EP2587148B1 - Chambre de combustion secondaire avec injection d'air secondaire - Google Patents

Chambre de combustion secondaire avec injection d'air secondaire Download PDF

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Publication number
EP2587148B1
EP2587148B1 EP12188466.2A EP12188466A EP2587148B1 EP 2587148 B1 EP2587148 B1 EP 2587148B1 EP 12188466 A EP12188466 A EP 12188466A EP 2587148 B1 EP2587148 B1 EP 2587148B1
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EP
European Patent Office
Prior art keywords
secondary air
flow
combustion chamber
air nozzles
duct
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EP12188466.2A
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German (de)
English (en)
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EP2587148A2 (fr
EP2587148A3 (fr
Inventor
Joerg Jockel
Carsten Rein
Damian Both
Paulo Jorge Ferreira Goncalves
Marcel Georg
Jan Klosok
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Robert Bosch GmbH
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Robert Bosch GmbH
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Priority to PL12188466T priority Critical patent/PL2587148T3/pl
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Publication of EP2587148A3 publication Critical patent/EP2587148A3/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L9/00—Passages or apertures for delivering secondary air for completing combustion of fuel 
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/08—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having supplementary heating
    • F23G5/14—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having supplementary heating including secondary combustion
    • F23G5/16—Incineration of waste; Incinerator constructions; Details, accessories or control therefor having supplementary heating including secondary combustion in a separate combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C3/00—Combustion apparatus characterised by the shape of the combustion chamber
    • F23C3/006—Combustion apparatus characterised by the shape of the combustion chamber the chamber being arranged for cyclonic combustion
    • 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
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G5/00—Incineration of waste; Incinerator constructions; Details, accessories or control therefor
    • F23G5/32—Incineration of waste; Incinerator constructions; Details, accessories or control therefor the waste being subjected to a whirling movement, e.g. cyclonic incinerators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G7/00—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals
    • F23G7/10—Incinerators or other apparatus for consuming industrial waste, e.g. chemicals of field or garden waste or biomasses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23G—CREMATION FURNACES; CONSUMING WASTE PRODUCTS BY COMBUSTION
    • F23G2202/00—Combustion
    • F23G2202/10—Combustion in two or more stages
    • F23G2202/103—Combustion in two or more stages in separate chambers

Definitions

  • the invention relates to secondary combustion chamber according to the preamble of claim 1 and a method for operating a secondary combustion chamber according to claim 9.
  • Secondary combustion chambers serve for the afterburning of a combustion gas stream, which is produced by combustion in a primary combustion chamber.
  • Biomass combustion devices therefore usually have a primary combustion chamber and a secondary combustion chamber.
  • the primary combustion chamber is also called filling space during log burning.
  • biomass z.
  • a thermochemical conversion of the biomass into the essential combustion products CO 2 and H 2 O takes place in three combustion phases with increasing degree of oxidation.
  • the biomass is heated and dried.
  • Especially in a combustion start and a stop of the combustion are released in the biomass combustion very many inorganic particles, such as K 2 O, CaO, K 2 SO 4 , K 2 CO 3 .
  • secondary combustion chambers are used to purify the combustion gas flow in order to carry out a fourth combustion phase.
  • the emerging from the primary combustion hot combustion gas flow is introduced for this purpose in the secondary combustion chamber.
  • the secondary combustion chamber Secondary air supplied to nachverbines the combustion gas flow and so to reduce the number of particles in the combustion gas stream. Ignition is usually not necessary because the combustion gas flow is so hot that it self-ignites when oxygen is supplied. In order to achieve good afterburning, it is necessary to mix the air and thus the oxygen well with the combustion gas flow, because only then can the particles oxidize.
  • the prior art provides tubular secondary combustion chambers, in which the secondary air is introduced tangentially.
  • the combustion gas stream is introduced axially into the secondary combustion chamber. Due to the tangential introduction of the secondary air creates a gas vortex in the secondary combustion chamber, which is why such secondary combustion chambers are also referred to as cyclone combustion chambers.
  • This gas vortex is intended to mix the combustion gas stream with the secondary air.
  • the disadvantage is that, inter alia, forms an axial core flow in the center of the vortex, in which no secondary air passes. The proportion of the combustion gas flow in the core flow is thus not post-combusted and the unburned particles pollute the environment.
  • the cyclone combustion chamber is quite bulky, to complete the secondary combustion can complete.
  • the secondary combustion chamber has a flow channel.
  • the combustion gas is passed from the primary chamber coming into another combustion chamber.
  • the secondary air is introduced tangentially and transversely to the combustion gas flow in this flow channel, the latter being cylindrical.
  • the GB 2199929 A discloses an afterburner for exhaust gases having means for causing a helical movement of the exhaust gases within the afterburner chamber.
  • a pre-combustion chamber arranged upstream of the after-combustion chamber serves to mix contaminated exhaust gases with air.
  • the pre-combustion chamber has a triangular cross-section, the air flowing through a series of parallel air nozzles along a first edge of the triangular preburn and the exhaust gases through a series of parallel exhaust nozzles along a second edge not parallel to each other in the pre-combustion chamber, while the Air-exhaust gas mixture flows out through a series of parallel mixture nozzles along a third edge of the pre-combustion chamber and flows into the afterburner.
  • the US 3875874 A shows an afterburner for the combustion of exhaust gases with a refractory chamber, which is divided into a first and a second region.
  • An oxidant flows into the turbulent exhaust gas through a plurality of spaced-apart, circumferentially and circumferentially spaced along the refractory chamber arranged air pipes, which are perpendicular to the exhaust gas flow or inclined in the direction of the flowing exhaust gas.
  • the aim of the invention is therefore to overcome the aforementioned disadvantages of the prior art, and to provide a secondary combustion chamber with a flow channel and a method which allow improved mixing of a combustion gas stream with secondary air, in order to optimize afterburning, especially in a biomass combustion device to reach.
  • a secondary combustion chamber should be simple, compact, safe in operation and low maintenance, and have low production costs.
  • the invention relates to a secondary combustion chamber with a flow channel for post combustion of a combustion gas stream by mixing with secondary air, wherein the flow channel defines a flow direction for the combustion gas flow, wherein the flow channel has a cross section with a long side and a short side, wherein at least two secondary air nozzles for injecting the secondary air lead into the flow channel, which within a Eindüsungsabterrorisms the Flow channels are arranged and not parallel to the flow direction aligned Eindüsungslegien.
  • the long side of two opposite long channel walls is formed, wherein at least two secondary air nozzles are arranged on the first long channel wall and at least two secondary air nozzles on the second long channel wall.
  • the secondary air nozzles arranged on the first long channel wall are in each case offset by an offset distance oriented transversely to the flow direction to the secondary air nozzles arranged on the second long channel wall.
  • a flow vortex is then formed between two offset secondary air nozzles which is set in rotation from two sides.
  • the injection of secondary air with two secondary air nozzles in the injection section allows the formation of several adjacent flow vortices in the flow channel.
  • these vortices continue essentially parallel in the flow channel.
  • smaller but smaller vertebrae can form.
  • One of the main parameters of a clean combustion - namely the mixing of the combustion gas with the secondary air - can be significantly improved. Accordingly, the gas phase oxidation increases and the emission of hydrocarbon, carbon monoxide and unburned particles decreases. Thus, for example, a clean combustion of biomass can be done.
  • the secondary combustion chamber can be made smaller overall due to the improved and very rapid mixing. Among other things, this reduces the required installation space and material costs. It is also particularly advantageous that a much faster start-up phase can be realized by a smaller storage mass in the secondary combustion chamber.
  • the combustion gases thus reach a temperature in the secondary combustion chamber, in which afterburning is possible, particularly fast.
  • the optimum temperature is above 700 ° C. Emissions during the start-up phase are thus avoided.
  • the secondary air injection according to the invention requires at most a small amount of energy, e.g. through a flow generator such as a fan.
  • the secondary air nozzles can be easily constructed, so that the secondary combustion chamber is low maintenance, safe in operation and low manufacturable.
  • the formation of the vortices is particularly good when the at least two secondary air nozzles are located approximately equidistant along the flow direction.
  • An embodiment of the invention therefore provides that two adjacent secondary air nozzles have a maximum distance in the flow direction to each other, which is twice the length of the short side of the flow channel cross-section. In this way it can be prevented that one of the flow vortices spreads over the entire flow cross-section of the flow channel, because its expansion is blocked (limited) by an adjacent flow vortex.
  • the flow vortices can also be formed with an equal intensity so that none of the vortices dominates or overlaps the adjacent vortices. Thus, as far as possible homogeneous, as well as uniformly formed adjacent flow vortexes can be realized.
  • the secondary air nozzles are actually arranged lying in the same direction along the direction of flow.
  • the secondary air nozzles should be arranged at the same height along the flow direction, so that they can be cut by a single plane perpendicular to the flow direction. In this way, none of the vortices can propagate over the entire flow cross-section of the flow channel, because its expansion is always, i. already from the time of injection of the secondary air, blocked by an adjacent flow vortex.
  • the injection directions are aligned at least approximately perpendicular to the flow direction. Up to 30 degrees deviation from the vertical lead to a good formation of the flow vortex. The more perpendicular the injection direction is aligned, the higher rotational speeds of the flow vortex can be achieved. In addition, there is a shear between the combustion gas flow and the secondary air flow, which greatly improves the mixing.
  • an embodiment of the invention is of particular advantage, in which the flow channel extends in the direction of flow to the injection section having subsequent mixing section.
  • the vertebrae should be able to continue parallel and adjacent to each other. Therefore, the mixing section should have no or only slight directional and / or cross-sectional changes.
  • the length of the mixing section should be adapted to the flow rates of the secondary air and the combustion gas flow, because of this depends decisively on how far the flow vortex can continue. Friction, secondary vortices and the like weaken the flow vortices with increasing distance from the injection section.
  • the mixing section should be at least three times as long as the length of the short side of the flow channel. Thus, the mixing section ensures that the flow vortices lead to a maximum mixing of the combustion gas flow with secondary air. The emissions are correspondingly low.
  • the mixing of the combustion gas flow with secondary air is further improved in one version of the invention in that the short side of two opposite short channel walls is formed, wherein at least one of the short channel walls is curved outwards.
  • the formation of a domed short outer wall allows a circular flow vortex to rotate along the entire short wall. There is no linear flow in a corner between the short channel wall and a long channel wall into which the flow vortex could not reach. Thus, no unburned combustion gas can move through the flow channel here.
  • the at least one short channel wall is curved in a semicircular outward direction.
  • the long side has a length (a) and the short side has a length (b), wherein the length (a) of the long side approximately multiplies the length (b) of the short side with the number of secondary air nozzles minus one.
  • each vortex can be rotated in two directions by secondary air in rotation.
  • the secondary air nozzles should be evenly distributed over the long side offset by a constant offset distance. That is to say, for example, that two secondary air nozzles arranged on one of the channel walls have a transversely to the flow direction spaced from each other, which corresponds to twice the offset distance. In each case centrally located between the secondary air nozzles on one of the long channel walls then opposite to the other channel wall another secondary air nozzle.
  • the length (a) of the long side should only be approximately equal to the length (b) of the short side multiplied by the number of secondary air nozzles minus one, because the vortexes can easily be easily elliptically formed. Therefore, the length (a) can also deviate from the target value by up to half the length (b) of the short side, without suffering great disadvantages. Too much elliptical formation will result in more shear in the gas stream, which may also result in positive mixing effects, but ultimately will cause an undesirably faster decay of the rotation.
  • the invention develops its full potential of mixing the combustion gas stream with the secondary air when at least four secondary air nozzles, but preferably at least six secondary air nozzles open into the flow channel. Although two or three secondary air nozzles can be produced more cheaply, the additional costs per secondary air nozzle remain within the limits. Regardless of the number of secondary air nozzles, these can be fed by a single flow generator with secondary air.
  • the improved mixing is based on a higher number of secondary air nozzles, in particular on the ratio of central flow vortex to flow vortex, which adjoin the short channel walls. The central flow vortices collide on two sides with adjacent vortices, which intensifies mixing.
  • an embodiment of the invention is of particular advantage, in which the flow channel opens into a combustion chamber, wherein the combustion chamber is preferably a cyclone combustion chamber.
  • the combustion chamber is preferably a cyclone combustion chamber.
  • the rotational speed of the flow vortices decreases, until hardly any mixing of the combustion gas with secondary air is achieved.
  • a change in the flow direction can be brought about and the Mixing of the combustion gas stream with the remaining secondary air, as well as the secondary combustion will be continued.
  • the remaining secondary air is already well distributed within the combustion gas stream, before the latter ever flows into the combustion chamber. Accordingly, the combustion chamber can be made relatively small, since the afterburning proceeds faster.
  • Particularly advantageous is the use of a cyclone combustion chamber, in which the introduced gas flow through rotation about an axis and associated friction, shear and the like can again be thoroughly mixed and post-combusted.
  • the arrangement of the flow channel to the cyclone combustion chamber is preferably eccentric, possibly also tangential, and not parallel to the axis of rotation of the cyclone combustion chamber.
  • the cyclone combustion chamber itself should be rotationally symmetrical about the axis of rotation.
  • the secondary combustion chamber can be made smaller overall due to the improved and very rapid mixing. Among other things, this reduces the required installation space and material costs. It is also particularly advantageous that a much faster start-up phase can be realized by a smaller storage mass in the secondary combustion chamber.
  • the combustion gases thus reach a temperature in the secondary combustion chamber, in which afterburning is possible, particularly fast.
  • the optimum temperature is above 700 ° C. Emissions during the start-up phase are thus avoided.
  • the introduction of the secondary air according to the invention requires at most a small amount of energy, e.g. through a flow generator such as a fan.
  • the secondary air nozzles can be simple in construction, so that the method with a low-maintenance secondary combustion chamber is feasible, which is also safe in operation and low manufacturable.
  • An important alternative method of the invention provides that the injection speed of the secondary air is at least half as large and at most four times as large as the flow velocity of the combustion gas. As a result, stable flow vortices can be formed, which lead to a good mixing of the combustion gas with secondary air.
  • Fig. 1 shows a cross section through a secondary combustion chamber, and in particular a sectional view EE, as shown in FIG. 3 is characterized by the flow channel 1 of the secondary combustion chamber.
  • the flow channel 1 is used for the afterburning of a combustion gas stream G by mixing with secondary air L.
  • the flow channel 1 is initially a flow direction for the combustion gas stream G, in the direction of the combustion gas G moves at a flow velocity v.
  • водородн ⁇ е nozzles 11, 12, 13, 14 open for the injection of the secondary air L into the flow channel 1. These are all arranged within an injection section 2 of the flow channel 1.
  • the secondary air nozzles 11, 12, 13, 14 are all cut from the plane E-E and are therefore all the same along the flow channel 1. Furthermore, they have not parallel to the flow direction R aligned Eindüsungslegien R1, R2, R3, R4. Rather, the Eindüsungslegien R1, R2, R3, R4 are aligned perpendicular to the flow direction of the combustion gas G.
  • the flow channel 1 has a cross section with a long side 5 and a short side 6.
  • the short side 6 is formed by two opposite short channel walls 61, 62, which are both arched outwards. In particular, these are curved semicircular outwards.
  • the long side 5 has a length a and the short side 6 has a length b, the length a of the long side 5 being approximately equal to the length b of the short side 6 multiplied by the number of secondary air nozzles 11, 12, 13, 14 minus one , That is, in the illustrated embodiment, the long side 5 has a length a which is about three times as long as the length b of the short side 6.
  • the long side 5 is formed by two opposite long channel walls 51, 52, wherein two secondary air nozzles 12, 14 are arranged on the first long channel wall 51 and two secondary air nozzles 11, 13 on the second long channel wall 52.
  • two secondary air nozzles 12, 14 are arranged on the first long channel wall 51 secondary air nozzles 12, 14 each offset by an aligned transversely to the flow direction of the combustion gas G offset distance c to the arranged on the second long channel wall 52 secondary air nozzles 11, 13 are arranged.
  • the distance e between two arranged on one side secondary air nozzles 11, 13 or 12, 14 is equal to twice the offset distance c.
  • the secondary air nozzles 11, 14 closest to the short channel walls 61, 62 are not arranged entirely on the outside, but they have a distance d to the outermost point of the short channel walls 61, 62.
  • the injection speed v L of the secondary air L should be at least half and at most four times as large as the flow velocity v G of the combustion gas G.
  • this can the cross-sectional areas of the flow channel 1 and the cumulative cross-sectional area of the secondary air nozzles 11, 12, 13, 14 are matched to one another.
  • Fig. 2 also shows a cross section through a secondary combustion chamber, and in particular a sectional view EE as shown in FIG. 3 is characterized by the flow channel 1 of the secondary combustion chamber.
  • the flow channel 1 is used for the afterburning of a combustion gas stream G by mixing with secondary air L.
  • the flow channel 1 is initially a flow direction for the combustion gas stream G, in the direction of the combustion gas G moves at a flow velocity v.
  • втори ⁇ ное nozzles 11, 12, 13, 14, 15, 16 open for the injection of the secondary air L into the flow channel 1. These are all arranged within an injection section 2 of the flow channel 1.
  • the secondary air nozzles 11, 12, 13, 14, 15, 16 are all cut from the plane EE and are therefore all the same along the flow channel 1. Furthermore, they have not aligned parallel to the flow direction R injection directions R1, R2, R3, R4, R5 , R6 on. Rather, the Eindüsungslegien R1, R2, R3, R4, R5, R6 are aligned perpendicular to the flow direction of the combustion gas G.
  • the flow channel 1 has a cross section with a long side 5 and a short side 6.
  • the short side 6 is formed by two opposite short channel walls 61, 62, which are both arched outwards. In particular, these are curved semicircular outwards.
  • the long side 5 is formed by two opposite long channel walls 51, 52, wherein two secondary air nozzles 13, 15 are arranged on the first long channel wall 51 and two secondary air nozzles 12, 14 on the second long channel wall 52.
  • the remaining two secondary air nozzles 11, 16 are each arranged on one of the short channel walls 61, 62.
  • secondary air nozzle 16 opens tangentially into the semicircular curvature of the second short channel wall 62.
  • secondary air nozzle 16 is also arranged completely outside, so that there is no distance to the outermost point of the second short channel wall 62.
  • Secondary air nozzle 11 opens eccentrically, but not tangentially in the semicircular curvature of the first short channel wall 61 and is not aligned perpendicular to the long channel walls 51, 52.
  • the arranged on the first long channel wall 51 secondary air nozzles 12, 14 and disposed on the second short channel wall 62 Sekundär Kunststoffdüse 16 are each offset by an aligned transversely to the flow direction of the combustion gas G offset distance to the arranged on the second long channel wall 52 secondary air nozzles 13, 15 and arranged on the first short channel wall 61 secondary air nozzle 11.
  • the injection speed v L of the secondary air L should be at least half and at most four times as large as the flow velocity v G of the combustion gas G.
  • Figure 3 shows a secondary combustion chamber 100 with a flow channel 1 for post combustion of a combustion gas stream G by means of mixing with secondary air L.
  • the flow channel 1 a flow direction R for the combustion gas flow G before.
  • the flow channel 1 has a cross section with a long side and a short side and on the observer facing side open two secondary air nozzles 11, 12 for injecting the secondary air L in the flow channel 1.
  • the secondary air nozzles 11, 12 are within a Eindüsungsabêts 2 of the flow channel 1 arranged and have not parallel to the flow direction R aligned Eindüsungsraumen. They are arranged parallel to one another in the direction of flow R, or lie uniformly along the flow channel 1. Thus, they can be cut perpendicularly to the flow direction R from a single plane EE.
  • the flow channel 1 has a mixing section M adjoining the injection section 2 in the flow direction R. With this, the flow channel 1 finally opens into a combustion chamber 102 designed as a cyclone combustion chamber. In particular, the flow channel 1 opens transversely to the axis of rotation of the cyclone combustion chamber in this. Whether tangential and / or eccentric is not visible in the figure.
  • a combustion gas G produced in a primary chamber 101 can now be introduced into the flow channel 1 through an inlet opening 3 with a flow velocity v G oriented in the flow direction R.
  • secondary air L with an injection speed v L through the secondary air nozzles 11, 12 in the flow channel 1 can be introduced.
  • parallel flow vortices form in the Flow channel 1 and continue in the mixing section M parallel.
  • the rotational speed of the flow vortices decreases.
  • the combustion gas G leaves well mixed with secondary air L, the flow channel 1 through an outlet opening 4 and flows into the combustion chamber 102 a.
  • the combustion gas G can be burned. This is particularly dependent on the temperature of the combustion gas G, which increases rapidly after a burner start due to the small volumes of the secondary combustion chamber 100. If the combustion gas G exceeds a certain temperature, it spontaneously ignites when it is enriched with secondary air L.
  • the injection speed v L of the secondary air L should be at least half and at most four times as large as the flow velocity v G of the combustion gas G.

Claims (10)

  1. Chambre de combustion secondaire (100) avec un canal d'écoulement (1) pour la postcombustion d'un flux de gaz de combustion (G) au moyen d'un mélange avec de l'air secondaire (L), le canal d'écoulement (1) prédéfinissant une direction d'écoulement (R) pour le flux de gaz de combustion (G),
    le canal d'écoulement (1) présentant une section transversale avec un côté long (5) et un côté court (6), au moins deux buses d'air secondaire (11, 12, 13, 14, 15, 16) débouchant dans le canal d'écoulement (1) pour injecter l'air secondaire (L), lesquelles buses d'air secondaire étant disposées à l'intérieur d'une section d'injection (2) du canal d'écoulement (1) et présentant des directions d'injection (R1, R2, R3, R4, R5, R6) orientées non parallèlement à la direction d'écoulement (R),
    le côté long (5) étant réalisé par deux parois de canal longues opposées (51, 52), caractérisée en ce qu'au moins deux buses d'air secondaire (11, 12, 13, 14, 15, 16) sont disposées au niveau de la première paroi de canal longue (51) et au moins deux buses d'air secondaire (11, 12, 13, 14, 15, 16) sont disposées au niveau de la deuxième paroi de canal longue (52) et les buses d'air secondaire (11, 12, 13, 14, 15, 16) disposées au niveau de la première paroi de canal longue (51) étant disposées à chaque fois de manière décalée d'une distance de décalage (c) orientée transversalement à la direction d'écoulement (R) par rapport aux buses d'air secondaire (11, 12, 13, 14, 15, 16) disposées au niveau de la deuxième paroi de canal longue (52).
  2. Chambre de combustion secondaire (100) selon la revendication 1,
    caractérisée en ce que deux buses d'air secondaire adjacentes (11, 12, 13, 14, 15, 16) présentent entre elles une distance maximale dans la direction d'écoulement (R) qui vaut le double de la longueur du côté court (6).
  3. Chambre de combustion secondaire (100) selon l'une quelconque des revendications 1 et 2,
    caractérisée en ce que les directions d'injection (R1, R2, R3, R4, R5, R6) sont orientées au moins approximativement perpendiculairement à la direction d'écoulement (R).
  4. Chambre de combustion secondaire (100) selon l'une quelconque des revendications précédentes,
    caractérisée en ce que le canal d'écoulement (1) présente une section de mélange (M) se raccordant à la section d'injection (2) dans la direction d'écoulement (R).
  5. Chambre de combustion secondaire (100) selon l'une quelconque des revendications précédentes,
    caractérisée en ce que le côté court (6) est réalisé par deux parois de canal courtes opposées (61, 62), au moins l'une des parois de canal courtes (61, 62) étant courbée vers l'extérieur.
  6. Chambre de combustion secondaire (100) selon l'une quelconque des revendications précédentes,
    caractérisée en ce que le côté long (5) présente une longueur (a) et le côté court (6) présente une longueur (b), la longueur (a) du côté long (5) correspondant approximativement à la longueur (b) du côté court (6) multipliée par le nombre des buses d'air secondaire (11, 12, 13, 14, 15, 16) moins un.
  7. Chambre de combustion secondaire (100) selon l'une quelconque des revendications précédentes, caractérisée en ce qu'au moins quatre buses d'air secondaire (11, 12, 13, 14, 15, 16) débouchent dans le canal d'écoulement (1).
  8. Chambre de combustion secondaire (100) selon l'une quelconque des revendications précédentes, caractérisée en ce que le canal d'écoulement (1) débouche dans une chambre de combustion à cyclone (102).
  9. Procédé pour faire fonctionner une chambre de combustion secondaire (100) selon l'une quelconque des revendications 1 à 8, caractérisé par les étapes suivantes :
    a) introduction de gaz de combustion (G) dans le canal d'écoulement (1) à une vitesse d'écoulement (vG) dans la direction d'écoulement (R),
    b) introduction d'air secondaire (L) à travers les buses d'air secondaire (11, 12, 13, 14, 15, 16) dans le canal d'écoulement (1) à une vitesse d'injection (vL),
    c) réalisation d'au moins deux tourbillons d'écoulement parallèles (W) dans le canal d'écoulement (1).
  10. Procédé selon la revendication 9,
    caractérisé en ce que la vitesse d'injection (vL) de l'air secondaire (L) est au moins deux fois plus petite et au maximum quatre fois plus grande que la vitesse d'écoulement (vG) du gaz de combustion (G).
EP12188466.2A 2011-10-24 2012-10-15 Chambre de combustion secondaire avec injection d'air secondaire Active EP2587148B1 (fr)

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DE102017008123A1 (de) * 2017-08-30 2019-02-28 Martin GmbH für Umwelt- und Energietechnik Feuerungsanlage und Verfahren zum Betreiben einer Feuerungsanlage
CN108317520B (zh) * 2017-12-21 2019-08-23 北方重工集团有限公司 一种垃圾焚烧炉双层旋涡二次风系统
CN110542097B (zh) * 2019-09-11 2021-05-28 王惠生 一种垃圾焚烧高效低成本的综合炉内脱硝方法

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US3875874A (en) * 1974-05-28 1975-04-08 Berton G Altmann Device for combustion of gaseous wastes
GB2199929B (en) * 1987-01-17 1990-12-05 Mcintyre J Afterburners
DE4021005C1 (fr) 1990-07-02 1991-08-14 Forschungszentrum Juelich Gmbh, 5170 Juelich, De

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EP2587148A3 (fr) 2013-06-12
PL2587148T3 (pl) 2015-05-29
DE102011116723A1 (de) 2013-04-25

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