EP0438682B1 - Système d'échappement avec filtre à particules et brûleur de régénération - Google Patents

Système d'échappement avec filtre à particules et brûleur de régénération Download PDF

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Publication number
EP0438682B1
EP0438682B1 EP90123506A EP90123506A EP0438682B1 EP 0438682 B1 EP0438682 B1 EP 0438682B1 EP 90123506 A EP90123506 A EP 90123506A EP 90123506 A EP90123506 A EP 90123506A EP 0438682 B1 EP0438682 B1 EP 0438682B1
Authority
EP
European Patent Office
Prior art keywords
exhaust
burner
exhaust system
flame tube
hot gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP90123506A
Other languages
German (de)
English (en)
Other versions
EP0438682A3 (en
EP0438682A2 (fr
Inventor
Josef Dipl.-Ing. Kreutmair (Fh)
Alfred Zöbl
Nikolaus Dipl.-Ing. König (FH)
David Michael Simpkin
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Arvin Industries Deutschland GmbH
Original Assignee
Zeuna Starker GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Zeuna Starker GmbH and Co KG filed Critical Zeuna Starker GmbH and Co KG
Publication of EP0438682A2 publication Critical patent/EP0438682A2/fr
Publication of EP0438682A3 publication Critical patent/EP0438682A3/de
Application granted granted Critical
Publication of EP0438682B1 publication Critical patent/EP0438682B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N3/00—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust
    • F01N3/02—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust
    • F01N3/021—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters
    • F01N3/023—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles
    • F01N3/025—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for cooling, or for removing solid constituents of, exhaust by means of filters using means for regenerating the filters, e.g. by burning trapped particles using fuel burner or by adding fuel to exhaust
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S55/00—Gas separation
    • Y10S55/30—Exhaust treatment

Definitions

  • the invention relates to an exhaust system with a particle filter and a burner for regenerating the particle filter, the burner being equipped with a fuel mixture nozzle and a flame tube which at least partially protrudes into the exhaust gas routing system and is flushed with the exhaust gas.
  • the burner is arranged in the exhaust pipe in such a way that the exhaust gas partially flows around the burner and mixes with the hot gases at the burner outlet.
  • the advantage of this design is that the burner can also be ignited while the engine is emitting exhaust gases.
  • a system of this type is known from EP 306 743 A2, in which the exhaust gases strike a flame tube of the burner perpendicularly through an annular gap, graze the flame tube in the longitudinal direction and finally mix with the hot gases of the burner in a crossflow mixer.
  • a hot gas outlet opening and a baffle plate at a distance from this opening are provided on the face of the flame tube, which radially deflect the axially emerging hot gases before they mix with the exhaust gases.
  • the invention has for its object to design an exhaust system of the type mentioned so that there is no risk of overheating a filter arranged close to the burner.
  • the hot gas is divided into a number of relatively small hot gas streams via the hot gas outlet openings in the flame tube.
  • This has the advantage that a uniform and complete mixing between exhaust gas and hot gas is possible and also the risk of the occurrence of larger secondary flame is eliminated. Due to the intimate mixing of the exhaust gases, a mixed gas with an almost homogeneous temperature is created from the mixing location. It is therefore possible to provide a particle or soot filter very close to the burner and thus to take advantage of the advantages associated with it.
  • the hot gas outlet openings are preferably evenly distributed on the flame tube and so far apart relative to its diameter that the escaping hot gas streams do not contact each other if possible.
  • the diameter is as small as possible and the number of outlet openings as large as possible, the lower or upper limit depending on the application being limited by the required pressure and flow conditions.
  • the flame tube provided with a plurality of outlet openings can be arranged differently in the exhaust gas flow path.
  • An arrangement is preferably selected in which the exhaust gas flows around the flame tube to cool it and finally hits the hot gas outlet openings transversely.
  • it is proposed to choose the arrangement so that the exhaust gas hits the flame tube tangentially and spirally flows around it and strikes the hot gas flows.
  • the hot gas outlet openings are distributed on one or more transverse planes near the end of the flame tube at uniform intervals on the circumference of the flame tube, the front end of the flame tube being closed.
  • the hot gas comes out of the flame tube in the form of a plurality of radial partial flows, wherein they lie in a plane which is oriented parallel to the inlet surface of the filter.
  • the above configurations have the advantage of a symmetrical distribution of the hot gas, which favors a homogenization of the gas temperature upstream of the filter.
  • the position of the hot gas outlet openings on the flame tube will depend on the respective construction concept of the exhaust system.
  • the outlet openings are provided on two diametrically opposed surface lines of the flame tube and on the diameter of the flame tube end face connecting these surface lines.
  • the mixing of the exhaust gases with the hot gases can be further optimized according to a further embodiment of the invention if a swirl plate is provided in the flow path of the exhaust gas or the gas mixture.
  • the swirl plate has several slots with slightly twisted sheets in between. When flowing through the slots, the already mixed gas or the exhaust gas is divided into several swirled gas streams, as a result of which the exhaust gases and hot gases are mixed more intensively over a very short distance.
  • the swirl plate is preferably arranged in the flow direction of the exhaust gas shortly before the hot gases emerge from the flame tube, so that a partial flow after the tear-off edge on the swirl plate can carry a partial hot gas flow with it into its swirling movement.
  • the swirl plate can simultaneously serve to concentrate or expand the exhaust gas flow, so that the flame contour outside the flame tube can be adapted to the shape of the filter housing.
  • the system is further favored by the use of a known blue burner which can be designed with variable output, for example depending on the engine exhaust gas temperature. In this way it is ensured that in the low load range of the engine a burner stoichiometric operation is possible, especially since pollutant values and unburned fuel quantities are low in the blue burner and these quantities can be easily combusted with the residual oxygen in the exhaust gas.
  • FIG. 1 shows an internal combustion engine 10, in the exhaust pipe 11 of which a particle filter 12 and a burner 13 are interposed.
  • the exhaust gases coming from the internal combustion engine 10 enter a housing 14 in which the burner 13 and the filter 12 are arranged one behind the other in the direction of flow.
  • the burner 13 will be out of operation while the engine 10 is running, so that the soot particles from the exhaust gases accumulate in the filter 12.
  • the burner 13 is put into operation if necessary by igniting by means of an arc 15 and supplying fuel 16 and combustion air 17.
  • the hot gases emerging from the burner 13 mix in the antechamber 18 of the filter 12 with the exhaust gas temperature being raised in such a way that the soot particles accumulated in the filter 12 oxidize.
  • the size, for example of the housing 14, depends, among other things, on the distance that must be maintained between the burner 13 and the filter 12. As a rule, this distance must be kept relatively large in order to avoid local overheating on the inlet side of the filter 12, which can be caused by uneven mixing of the exhaust and hot gases and by secondary flames in the antechamber 18.
  • a burner 13 is provided, the hot gases of which emerge not through one but through a plurality of openings on the flame tube, these openings being arranged in a plane which is parallel to the inlet surface 20 of the filter 12. This can happen in different ways, depending on which one Orientation of the burner 13 relative to the inlet surface 20 of the filter 12.
  • FIG. 2 An embodiment according to FIG. 2 is possible in which the flame tube 21 runs parallel to the inlet surface 20 of the filter 12.
  • the hot gas outlet openings 22 are located on a plane 23 which is formed on the end face 26 by two diametrically opposed surface lines 24, 25 of the flame tube 21 and a line connecting the two surface lines 24, 25.
  • the plane 23 is also selected so that it lies parallel to the inlet surface 20 of the filter 12.
  • This longitudinal section plane is shown in FIG. 3 with the emerging hot gas flows 27.
  • the exhaust gas stream 11 entering the housing 14 enclosing the burner 21 and the filter 12 strikes the hot gas partial streams 27 perpendicularly and mixes them largely homogeneously due to the distribution of the hot gas.
  • the division of the hot gases into a large number of small streams is preferably carried out in connection with a flame tube, which is arranged perpendicular to the inlet plane 20 of the filter 12. This arrangement is shown in Fig. 1.
  • the burner 13 consists of a flame tube 30, a mixing tube 31 and an atomizer nozzle 32.
  • the end face 33 of the flame tube opposite the atomizer nozzle 32 30 is completely closed.
  • the flame tube 30 has outlet openings 34 which are uniformly distributed on the circumference and are all located on a plane 35 which is oriented parallel to the inlet plane 20 of the filter.
  • the hot gas 36 emerges in star form in numerous partial streams 37 from the flame tube 30, ie parallel to the inlet surface 20 of the filter 12.
  • the exhaust gases 40 flow, as in FIG.
  • the embodiment according to FIG. 4 has the advantage over that of FIG. 2 that a better burned hot gas 36 emerges from the outlet openings 34 located at the end of the flame tube 30. Further rows of outlet openings for the hot gas 36 can be provided, which are arranged in one or more planes parallel to the first plane 35. 4 shows a further level 46 with outlet openings 45 in dashed lines. The outlet openings 45 of this second level 46 can be placed on the hatch opposite the outlet openings 34 of the first level 35.
  • the connection of the hot gas outlet distribution with a so-called blue burner with or without a mixing tube 31 and / or a hot gas recirculation has the further advantage that an exhaust system with variable burner output can be produced due to the relatively good combustion in the wide output range of the blue burner.
  • the burner output is adapted to the engine exhaust gas temperature, which enables a fuel-saving design and optimal control of the exhaust gas inlet temperature into the filter.
  • the division into a large number of small hot gas partial streams 37 therefore not only brings about the homogenization of the gas temperature, but also a reduction in the secondary flame length in the afterburning of the unburned constituents which escape, particularly in substoichiometric burner operation. Because of the division of the hot gases 36, only small lengths of flame can arise due to the smaller amount of hot gas. From this point of view, too, there is a danger of local combustion of the filter surface or uneven burning of the particle filter.
  • FIG. 6 shows an exemplary embodiment in which a swirl plate 50 is arranged parallel to the plane 35 of the outlet openings 34 in front of the outlet openings 34 of the hot gases in the flow direction of the exhaust gases 40.
  • the swirl plate 50 which is shown in a top view (partially) in FIG. 7, consists of an annular disk which is pushed onto the flame tube 30 and is fixedly connected to the housing or flame tube and has a plurality of radial slots 51 to 53.
  • the slats 54 formed by the slots 51-53 are slightly twisted around radial axes.
  • the inflowing exhaust gas 40 is divided with the swirl plate 50 into many partial flows, which form individual vortices 55 behind the swirl plate 50.
  • the arrangement of the swirl plate 50 and the outlet openings 34 for the hot gas are preferably designed and arranged such that each exhaust gas vortex 55 swirls into a partial hot gas flow and thus the essential mixing of the two gases takes place at the hot gas outlet 34.
  • the acting as steering plates lamellae 54 of the swirl plate 50 can also be oriented so that they not only swirl the partial flows, but also divert as needed, z. B. in the direction of the burner axis, d. H. concentrating the exhaust gas flow or, in contrast, expanding the exhaust gas flow.
  • the slots of the swirl plate 50 can run radially, as shown under the number 51 in FIG. 7, or more (52) or less (53) can be chosen obliquely to increase the flow cross section on the swirl plate 50.
  • the swirl plate 50 contributes to shortening the mixing path between exhaust gas and hot gas and thus enables a further reduction in the distance between burner 13 and filter 12.
  • the swirl plate 50 causes an undesirable jam in the exhaust gas flow, then it is possible to pass a partial flow, usually the lower partial flow 11 '(FIG. 1), into the burner 13, in which the residual oxygen from the exhaust gases can be used simultaneously.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Processes For Solid Components From Exhaust (AREA)
  • Filtering Of Dispersed Particles In Gases (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)

Claims (13)

  1. Système pour gaz d'échappement, avec un filtre de particules (12) et un brûleur (13), pour la régénération du filtre de particules, dans lequel le brûleur est équipé d'une buse de carburant (32) et d'un tuyau pour flamme (21, 30), qui pénètre au moins partiellement dans le système d'évacuation des gaz d'échappement et peut être balayé par les gaz d'échappement, caractérisé en ce que le tuyau pour flamme (21, 30) est réalisé avec une pluralité d'orifices de sortie de gaz chauds (22, 34), situés dans au moins un plan (23,35, respectivement 46), orienté à peu près parallèlement à la surface d'entrée (20) du filtre.
  2. Système pour gaz d'échappement selon la revendication 1, caractérisé en ce que les orifices de sortie de gaz chauds (22,34,45) sont répartis à des intervalles réguliers sur le tube pour flamme (21 ou 30).
  3. Système pour gaz d'échappement selon la revendication 1 ou 2, caractérisé en ce que le système pour gaz d'échappement est constitué dans la zone du brûleur (13) de telle façon qu'il se produit un mélange des courants transversaux entre les gaz d'échappement (11,40) et les gaz chauds (27,37) sortant des orifices de sortie (22,34,45).
  4. Système pour gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce que le filtre de particules (12) est disposé dans le sens du courant des gaz d'échappement immédiatement après le brûleur (13).
  5. Système pour gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce qu'un brûleur (13) est prévu avec un tube mélangeur (31) et/ou une recirculation des gaz chauds (36).
  6. Système pour gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce qu'un dispositif de réglage du mélange carburant/air comburant, est associé au brûleur (13), dispositif grâce auquel on peut régler en fonction de la charge du moteur la puissance du brûleur.
  7. Système pour gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce que le tube pour flammes (30) est fermé du côté frontal (33) situé en face de la buse et est pourvu à cette extrémité d'orifices de sortie sensiblement radiaux des gaz chauds (34,45).
  8. Système pour gaz d'échappement selon la revendication 7, caractérisé en ce que les orifices de sortie des gaz chauds (34) sont répartis à des distances régulières les uns les autres dans un plan transversal (35) sur le pourtour du tube pour flammes (30)
  9. Système pour gaz d'échappement selon la revendication 8, caractérisé en ce qu'en outre des orifices de sortie de gaz chauds sont prévus dans un deuxième plan transversal (46) du tube pour flammes (30).
  10. Système pour gaz d'échappement selon l'une des revendications 7 à 9, caractérisé en ce que le tube pour flamme (30) et la conduite des gaz d'échappement (11) son associés de telle manière que le tube pour flammes puisse être balayé selon un trajet en forme de spirale par les gaz d'échappement.
  11. Système pour gaz d'échappement selon l'une des revendications précédentes, caractérisé en ce qu'il est prévu dans le courant mélangé des gaz d'échappement ou des gaz d'échappement et des gaz chauds, un disque de déviation (50) qui répartit le courant gazeux en plusieurs courants partiels (55) tourbillonnants.
  12. Système pour gaz d'échappement selon la revendication 11, caractérisé en ce que le disque de déviation (50) est disposé dans le sens du courant des gaz d'échappement immédiatement avant les orifices de sortie (34 ou 45) des gaz chauds.
  13. Système pour gaz d'échappement selon la revendication 11, caractérisé en ce que le contour de flamme est adaptable à la forme du carter de filtre selon la forme donnée au disque de déviation (50).
EP90123506A 1990-01-25 1990-12-07 Système d'échappement avec filtre à particules et brûleur de régénération Expired - Lifetime EP0438682B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE4002130 1990-01-25
DE4002130 1990-01-25
DE4009201 1990-03-22
DE4009201A DE4009201A1 (de) 1990-01-25 1990-03-22 Abgassystem mit einem partikelfilter und einem regenerierungsbrenner

Publications (3)

Publication Number Publication Date
EP0438682A2 EP0438682A2 (fr) 1991-07-31
EP0438682A3 EP0438682A3 (en) 1992-02-26
EP0438682B1 true EP0438682B1 (fr) 1994-07-20

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EP90123506A Expired - Lifetime EP0438682B1 (fr) 1990-01-25 1990-12-07 Système d'échappement avec filtre à particules et brûleur de régénération

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US (1) US5140814A (fr)
EP (1) EP0438682B1 (fr)
JP (1) JPH04350315A (fr)
AT (1) ATE108865T1 (fr)
DE (2) DE4009201A1 (fr)
DK (1) DK0438682T3 (fr)
ES (1) ES2031055T3 (fr)
GR (1) GR920300093T1 (fr)

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EP0438682A3 (en) 1992-02-26
GR920300093T1 (en) 1993-02-17
US5140814A (en) 1992-08-25
JPH04350315A (ja) 1992-12-04
DE4009201A1 (de) 1991-08-01
ES2031055T3 (es) 1994-10-16
DK0438682T3 (da) 1994-08-29
EP0438682A2 (fr) 1991-07-31
ATE108865T1 (de) 1994-08-15
ES2031055T1 (es) 1992-12-01
DE59006514D1 (de) 1994-08-25

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