by means of a secondary air inlet housing arranged on the circumference of the primary mixture tube and the passage channels leading therefrom and leading into the secondary air line.
• the passage channel is designed in such a way that the secondary air flow can be introduced into the secondary air pipe tangentially, radially and with an angular range lying in between.
• This constructive measure makes it possible to control the secondary air flow by means of an aid, e.g. a swirl control device with a strong, a weakened or no swirl to feed the secondary air pipe.
• the introduction or the inflow direction of the secondary air flow into the Secondary air pipe can be regulated advantageously.
• This measure makes it possible for the secondary air flow to be introduced or introduced radially, ie without swirl or tangentially, ie with swirl, into the secondary air pipe without having to provide special devices for this purpose within the secondary air pipe.
• the introduction with a weakened swirl is also possible if the direction of introduction generated by the swirl control flap lies in a range between radial and tangential introduction.
• the twisting of the secondary air flow creates a vacuum zone at the burner outlet near the burner axis, which also transports hot flue gases from the flame towards the flame root and thus increases the ignition stability and the reaction density in the flame.
• an area is created in which the mixture between the dust jet and the secondary air achieves an ignitable dust / air concentration as well as the mixing temperature of hot smoke gases from the combustion chamber and hot smoke gases from the flame itself. If no wired secondary air is required on the combustion side or fuel-related, then this can be introduced radially into the secondary air pipe.
• the channel of the inlet housing has a substantially reduced depth as the circumferential angle increases, in order to achieve a uniform flow velocity within the inlet housing and in the outlet channels branching off therefrom. This can most conveniently be achieved by a spiral inlet housing.
• the secondary air tube or at least a part of the secondary air tube on the outlet side can advantageously be axially displaced within the primary mixture tube.
• the level of the secondary air tube outlet is advantageously on the flow medium side and, viewed with respect to the longitudinal axis of the secondary and primary mixture tube, downstream or upstream or at the same level of the primary mixture tube outlet. This arrangement allows an optimal alignment of the two Air pipes to each other are created with regard to the ignition zone and the ignition stability.
• the end wall of the passage channel facing the burner mouth is formed on the outflow side of the primary gas mixture with a displacement body in order to also prevent turbulence and deposits.
• the secondary air tube is formed on its outer periphery of the outlet end with a retaining ring or it is flared to exit into the combustion chamber.
• the ignition stability can be increased further by both measures.
• each baffle segment extending radially between the secondary air pipe and the primary mixture pipe and angularly over a partial area of the burner outlet circumference or over a partial area of the annular outlet between the secondary air pipe and the primary mixture pipe and the baffle segments being evenly spaced apart from one another on the angle
• the contact area between the primary mixture and hot flue gases is further increased and an improved mixing of the primary mixture, secondary air and flue gases is achieved. This results in increased ignition stability.
• the distance L between the burner mouth and the end wall of the secondary air inlet housing facing the burner mouth is 1.0 to 10 times the diameter d SL of the secondary air pipe in order to have a sufficient or effective rotational swirl of the secondary air at the burner mouth.
• the primary mixture tube has a conical widening at its outlet end in order to influence the ignition stability.
• An expedient embodiment of the invention has, on the side of the inner surface of the primary mixture tube opposite the primary mixture tube inlet, at least one leveling body located downstream of the primary mixture tube inlet on the fluid side for equalizing the primary mixture stream. This measure enables strands of mixture in the primary mixture tube, which form predominantly on the opposite side of the mixture inlet, to be dissolved and the mixture flow to be made more uniform.
• annular guide body is arranged on the inner circumference or the inner surface of the primary mixture tube in the area of the secondary air tube or in the area of the secondary air tube outlet, which takes up part of the annular cross section between the primary mixture tube and secondary air tube. This allows local enrichment of the primary mixture can be achieved on the inner periphery of the annular cross section and consequently more efficient mixing of the primary mixture with the secondary air.
• passage channels are also advantageous to arrange the passage channels at the same angular distance from one another and to make them the same width, i.e. that they each occupy an equally large partial area of the annular cross section in order to achieve equally large passage cross sections for the primary mixture flow.
• the burner according to the invention is expediently operated stoichiometrically, ie with a shortage of oxygen, in order to achieve a combustion of the fuel that is as low in NO x as possible and thus to provide the most environmentally friendly combustion possible.
• FIG. 1 schematically shows the front view of a jet burner according to a prior art
• FIG. 2 shows a longitudinal section through the jet burner according to section A-A of FIG. 1,
• FIG. 4 shows a longitudinal section through the round burner according to section B-B of FIG. 3,
• FIG. 5 schematically shows the cross section of a burner according to the invention in the region of the tangential or radial supply of the secondary air (section EE of FIG. 6), 6 shows a longitudinal section through the burner according to section DD of FIG. 5,
• FIG. 7 shows a longitudinal section according to section F-F of FIG. 6,
• FIG. 10 shows a partial longitudinal section through the burner according to section D-D of FIG. 5 in the region between tangential or radial secondary air supply and burner mouth, alternative embodiment,
• Fig. 1 1 shows a longitudinal section through the burner according to section D-D of Figure 5, alternative embodiment.
• Figures 1 and 2 has a jet burner according to a prior art. These burners consist of a dust nozzle 24, an under air nozzle 25 and an upper air nozzle 26, the cross sections of which are rectangular. In most cases, the entire burner consists of several dust nozzles 24, usually 2 or 3 pieces. In this case, the upper and lower air cross sections lying in the vertical direction between two dust nozzles 24 can be combined to form an intermediate air cross section.
• Lignite is predominantly ground in beater wheel mills, dried with hot flue gases sucked back from the combustion chamber or the combustion chamber 10 and, by the ventilation effect of the beater wheel mill, not shown, to the Dust nozzles 24 promoted the burner.
• a mixture of fuel dust, flue gas, water vapor and primary air therefore emerges from the dust nozzle 24 into the combustion chamber 10, which is referred to below as the primary mixture.
• the secondary air emerges from the upper, lower and intermediate air nozzles 25, 26.
• Core air tubes (not shown) through which a small part of the combustion air emerges are generally also integrated within the rectangular dust nozzle 24.
• Fig. 2 shows the longitudinal section of a jet burner with the exit of the jets into the combustion chamber 10.
• the ignition zone 18 of such a burner is usually at a certain distance from the burner outlet, in the area in which contact between the secondary air flows or -jets 19 and the dust stream or jet 20 comes.
• the dust jet 20 is first heated to the ignition temperature and pyrolyzed via hot flue gas 21 drawn in from the combustion chamber 10. Due to the geometrical arrangement of the dust nozzles 24 and air nozzles 25, 26, the recirculated, hot flue gas 21 is sucked in by the dust jet 20 mainly on the side surfaces of the rectangular dust nozzle 24 (FIG. 1).
• FIGS. 3 and 4 show a round or swirl or swirl burner according to a prior art, which has a central, round dust or primary mixture pipe 4 and a secondary air pipe 3 concentric therewith.
• both the secondary air flow 19 and the dust flow 20 are usually swirled.
• the swirl blades 12 are present in the dust tube 4 and a spiral-shaped secondary air inlet housing 28 with tangential secondary air supply is provided on the secondary air side.
• FIGS. 5 to 12 possible configurations show a burner 1 according to the invention
• FIG 5 and 12 a cross-section in the region of the pre-and introduction of secondary air into the secondary air tube
• Figures 6, '8, 10 and 1 1 each show a longitudinal section and partial longitudinal section of the Show burner 1, from which the structure of this burner can be seen.
• the burner 1 is essentially formed from a central and round secondary air tube 3, the center of which is the longitudinal axis 27, and a round primary mixture tube or dust tube 4, which concentrically surrounds the secondary air pipe 3 to form an annular cross section 9.
• the inlet-side end 6 of the primary mixture pipe 4 is connected to a supply line 17 arranged essentially perpendicular to the primary mixture pipe 4 and the inlet-side end 5 of the secondary air pipe 3 is connected to a supply line 16 via passage channels 35 and via the channel 40 of the secondary air inlet housing 28.
• the outlet ends 7, 8 of the primary mixture pipe 4 and secondary air pipe 3 open into the burner opening or burner mouth 2 of the combustion chamber wall 11.
• the secondary air pipe outlet 7 extends over the entire cross section of the secondary air pipe 3 and possibly over the conical widening 30, which is shown in FIG. 8 as a preferred embodiment of the invention.
• the primary mixture pipe outlet 8 extends over the entire cross section of the annular cross section 9 between the two pipes 3 and 4 reduced by the - if used - constriction caused by the conical widening 30 of the secondary air pipe 3 or expanded - if used - by the conical widening 48 of the Primary mixture pipe 4.
• the supply of the entire secondary air flow 19 or all air going beyond the primary air into the burner 1 takes place in the flow direction (represented by arrows in the figures) through the supply line 16, which is preferably arranged perpendicular to the longitudinal axis 27 of the burner, through the radial one Inlet housing 28 forming channel 40, through the passage channels 35 penetrating the annular cross-section 9 and via the secondary air tube inlet 5 into the secondary air tube 3.
• the end face of the inlet-side end of the secondary air tube 3 is closed according to the invention with an end wall 38 - This flows parallel to the longitudinal axis 27 and emerges from the secondary air pipe 3 into the combustion chamber 10 at the open cross section of the secondary air pipe outlet 7.
• the passage channels 35 are designed such that the secondary air flow 19 can be introduced into the secondary air pipe 3 tangentially, radially and in any desired intermediate direction.
• at least two through channels 35 are provided according to the invention - in the example according to FIGS. 5 to 12 there are three through channels 35 which channel 40 Connect the inlet housing 28 to the inner cross section of the secondary air tube 3.
• both the primary mixture pipe 4 and the secondary air pipe 3 have openings 42, 43 in the size of the cross section of the passage channel 35 for the passage of the secondary air flow 19.
• Each passageway 35 angularly occupies part of the annular cross-section 9 between the primary mixture pipe 4 and secondary air pipe 3, with each passageway 35 angularly occupying the same part of the annular cross-section 9 in a preferred embodiment.
• the cross section of the passage channels 35 is generally rectangular - with a width b and a height h.
• the passage channel 35 is designed such that, as already mentioned above, the secondary air flow 19 can be introduced into the secondary air pipe 3 either radially, tangentially or in an angular range therebetween.
• This specification can be achieved, for example, by a passage channel 35 according to FIG. 12, in which the side walls 46, 47 are designed accordingly.
• a swirl control device 34 in particular a swirl control flap, which is arranged within the passage channel 35 or at the secondary air pipe inlet 5 or at the opening 42, can be provided.
• the passage channel 35 is formed by means of the end walls 39 and 45 and the side walls 46 and 47.
• the secondary air flow 19 is introduced tangentially into the secondary air pipe 3 by means of the swirl control device 34 and thus the rotation 19 is given a rotational swirl which is maintained until it exits into the combustion chamber 10 and which is achieved in the secondary air pipe 3 without separate devices ,
• the swirl control device 34 By means of the swirl control device 34, the swirl of the secondary air flow 19 can be influenced or weakened up to the swirl-free supply when the secondary air flow 19 is introduced radially into the secondary air pipe 3.
• the rotary control device 34 of all the passage channels 35 can be operated, for example, by a central spindle adjustment device, not shown, so that exactly the same control position and thus the same secondary air quantity setting is achieved on each passage channel 35.
• the passage channels 35 are preferably evenly spaced apart from one another within the annular cross section 9, so that the passages 44 for the primary mixture stream 20 have the same cross sections with the same transverse dimensions of the passage channels 35, and a uniform distribution of the primary mixture stream 20 is achieved.
• the inlet housing 28 arranged radially outside the primary mixture pipe 4 and in the area of the passage channels 35 extends at least over part of the circumference of the pipe 4 in such a way that all existing passage channels 35 can be acted upon by secondary air.
• the inlet housing 28 can be a box-shaped housing in a simple manner, which thus forms the above-mentioned channel 40 between the tube 4 and the outer wall of the housing 28 (see FIG. 12).
• the channel 40 formed by the inlet housing 28 on the outer circumference of the tube 4 preferably has a substantially reduced depth with an increasing circumferential angle in order to have a largely uniform speed and allocation of the secondary air flow 19 to each individual through-channel 35 and further in over the circumference to achieve the secondary air pipe 3. This requirement can be achieved, inter alia, by a preferred spiral configuration of the inlet housing 28.
• the distance L between the burner mouth 2 and the end wall of the inlet housing 28 pointing towards the burner mouth 2 (essentially also corresponds to the opening limitation of the inlet opening 5 towards the burner mouth 2) preferably formed with 0.5 to 10 times the diameter d SL of the secondary air pipe 3.
• the secondary air pipe 3 or an outlet-side part 13 of the secondary air pipe 3 can be axially displaced within the primary mixture pipe 4.
• the exit plane of the outlet-side end 7 of the secondary air tube 3 or of the outlet-side part 13 can thus be brought into different positions in relation to the outlet plane of the outlet-side end 8 of the primary mixture tube 4.
• the outlet plane of the outlet-side end 7 of the secondary air pipe 3 or of the outlet-side part 13, as seen on the flow medium side, is situated by the dimension k upstream of the outlet plane of the outlet-side end 8 of the primary mixture pipe 4.
• the dimension k can be up to 0.5 times the diameter d SL of the secondary air pipe 3, ie the two ends 7, 8 on the outlet side can also be flush with one another.
• a protrusion of the secondary air tube 3, ie the outlet plane of the outlet-side end 7 of the secondary air tube 3 is, seen on the flow medium side, by the dimension k downstream of the outlet plane of the outlet-side end 8 of the primary mixture tube 4.
• the dimension k can also be up to 0.5 times the diameter d SL of the secondary air pipe 3.
• the secondary air pipe 3 can consist of two parts, a stationary part and an axially displaceable part 13, both parts being designed to overlap (FIG. 10). '
• the ignition stability can also be influenced by constructive measures at the outlet 7 of the secondary air tube 3, in that the end of the tube 3 undergoes a conical widening 30 according to FIG. 6, or by providing a retaining ring 15 on the outer circumference of the secondary air tube 3, which ring has the annular shape Cross section 9 at the primary mixture pipe outlet 8 is reduced.
• primary air or primary gas which essentially consists of primary air, flue gas and water vapor, is fed to the burner 1 together with particulate or dust-like fuel through the supply line 17 arranged in most cases perpendicular to the primary mixture pipe 4 and this mixture (Primary mixture) passes through the primary mixture pipe inlet 6 into the primary mixture pipe 4.
• the primary mixture pipe 4 Downstream of the inlet 6 and upstream of the secondary air pipe 3, the primary mixture pipe 4 contains a flow stabilization area 49, in which the deflected primary mixture flow 20 is stabilized according to the invention, ie is aligned in the axial flow direction. Seen in the direction of flow, the primary mixture pipe 4 downstream of the flow stabilization area 49 or upstream of the secondary air pipe 3 can experience an expansion of the outside diameter in order to possibly achieve essentially the same flow velocities in the circular cross section 9 as in the flow stabilization area 49. After flowing through the passages 44 and the primary mixture pipe 4 in the region of or between the secondary air passage channels 35 and in the direction parallel to the longitudinal axis 27, the primary mixture flow 20 exits the combustion chamber 10 at the outlet 8. In the passage 44 there is an increased flow velocity compared to the free circular cross-section 9, which proves to be advantageous for preventing deposits on this narrowed cross-section.
• At least one equalizing body 31 can be provided within the primary mixture tube 4, since strands, ie fuel dust accumulations, can form when the primary mixture stream 20 enters the primary mixture tube 4. This occurs in particular on the side of the primary mixture pipe 4, which is located opposite the primary mixture pipe inlet 6.
• the equalization body (s) 31 is arranged on this side of the inner surface of the primary mixture tube 4, specifically on the flow medium side downstream of the primary mixture tube inlet 6.
• the equalization body 31 can be, for example, a sheet metal body.
• annular guide body 32 which can be arranged on the inner circumference or on the inner surface of the primary mixture tube 4 in the region of the secondary air tube 3 or preferably in the region of the secondary air tube outlet 7 and which has a radial part of the annular cross section 9 between the primary mixture tube 4 and occupies the secondary air pipe 3. Local enrichment of the primary mixture 20 on the inner periphery of the annular cross section 9 can thus be achieved.
• the pressure loss in this system is advantageously reduced. Furthermore, a more uniform distribution of the dust-like fuel over the cross section is achieved.
• a swirl device can also be provided for the dust stream 20 within the primary mixture pipe 4 or directly upstream of this on the fluid side.
• This can be achieved in the form of a spiral-shaped primary mixture inlet housing 29, not shown, which is arranged on the outer circumference of the primary mixture tube 4 and is connected to the feed line 17.
• the swirling of the dust stream 20 again increases the ignition stability.
• a swirl device 14 can be provided within the primary mixture tube 4 or its annular cross section 9 for swirling the dust stream 20 (FIG. 8).
• the outlet-side end 7 of the secondary air tube 3 is alternatively formed with a conical widening 30.
• the end wall 45 is preferably formed downstream with a displacement body or spoiler 41. Like the means 36, 37, this can be designed or constructed.
• the outlet of the primary mixture tube 4 can also be designed with a conical expansion 48 with a conical expansion 30 of the secondary air tube 3 (FIG. 8).
• baffle segments 33 can be arranged at the burner outlet 2, each baffle segment 33 extending radially between the secondary air tube 3 and the primary mixture tube 4 and angularly over a partial region of the annular outlet between the two tubes 3, 4, and the baffle segments 33 being evenly spaced from one another , As a result, the contact area between the emerging primary mixture stream 20 and the sucked-in hot flue gases is further increased and an improved mixing of the primary mixture 20, secondary air 19 and flue gases 21 is achieved. This results in increased ignition stability.
• the stowage segment 33 can be, for example, a correspondingly manufactured sheet metal segment.
• a vacuum zone 23 is created at the burner outlet 2 in the immediate vicinity of the longitudinal axis 27, which additionally transports hot flue gases 22 from the flame in the direction of the flame root and thus increases the ignition stability and the reaction density in the flame.
• the respective secondary air and primary mixture pipes 3, 4 are usually arranged at a distance from one another in the vertical direction. This measure increases the reaction density in the ignition zone 18 and thus the ignition stability.
• the combination of several burners 1 can also have structural reasons, for example in order not to make the firebox 10 larger than necessary.
• the longitudinal axis 27 of the burner 1 can be horizontal or, as shown in FIG. 11, can be inclined to the horizontal by an angle, which is preferably 0 to 20 °, in the discharge direction or to the burner outlet 2. Due to the slightly inclined downward direction of the secondary air and primary mixture pipes 3, 4, the residence time of the fuel in the combustion chamber 10 can be increased and thus the burnout can be improved.
• the burner 1 according to the invention can be used, for example, for direct (ie the fuel comes directly from the mill) lignite dust furnaces with upstream coal mills, in particular beater wheel or bowl mills (not shown) and for indirect (ie the fuel is already ground and is, for example, from a fuel silo by means of pneumatic Conveyors) dry lignite dust furnaces (not shown) are used.
• direct ie the fuel comes directly from the mill
• indirect ie the fuel is already ground and is, for example, from a fuel silo by means of pneumatic Conveyors dry lignite dust furnaces (not shown) are used.
• the differences lie only in the amount and in the composition of the gas mixture present in the dust jet 20 in addition to the fuel dust.
• the burner 1 according to the invention is operated sub-stoichiometrically, ie with a shortage of oxygen, in order to achieve a combustion of the fuel used which is as low in NO x as possible and thus to provide the most environmentally friendly combustion possible.
• the air required for further burning out of the fuel is added to the furnace, for example in the form of upper air, in the further course of the combustion within the combustion chamber 10.

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• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Fluidized-Bed Combustion And Resonant Combustion (AREA)

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• 2002
  • 2002-01-17 WO PCT/DE2002/000116 patent/WO2002057689A1/fr active IP Right Grant
  • 2002-01-17 PL PL363327A patent/PL199944B1/pl unknown
  • 2002-01-17 EP EP02704591A patent/EP1352197B1/fr not_active Expired - Lifetime
  • 2002-01-17 AU AU2002238385A patent/AU2002238385B2/en not_active Ceased
  • 2002-01-17 AT AT02704591T patent/ATE365891T1/de not_active IP Right Cessation
  • 2002-01-17 DE DE2002101558 patent/DE10201558A1/de not_active Withdrawn
  • 2002-01-17 DE DE50210375T patent/DE50210375D1/de not_active Expired - Lifetime
• 2003
  • 2003-07-29 BG BG108040A patent/BG65334B1/bg unknown

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