EP0367280A1 - Particle filter system - Google Patents

Particle filter system Download PDF

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Publication number
EP0367280A1
EP0367280A1 EP89120374A EP89120374A EP0367280A1 EP 0367280 A1 EP0367280 A1 EP 0367280A1 EP 89120374 A EP89120374 A EP 89120374A EP 89120374 A EP89120374 A EP 89120374A EP 0367280 A1 EP0367280 A1 EP 0367280A1
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EP
European Patent Office
Prior art keywords
combustion chamber
burner
filter system
particle filter
diesel engine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP89120374A
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German (de)
French (fr)
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EP0367280B1 (en
EP0367280B2 (en
Inventor
Heinrich Dipl.-Ing. Berendes
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Deutz AG
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Kloeckner Humboldt Deutz AG
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Application filed by Kloeckner Humboldt Deutz AG filed Critical Kloeckner Humboldt Deutz AG
Priority to AT89120374T priority Critical patent/ATE79921T1/en
Publication of EP0367280A1 publication Critical patent/EP0367280A1/en
Publication of EP0367280B1 publication Critical patent/EP0367280B1/en
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    • 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
    • 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
    • F01N2240/00—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being
    • F01N2240/14—Combination or association of two or more different exhaust treating devices, or of at least one such device with an auxiliary device, not covered by indexing codes F01N2230/00 or F01N2250/00, one of the devices being a fuel burner
    • 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
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/30—Arrangements for supply of additional air
    • 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
    • F01N3/08—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous
    • F01N3/10—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust
    • F01N3/24—Exhaust or silencing apparatus having means for purifying, rendering innocuous, or otherwise treating exhaust for rendering innocuous by thermal or catalytic conversion of noxious components of exhaust characterised by constructional aspects of converting apparatus
    • F01N3/36—Arrangements for supply of additional fuel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • 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 a method for regenerating particle filters according to the preamble of claim 1.
  • Particle emission is a procedural disadvantage of the diesel engine. So far, attempts have been made to solve this problem by means of internal engine measures. However, the increasingly stringent legal requirements for vehicle engines will in future require the use of particle filters in the exhaust gas flow.
  • Such a particle filter is described in the unpublished DE-OS 37 29 861. This is a ceramic filter arranged in the main exhaust gas flow, which can be regenerated by burning off the particle coating during engine operation.
  • the burner output required for this depends on the respective quantity and temperature of the exhaust gas from the diesel engine and thus on its speed and load. A constant or only dependent on the engine speed mixture amount and thus burner output, as described in DE-OS 37 29 861, can not meet this requirement.
  • the particle filter For the effectiveness and lifespan of the particle filter, it is important that its surface is evenly loaded with particles and that the particles burn off evenly and completely. This is the only way to maximize the useful life of the particle filter between regenerations and to avoid thermal stresses with the associated heat cracks in the ceramic filter body.
  • the engine exhaust gas and the hot gas of the burner enter radially from the inside out into an afterburning chamber in front of the particle filter.
  • the outer edge parts of the particle filter are preferably loaded with particles and are preferably regenerated in the regeneration phase. It follows that the use of the filter surface in connection with the thermal stresses is not optimal.
  • the invention has for its object to provide an improved particle filter system that is regenerative in the entire operating range of the diesel engine without endangering the particle filter.
  • the output of the burner can be varied as desired within the scope of the amount of oxygen that is fed directly to the burner and that is available as residual oxygen in the exhaust gas of the diesel engine, simply by varying the amount of fuel.
  • the arrangement according to claim 2 offers the advantage of the smallest possible amount of burner air and therefore the lowest possible fuel consumption for their promotion and heating.
  • the embodiment according to claim 3 offers the advantage of being able to achieve an optimal coordination of the amounts of fuel and oxygen-containing gas for each operating point of the internal combustion engine.
  • the arrangement according to claim 4 offers the advantage of a simple air supply system of the burner, which can be varied in a simple manner by the design according to claim 5 in its delivery characteristics.
  • the object of the invention is also achieved by the characterizing part of independent claim 7.
  • the configuration according to the invention ensures that the exhaust gas of the internal combustion engine is evenly distributed in the secondary combustion chamber by the swirl flow in normal engine operation and thus loads the particle filter evenly.
  • the exhaust gas flows of the diesel engine and the burner mix intensively in the manner of a shear current mixture due to their opposite sense of swirl and thus lead to a uniform, complete and gentle regeneration of the particle filter via a uniform temperature distribution.
  • flow guiding devices or similar internals are present in the secondary combustion chamber, e.g. flow baffles or flow orifices arranged radially in the secondary combustion chamber, it can be advantageous to design the direction of the swirl in the primary and secondary combustion chamber in the same direction.
  • the embodiment according to claim 8 offers the advantage of a short overall length of the particle filter system, an advantage which is further enhanced by the arrangement according to claim 9, since the mixing and homogenization path of the exhaust gas up to the particle filter is maximized.
  • the embodiment according to claim 10 offers the advantage of a symmetrical flow, which leads to a uniform mixing of the individual exhaust gas flows when loading the particle filter and, in addition, to the uniform admixing of the fuel gas when regenerating.
  • the arrangement according to claim 11 offers the advantage of the greatest possible mixing length for the exhaust gas of the internal combustion engine and the burner.
  • the combustion chamber is cooled by the engine exhaust gas, the heat absorbed directly benefiting the regeneration.
  • the axis of the primary combustion chamber can run parallel to the axis of the secondary combustion chamber or cut it or run obliquely to it.
  • the primary combustion chamber on the periphery of the secondary combustion chamber and outside of it.
  • the inflow direction into the secondary combustion chamber can be radial or tangential, the tangential inflow being directed in the sense or in the opposite direction to the flow of the exhaust gas line.
  • the arrangement according to claim 12 prevents negative effects of the exhaust gas pulsations of the diesel engine on the stability of the flame of the primary combustion chamber and enables an admixture of oxygen-containing exhaust gas into the primary combustion chamber.
  • the design according to claim 13 reflects the area of the combustion chamber bores, which has proven itself for a tuning to insensitivity to pressure fluctuations.
  • the baffle plate Due to the relatively small diameter of the baffle plate and its large distance from the outlet opening of the primary combustion chamber, the baffle plate has no significant influence on the flow, so that the uniformity of the action on the particle filter remains guaranteed.
  • the design according to claim 16 ensures that the baffle plate is not destroyed by overheating due to the high thermal stress in the hot gas stream of the primary combustion chamber.
  • ceramics are particularly suitable for this task.
  • the arrangement according to claim 17 represents a simple form of air supply to the burner.
  • the delivery characteristic of the displacement fan can be modified in a simple manner by the design according to claim 18.
  • the arrangement according to claim 19 offers an elegant solution for supplying air to the primary combustion chamber in the case of a compressed air source, as is given in the compressed air tank of commercial vehicles in the normal case.
  • the supercritical nozzle has the advantage that an approximately constant amount of air is supplied even with certain pressure fluctuations in the reservoir.
  • the embodiment according to claim 20 allows a so-called button regeneration. In contrast to fully automatic regeneration, this is triggered at the driver's request by pressing a button when the engine is idling. Since there is a large excess of air in the exhaust gas of the engine in this operating state of the internal combustion engine, an external oxygen supply can be dispensed with. As a result, the construction effort for the regeneration plant is particularly low, but the operating effort is increased.
  • the particle filter system 2 consists of a burner 3 and a particle filter 7, both of which are arranged in the main flow of an exhaust pipe 10 of a diesel engine 1.
  • the burner 3 consists of an air swirl nozzle 5, a primary combustion chamber 6 and a secondary combustion chamber 9.
  • the air swirl atomizer nozzle 5 is supplied with fuel of low pressure by a delivery and metering device (not shown) via the fuel supply line 18.
  • the supply of compressed air at low pressure takes place via the gas line 4.
  • this is connected to a displacement blower 15 driven by the diesel engine 1, to which a blow-off valve 11 is assigned.
  • the air swirl atomizer nozzle 5 is connected to a pressure vessel 20 via a solenoid valve 21 and a nozzle 19 with a supercritical flow.
  • the air swirl atomizer nozzle 5 is followed by the primary combustion chamber 6.
  • the primary combustion chamber 6 sits coaxially in the secondary combustion chamber 9, on the front wall 22 of which it is attached.
  • the primary combustion chamber 6 has an axial outlet opening 8, the diameter of which is approximately 60 to 80% of the diameter of the primary combustion chamber 6.
  • openings 12 are provided on the circumference of the primary combustion chamber 6 in its front third, as seen in the direction of flow. These openings have a total cross section of 5 and 20% of the primary combustion chamber cross section.
  • the secondary combustion chamber 9 like the primary combustion chamber 6, is cylindrical. On its circumference and - seen in the direction of flow - the front part, the exhaust pipe 10 is connected tangentially. In the case of a plurality of exhaust gas lines 10, the distances between them on the circumference of the secondary combustion chamber 9 are the same, as shown in FIG. 2.
  • the primary combustion chamber 9 is followed by the particle filter 7.
  • This is a monolithic ceramic filter of the usual type.
  • a circular baffle plate 13 is provided between the outlet opening 8 of the primary combustion chamber 6 and the particle filter 7, which e.g. is connected via spokes 14 to the circumference of the secondary combustion chamber 9.
  • the baffle plate 13, which is made of heat-resistant material such. B. ceramic, has a diameter of about 60 of the primary combustion chamber diameter and a distance to the opening 8 of about 150% of the primary combustion chamber diameter.
  • the particle filter system works as follows:
  • the exhaust gas of the diesel engine 1 enters tangentially into the secondary combustion chamber 9 through the exhaust gas line 10 and causes a swirl flow there.
  • the swirl flow in the secondary combustion chamber 9 In the case of two or more exhaust pipes, as z. B. are common in V-engines, any differences in the exhaust gas temperature and the particle content between the different exhaust pipes 10 are compensated for by the swirl flow in the secondary combustion chamber 9. This homogenization of the exhaust gas flow leads to an even loading and thus to the optimal use of the particle filter.
  • the exhaust gas back pressure of the diesel engine 1 increases.
  • the burner 3 is automatically switched on during the normal operation of the diesel engine 1 in order to regenerate the particle filter 7.
  • the air swirl atomizer nozzle 5 receives fuel via the fuel line 18 and air via the gas line 4.
  • the fuel is from a source not shown, e.g. B.
  • the fuel delivery pump of the diesel engine 1 is delivered under relatively low pressure. Its amount depends on the current load or exhaust gas temperature and speed of the diesel engine 1.
  • the air which also has a relatively low pressure, is either conveyed by a diesel engine-driven displacement fan 15 or by a pressure vessel 20 via a solenoid valve 21 and via a supercritical nozzle 19 to the air swirl atomizer nozzle.
  • the solution with the pressure container 20 is suitable for vehicles with a compressed air brake and an appropriately dimensioned air compressor.
  • This structurally simple solution delivers a largely constant air pressure in front of the air swirl atomizer nozzle 5 even when the tank pressure is not quite constant.
  • the pressure that the displacement blower 15 supplies depends on the speed of the diesel engine 1, a blow-off valve 11 being provided to limit the pressure.
  • the amount of air supplied to the air swirl atomizer nozzle 5 and thus also the energy required for its promotion and heating is relatively small, since in the particle filter system 1 according to the invention the residual oxygen of the diesel engine exhaust gas is also used to regenerate the particle filter 7.
  • the residual oxygen content in the exhaust gas of a diesel engine is between approx. 7% at full load and approx. 18% when idling.
  • the 7% residual oxygen content at full load is just sufficient to carry out regeneration in a reasonable time, provided that the exhaust gas temperature reaches the regeneration temperature at this load point.
  • This is only the case for diesel engines with a relatively high nominal speed.
  • the nominal speed is chosen to be relatively low for reasons of fuel consumption and emissions, which also means that the maximum exhaust gas temperature remains relatively low. Therefore, the burner 3 must also work at the full load point of the nominal speed, the point of the lowest power requirement, in order to reach the regeneration temperature.
  • the fuel-air mixture of the burner 3 is approximately stoichiometric at this operating point. In this way, the regeneration temperature is achieved with the lowest possible amount of additional air and without using the residual oxygen content of the exhaust gas.
  • the compressed air supplied forms a swirl flow, which leads to fine atomization of the fuel at a cutting edge.
  • the fuel-air mixture enters the primary combustion chamber 6 with swirl from the air swirl atomizer nozzle 5 and is ignited there with the aid of a high-voltage ignition device (not shown).
  • the freshly blown mixture hits this torus vortex and is intensively processed by multiple recirculation.
  • the stationary torus vortex also acts as a flame holder, which ensures a stable flame in the primary combustion chamber 6.
  • the stability of the flame also depends on pressure fluctuations in the primary combustion chamber 6 which result from the exhaust gas flow from the diesel engine 1. These pressure fluctuations are largely weakened by the openings 12 on the circumference of the primary combustion chamber 6. In the area of the openings 12, there is a negative pressure in the primary combustion chamber 6 due to the ejector action of the air swirl atomizing nozzle 5, through which the pulsating exhaust gas from the secondary combustion chamber 9 enters the primary combustion chamber 6. Since the flue gas pressure fluctuations are also effective at the opening 8 of the primary combustion chamber 6, their effects on the flame in the primary combustion chamber 6 largely cancel each other out.
  • Another possibility of processing the residual oxygen of the exhaust gas of the internal combustion engine in the primary combustion chamber 6 is to supply exhaust gas from the exhaust gas line 10 to the air swirl atomizer nozzle 5 instead of external air, as shown in FIG. 4.
  • the required flow connection is established via the gas line 4.
  • the required pressure difference between the air swirl atomizer nozzle 5 and the primary combustion chamber 6 is achieved by a deliberate leak in the throttle valve 17, which either has a defined bore or a defined gap to the exhaust gas line 10 owns.
  • This type of regeneration only works when idling, since only at this operating point is there a sufficiently high residual oxygen content in the exhaust gas. Therefore, automatic regeneration is not possible, so that in this case the regeneration must be triggered by the driver at the push of a button.
  • the baffle plate 13 located in front of the opening 8 of the primary combustion chamber 6 prevents unburned fuel from reaching the particle filter 7 when the primary combustion chamber 6 is not ignited and this is at risk of being overheated after ignition. Since the baffle plate 13 is in the hot exhaust gas flow, it is itself hot and acts as a surface carburetor for the fuel until the fuel-air mixture is ignited. Because of its small size, based on the diameter of the secondary combustion chamber 9, it does not influence the uniformity of the flow in the secondary combustion chamber 9.
  • the combustion of a partly substoichiometric mixture in the primary combustion chamber 6 leads to a particle-free partial combustion due to the intensive mixture preparation with strong formation of CO, H2 and radicals.
  • These gases combine in the secondary combustion chamber 9 with part of the residual oxygen in the exhaust gas, the mixing of the exhaust gas with the reaction gas emerging from the primary combustion chamber 6 taking place according to the invention by the opposite direction of rotation of the swirl in the primary and secondary combustion chamber in the manner of a shear current mixture.
  • This intensive mixing process causes the secondary combustion chamber 9 and thus also the end face of the particle filter 7 to be evenly exposed to flames. Starting from individual ignition nuclei, therefore, a uniform and gentle combustion of the particle coating of the particle filter 7 is achieved.

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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)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
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Abstract

Method for the regeneration of a particle filter of a diesel engine <??>The aim of the method is a particle filter which can be regenerated in all operating points of the diesel engine with the aid of a burner operating in the full flow of the engine exhaust. <??>The solution is achieved by a burner (3) to which fuel and oxygen- containing gas are fed in a variable ratio. As a result, the burner can produce the output required for achieving the regeneration temperature at any operating point of the diesel engine. <??>The method is suitable for diesel engines with thermally regenerable particle filters. <IMAGE>

Description

Die Erfindung betrifft ein Verfahren zur Regenerierung von Partikelfiltern nach dem Oberbegriff des Anspruchs 1.The invention relates to a method for regenerating particle filters according to the preamble of claim 1.

Die Partikelemission ist ein verfahrensbedingter Nachteil des Dieselmotors. Bisher wurde versucht, dieses Problem durch innermotorische Maßnahmen zu lösen. Die immer schär­fer werdenden gesetzlichen Auflagen für Fahrzeugmotoren erfordern in Zukunft aber den Einsatz von Partikelfiltern im Abgasstrom.Particle emission is a procedural disadvantage of the diesel engine. So far, attempts have been made to solve this problem by means of internal engine measures. However, the increasingly stringent legal requirements for vehicle engines will in future require the use of particle filters in the exhaust gas flow.

Ein solches Partikelfilter wird in der nicht vorveröffent­lichten DE-OS 37 29 861 beschrieben. Hierbei handelt es sich um ein im Abgashauptstrom angeordnetes Keramikfilter, das während des Motorbetriebes durch Abbrennen des Parti­kelbelages regenerierbar ist.Such a particle filter is described in the unpublished DE-OS 37 29 861. This is a ceramic filter arranged in the main exhaust gas flow, which can be regenerated by burning off the particle coating during engine operation.

Da die zur Regeneration erforderliche Abgastemperatur von mehr als 550 Grad Celsius im Motorbetrieb in der Regel nicht erreicht wird, muß das Abgas entsprechend aufgeheizt werden. Dazu dient ein Brenner mit einer Luftdrallzerstäu­ berdüse, der Druckluft in konstantem unterstöchiometrischem Mengenstrom zugeführt wird. Die noch unverbrannten Be­standteile der den Brenner verlassenden heißen Gase reagieren in einer Nachbrennkammer mit dem Restsauerstoff der dort eingeleiteten Abgase des Dieselmotors. Dadurch wird die zur Regeneration erforderliche Temperatur er­reicht.Since the exhaust gas temperature required for regeneration of more than 550 degrees Celsius is usually not reached in engine operation, the exhaust gas must be heated up accordingly. A burner with an air swirl atomizer is used for this Over nozzle, the compressed air is supplied in a constant substoichiometric flow. The still unburned components of the hot gases leaving the burner react in a post-combustion chamber with the residual oxygen from the exhaust gases of the diesel engine introduced there. The temperature required for regeneration is thereby achieved.

Die dazu benötigte Brennerleistung ist von der jeweiligen Menge und Temperatur des Abgases des Dieselmotors und da­mit von dessen Drehzahl und Last abhängig. Eine konstante oder nur von der Motordrehzahl abhängige Gemischmenge und damit Brennerleistung, wie sie in der DE-OS 37 29 861 be­schrieben ist, kann diese Forderung nicht erfüllen.The burner output required for this depends on the respective quantity and temperature of the exhaust gas from the diesel engine and thus on its speed and load. A constant or only dependent on the engine speed mixture amount and thus burner output, as described in DE-OS 37 29 861, can not meet this requirement.

Für die Wirksamkeit und Lebensdauer des Partikelfilters ist es wichtig, das dessen Oberfläche gleichmäßig mit Partikeln beladen wird und der Abbrand der Partikel gleichmäßig und vollständig erfolgt. Nur so kann die Nutzungsdauer des Partikelfilters zwischen den Regenera­tionen maximiert werden und Wärmespannungen mit den damit verbundenen Wärmerissen im keramischen Filterkörper ver­mieden werden.For the effectiveness and lifespan of the particle filter, it is important that its surface is evenly loaded with particles and that the particles burn off evenly and completely. This is the only way to maximize the useful life of the particle filter between regenerations and to avoid thermal stresses with the associated heat cracks in the ceramic filter body.

Bei dem Partikelfilter nach der DE-OS 37 29 861 treten das Motorabgas und das Heißgas des Brenners radial von innen nach außen in eine Nachbrennkammer vor dem Partikelfilter ein. Dadurch werden die äußeren Randpartien des Partikel­filters bevorzugt mit Partikeln beladen und in der Regene­rierungsphase bevorzugt regeneriert. Daraus folgt, daß die Nutzung der Filteroberfläche in Verbindung mit den Wärme­spannungen nicht optimal ist.In the particle filter according to DE-OS 37 29 861, the engine exhaust gas and the hot gas of the burner enter radially from the inside out into an afterburning chamber in front of the particle filter. As a result, the outer edge parts of the particle filter are preferably loaded with particles and are preferably regenerated in the regeneration phase. It follows that the use of the filter surface in connection with the thermal stresses is not optimal.

Der Erfindung liegt die Aufgabe zugrunde, ein verbessertes Partikelfiltersystem zu schaffen, das im gesamten Be­triebsbereich des Dieselmotors regenerationsfähig ist, ohne das Partikelfilter zu gefährden.The invention has for its object to provide an improved particle filter system that is regenerative in the entire operating range of the diesel engine without endangering the particle filter.

Die Aufgabe wird durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst.The object is achieved by the characterizing features of claim 1.

Durch die erfindungsgemäße Lösung kann die Leistung des Brenners im Rahmen der Sauerstoffmenge, die dem Brenner direkt zugeführt wird und die als Restsauerstoff im Abgas des Dieselmotors verfügbar ist, allein durch Variation der Brennstoffmenge beliebig verändert werden.With the solution according to the invention, the output of the burner can be varied as desired within the scope of the amount of oxygen that is fed directly to the burner and that is available as residual oxygen in the exhaust gas of the diesel engine, simply by varying the amount of fuel.

Auf diese Weise kann die Forderung erfüllt werden, im ge­sainten Betriebsbereich des Dieselmotors eine annähernd konstante und ausreichend hohe Regenerationstemperatur und damit eine vollständige Regeneration des Partikelfilters zu verwirklichen. Damit ist auch die Voraussetzung für ei­ne vollautomatische, vom Fahrer unabhängige Regeneration erfüllt.In this way, the requirement can be met to achieve an approximately constant and sufficiently high regeneration temperature and thus a complete regeneration of the particle filter in the clean operating range of the diesel engine. This also fulfills the prerequisite for fully automatic regeneration that is independent of the driver.

Die Anordnung nach Anspruch 2 bietet den Vorteil kleinst­möglicher Brennerluftmenge und danit kleinstmöglichen Brennstoffverbrauch zu deren Förderung und Aufheizung.The arrangement according to claim 2 offers the advantage of the smallest possible amount of burner air and therefore the lowest possible fuel consumption for their promotion and heating.

Die erfindungsgemäße Ausbildung nach Anspruch 3 bietet den Vorteil, eine für jeden Betriebspunkt der Brennkraft­maschine optimale Abstimmung der Mengen von Brennstoff und sauerstoffhaltigem Gas verwirklichen zu können.The embodiment according to claim 3 offers the advantage of being able to achieve an optimal coordination of the amounts of fuel and oxygen-containing gas for each operating point of the internal combustion engine.

Die Anordnung nach Anspruch 4 bietet den Vorteil einer einfachen Luftversorgungsanlage des Brenners, die durch die Ausbildung nach Anspruch 5 in ihrer Liefercharakte­ristik auf einfache Weise variiert werden kann.The arrangement according to claim 4 offers the advantage of a simple air supply system of the burner, which can be varied in a simple manner by the design according to claim 5 in its delivery characteristics.

Die Ausbildung nach Anspruch 6 ermöglicht bei Vorhanden­sein einer Druckluftquelle mit in etwa konstantem Druck, wie sie in Nutzfahrzeugen üblich ist, in Verbindung mit einer überkritisch durchströmten Düse eine besonders ein­fache Lösung der Luftversorgung des Brenners.The embodiment according to claim 6, in the presence of a compressed air source with approximately constant pressure, as is customary in commercial vehicles, in connection with a supercritically flowed nozzle enables a particularly simple solution to the air supply to the burner.

Die Aufgabe der Erfindung wird auch durch den kennzeich­nenden Teil des unabhängigen Anspruchs 7 gelöst. Durch die erfindungsgemäße Ausbildung wird erreicht, daß das Abgas der Brennkraftmaschine sich im normalen Motorbetrieb durch die Drallströmung gleichmäßig in der Sekundärbrennkammer verteilt und dadurch das Partikelfilter gleichmäßig belädt. Zum andern wird erreicht, daß sich bei der Regeneration die Abgasströme des Dieselmotors und des Brenners durch deren entgegengesetzten Drallsinn in Art einer Scherstrom­mischung intensiv mischen und so über eine gleichmäßige Temperaturverteilung vor dem Partikelfilter zu dessen gleichmäßiger, vollständiger und schonender Regeneration führen.The object of the invention is also achieved by the characterizing part of independent claim 7. The configuration according to the invention ensures that the exhaust gas of the internal combustion engine is evenly distributed in the secondary combustion chamber by the swirl flow in normal engine operation and thus loads the particle filter evenly. On the other hand, it is achieved that during the regeneration, the exhaust gas flows of the diesel engine and the burner mix intensively in the manner of a shear current mixture due to their opposite sense of swirl and thus lead to a uniform, complete and gentle regeneration of the particle filter via a uniform temperature distribution.

Bei Vorhandensein von Strömungsleitvorrichtungen oder ähn­lichen Einbauten in der Sekundärbrennkammer, z.B radial in der Sekundärbrennkammer angeordneten Strömungsleit­blechen oder Strömungsblenden, kann es vorteilhaft sein, die Richtung des Dralls in der Primär- und Sekundärbrenn­kammer gleichsinnig zu gestalten.If flow guiding devices or similar internals are present in the secondary combustion chamber, e.g. flow baffles or flow orifices arranged radially in the secondary combustion chamber, it can be advantageous to design the direction of the swirl in the primary and secondary combustion chamber in the same direction.

Die Ausbildung nach Anspruch 8 bietet den Vorteil kurzer Baulänge des Partikelfiltersystems, ein Vorteil, der durch die Anordnung nach Anspruch 9 noch verstärkt wird, da der Mischungs- und Homogenisierungsweg des Abgases bis zum Partikelfilter maximiert wird.The embodiment according to claim 8 offers the advantage of a short overall length of the particle filter system, an advantage which is further enhanced by the arrangement according to claim 9, since the mixing and homogenization path of the exhaust gas up to the particle filter is maximized.

Die Ausbildung nach Anspruch 10 bietet den Vorteil einer symmetrischen Strömung, die beim Beladen des Partikelfil­ters zu einer gleichmäßigen Vermischung der einzelnen Ab­gasströme führt und beim Regenerieren zusätzlich zur gleichmäßigen Zumischung des Brenngases.The embodiment according to claim 10 offers the advantage of a symmetrical flow, which leads to a uniform mixing of the individual exhaust gas flows when loading the particle filter and, in addition, to the uniform admixing of the fuel gas when regenerating.

Die Anordnung nach Anspruch 11 bietet den Vorteil einer größtmöglichen Mischlänge für das Abgas der Brennkraft­maschine und des Brenners. Außerdem wird die Brennkammer von dem Motorabgas gekühlt, wobei die aufgenommene Wärme der Regeneration direkt zugute kommt.The arrangement according to claim 11 offers the advantage of the greatest possible mixing length for the exhaust gas of the internal combustion engine and the burner. In addition, the combustion chamber is cooled by the engine exhaust gas, the heat absorbed directly benefiting the regeneration.

Von dieser bevorzugten Anordnung und Ausbildung der Pri­märbrennkammer kann auch abgewichen werden. So kann es bei gewissen Anwendungsfällen vorteilhaft sein, die Primär­brennkammer komplett in die Sekundärbrennkammer einzu­bauen, so daß zwischen der Vorderwand der Sekundärbrenn­kammer und der Primärbrennkammer ein Abstand entsteht, der die Anbringung von axialen Öffnungen in der Vorderwand der Primärbrennkammer gestattet.It is also possible to deviate from this preferred arrangement and design of the primary combustion chamber. So it can be advantageous in certain applications to completely install the primary combustion chamber in the secondary combustion chamber so that there is a distance between the front wall of the secondary combustion chamber and the primary combustion chamber, which allows axial openings to be made in the front wall of the primary combustion chamber.

Es kann aber auch vorteilhaft sein, die Primärbrennkammer wenigstens teilweise außerhalb und vor der Sekundärbrenn­kammer anzubringen.However, it may also be advantageous to at least partially mount the primary combustion chamber outside and in front of the secondary combustion chamber.

Auch kann es von Vorteil sein, die Primärbrennkammer nicht koaxial zur Sekundärbrennkammer anzubringen, sondern aus der Mitte der Sekundärbrennkammer versetzt. Dabei kann die Achse der Primärbrennkammer parallel zur Achse der Sekun­därbrennkammer verlaufen oder diese schneiden oder wind­schief zu dieser verlaufen.It may also be advantageous not to mount the primary combustion chamber coaxially with the secondary combustion chamber, but to move it from the center of the secondary combustion chamber. The axis of the primary combustion chamber can run parallel to the axis of the secondary combustion chamber or cut it or run obliquely to it.

Bei Einbaufällen mit möglichst kurz bauenden Partikelfil­tersystem ist es auch denkbar, die Primärbrennkammer am Umfang der Sekundärbrennkammer und außerhalb derselben an­zubringen. Dabei kann die Einströmrichtung in die Sekun­därbrennkammer radial oder tangential sein, wobei die tangentiale Einströmung im Sinne oder im Gegensinne zur Strömung der Abgasleitung gerichtet sein kann.For installation cases with the shortest possible particle filter system, it is also conceivable to mount the primary combustion chamber on the periphery of the secondary combustion chamber and outside of it. The inflow direction into the secondary combustion chamber can be radial or tangential, the tangential inflow being directed in the sense or in the opposite direction to the flow of the exhaust gas line.

Die Anordnung nach Anspruch 12 verhindert negative Auswir­kungen der Abgaspulsationen des Dieselmotors auf die Stabilität der Flamme der Primärbrennkammer und ermöglicht eine Zumischung sauerstoffhaltigen Abgases in die Primär­brennkammer.The arrangement according to claim 12 prevents negative effects of the exhaust gas pulsations of the diesel engine on the stability of the flame of the primary combustion chamber and enables an admixture of oxygen-containing exhaust gas into the primary combustion chamber.

Die Ausbildung nach Anspruch 13 gibt den Bereich der Brennkammerbohrungen wieder, der sich für eine Abstimmung auf Druckschwankungsunempfindlichkeit bewährt hat.The design according to claim 13 reflects the area of the combustion chamber bores, which has proven itself for a tuning to insensitivity to pressure fluctuations.

Die Anordnung nach den Ansprüchen 14 und 15 bietet den Vorteil, daß bei Ausfall der Zündung der Kraftstoff nicht in den Kernbereich des Partikelfilters gelangen kann, was zur Überhitzung und partiellen Zerstörung des Filters führen würde.The arrangement according to claims 14 and 15 offers the advantage that if the ignition fails, the fuel cannot reach the core area of the particle filter, which would lead to overheating and partial destruction of the filter.

Aufgrund des relativ kleinen Durchmessers der Prallplatte und ihres großen Abstandes von der Austrittsöffnung der Primärbrennkammer, bewirkt die Prallplatte keine wesent­liche Strömungsbeeinflussung, so daß die Gleichmäßigkeit der Beaufschlagung des Partikelfilters gewährleistet bleibt.Due to the relatively small diameter of the baffle plate and its large distance from the outlet opening of the primary combustion chamber, the baffle plate has no significant influence on the flow, so that the uniformity of the action on the particle filter remains guaranteed.

Durch die Ausbildung nach Anspruch 16 wird sichergestellt, daß die Prallplatte durch die hohe thermische Bean­spruchung im Heißgasstrom der Primärbrennkammer nicht durch Überhitzung zerstört wird. Für diese Aufgabe eignet sich neben hochwarmfestem Stahl insbesondere Keramik.The design according to claim 16 ensures that the baffle plate is not destroyed by overheating due to the high thermal stress in the hot gas stream of the primary combustion chamber. In addition to high-temperature steel, ceramics are particularly suitable for this task.

Die Anordnung nach Anspruch 17 stellt eine einfache Form der Luftversorgung des Brenners dar.The arrangement according to claim 17 represents a simple form of air supply to the burner.

Die Fördercharakteristik des Verdrängergebläses kann durch die Ausbildung nach Anspruch 18 auf einfache Weise modifi­ziert werden.The delivery characteristic of the displacement fan can be modified in a simple manner by the design according to claim 18.

Die Anordnnung nach Anspruch 19 bietet für den Fall einer Druckluftquelle, wie sie im Druckluftbehälter von Nutz­fahrzeugen im normalen Fall gegeben ist, eine elegante Lösung zur Luftversorgung der Primärbrennkammer. Die über­kritische Düse bietet dabei den Vorteil, daß auch bei ge­wissen Druckschwankungen im Vorratsbehälter eine annähernd konstante Luftmenge geliefert wird.The arrangement according to claim 19 offers an elegant solution for supplying air to the primary combustion chamber in the case of a compressed air source, as is given in the compressed air tank of commercial vehicles in the normal case. The supercritical nozzle has the advantage that an approximately constant amount of air is supplied even with certain pressure fluctuations in the reservoir.

Die Ausbildung nach Anspruch 20 gestattet eine sogenannte Knopfdruckregeneration. Diese wird im Gegensatz zur voll­automatischen Regeneration auf Wunsch des Fahrers durch Knopfdruck bei Leerlauf des Motors ausgelöst. Da in diesem Betriebszustand der Brennkraftmaschine ein großer Luft­überschuß im Abgas des Motors besteht, kann auf eine äuße­re Sauerstoffzufuhr verzichtet werden. Dadurch wird der Bauaufwand für die Regenerationsanlage besonders niedrig, der Bedienungsaufwand jedoch erhöht.The embodiment according to claim 20 allows a so-called button regeneration. In contrast to fully automatic regeneration, this is triggered at the driver's request by pressing a button when the engine is idling. Since there is a large excess of air in the exhaust gas of the engine in this operating state of the internal combustion engine, an external oxygen supply can be dispensed with. As a result, the construction effort for the regeneration plant is particularly low, but the operating effort is increased.

Weitere Merkmale der Erfindung ergeben sich aus der fol­genden Beschreibung und der Zeichnung, in der ein Aus­führungsbeispiel der Erfindung schematisch dargestellt ist.Further features of the invention result from the following description and the drawing, in which an embodiment of the invention is shown schematically.

Es zeigen:

  • Fig. 1: Einen Längsschnitt durch das Partikelfil­tersystem mit der Luftversorgung der Luftdrall­zerstäuberdüse durch ein Verdrängergebläse
  • Fig. 2: Einen Querschnitt durch die Primär- und Sekundärbrennkammer mit zwei Abgasleitungen, die tangential in die Sekundärbrennkammer münden.
  • Fig. 3: Einen Längsschnitt durch das Partikelfil­tersystem mit der Luftversorgung der Luftdrall­zerstäuberdüse aus einer Konstantdruckquelle
  • Fig. 4: Einen Längsschnitt durch das Partikelfil­tersystem mit der Sauerstoffversorgung der Luft­drallzerstäuberdüse durch Zufuhr von Motor­abgas.
Show it:
  • Fig. 1: A longitudinal section through the particle filter system with the air supply to the air swirl nozzle through a displacement fan
  • Fig. 2: A cross section through the primary and secondary combustion chamber with two exhaust pipes, which open tangentially into the secondary combustion chamber.
  • Fig. 3: A longitudinal section through the particle filter system with the air supply to the air swirl atomizer nozzle from a constant pressure source
  • Fig. 4: A longitudinal section through the particle filter system with the oxygen supply to the air swirl atomizer nozzle by supplying engine exhaust.

Das Partikelfiltersystem 2 besteht aus einem Brenner 3 und einem Partikelfilter 7, die beide im Hauptstrom einer Ab­gasleitung 10 eines Dieselmotors 1 angeordnet sind. Der Brenner 3 besteht aus einer Luftdrallzerstäuberdüse 5, ei­ner Primärbrennkammer 6 und einer Sekundärbrennkammer 9.The particle filter system 2 consists of a burner 3 and a particle filter 7, both of which are arranged in the main flow of an exhaust pipe 10 of a diesel engine 1. The burner 3 consists of an air swirl nozzle 5, a primary combustion chamber 6 and a secondary combustion chamber 9.

Die Luftdrallzerstäuberdüse 5 wird von einer nicht darge­stellten Förder- und Dosiereinrichtung über die Brenn­stoffzufuhrleitung 18 mit Brennstoff niedrigen Druckes versorgt. Die Versorgung mit Druckluft geringen Druckes erfolgt über die Gasleitung 4. Diese ist in der Ausführung nach Figur 1 mit einem von dem Dieselmotor 1 angetriebenen Verdrängergebläse 15 verbunden, dem ein Abblaseventil 11 zugeordnet ist.The air swirl atomizer nozzle 5 is supplied with fuel of low pressure by a delivery and metering device (not shown) via the fuel supply line 18. The supply of compressed air at low pressure takes place via the gas line 4. In the embodiment according to FIG. 1, this is connected to a displacement blower 15 driven by the diesel engine 1, to which a blow-off valve 11 is assigned.

In der Ausführung nach Figur 3 ist die Luftdrallzerstäu­berdüse 5 über ein Magnetventil 21 und eine überkritisch durchströmte Düse 19 mit einem Druckbehälter 20 verbunden.In the embodiment according to FIG. 3, the air swirl atomizer nozzle 5 is connected to a pressure vessel 20 via a solenoid valve 21 and a nozzle 19 with a supercritical flow.

Bei der Lösung nach Figur 4 besteht eine Verbindung zwi­schen der Abgasleitung 10 und der Gasleitung 4, wobei in der Abgasleitung 10 eine Drosselklappe 17 und in der Gas­leitung 4 ein Magnetventil 16 angeordnet sind.In the solution according to FIG. 4, there is a connection between the exhaust line 10 and the gas line 4, a throttle valve 17 being arranged in the exhaust line 10 and a solenoid valve 16 being arranged in the gas line 4.

Der Luftdrallzerstäuberdüse 5 ist die Primärbrennkammer 6 nachgeschaltet. Die Primärbrennkammer 6 sitzt koaxial in der Sekundärbrennkammer 9, an deren Vorderwand 22 sie be­festigt ist.The air swirl atomizer nozzle 5 is followed by the primary combustion chamber 6. The primary combustion chamber 6 sits coaxially in the secondary combustion chamber 9, on the front wall 22 of which it is attached.

Die Primärbrennkammer 6 besitzt eine axiale Austrittsöff­nung 8, deren Durchmesser ca. 60 bis 80 % des Durchmessers der Primärbrennkammer 6 beträgt. Außerdem sind an Umfang der Primärbrennkammer 6 in deren - in Strömungsrichtung gesehen - vorderem Drittel Öffnungen 12 angebracht. Diese Öffnungen haben einen Gesamtquerschnitt von 5 und 20 % des Primärbrennkammerquerschnitts.The primary combustion chamber 6 has an axial outlet opening 8, the diameter of which is approximately 60 to 80% of the diameter of the primary combustion chamber 6. In addition, openings 12 are provided on the circumference of the primary combustion chamber 6 in its front third, as seen in the direction of flow. These openings have a total cross section of 5 and 20% of the primary combustion chamber cross section.

Die Sekundärbrennkammer 9 ist wie die Primärbrennkammer 6 zylinderförmig. An ihrem Umfang und - in Strömungsrichtung gesehen - vorderen Teil ist die Abgasleitung 10 tangential angeschlossen. Bei mehreren Abgasleitungen 10 sind deren Abstände am Umfang der Sekundärbrennkammer 9 gleich, wie in Figur 2 dargestellt.The secondary combustion chamber 9, like the primary combustion chamber 6, is cylindrical. On its circumference and - seen in the direction of flow - the front part, the exhaust pipe 10 is connected tangentially. In the case of a plurality of exhaust gas lines 10, the distances between them on the circumference of the secondary combustion chamber 9 are the same, as shown in FIG. 2.

Der Primärbrennkammer 9 schließt sich das Partikelfilter 7 an. Hierbei handelt es sich um ein monolithisches Keramik­filter üblicher Bauart.The primary combustion chamber 9 is followed by the particle filter 7. This is a monolithic ceramic filter of the usual type.

Zwischen der Austrittsöffnung 8 der Primärbrennkammer 6 und dem Partikelfilter 7 ist eine kreisförmige Prallplatte 13 vorgesehen, die z.B. über Speichen 14 mit dem Umfang der Sekundärbrennkammer 9 verbunden ist. Die Prallplatte 13, die aus warmfestem Material wie z. B. Keramik besteht, hat einen Durchmesser von ca. 60 des Primärbrennkammer­durchmessers und einen Abstand zur Öffnung 8 von ca. 150 % des Primärbrennkammerdurchmessers.A circular baffle plate 13 is provided between the outlet opening 8 of the primary combustion chamber 6 and the particle filter 7, which e.g. is connected via spokes 14 to the circumference of the secondary combustion chamber 9. The baffle plate 13, which is made of heat-resistant material such. B. ceramic, has a diameter of about 60 of the primary combustion chamber diameter and a distance to the opening 8 of about 150% of the primary combustion chamber diameter.

Das Partikelfiltersystem funktioniert wie folgt:The particle filter system works as follows:

Im normalen Motorbetrieb tritt das Abgas des Dieselmotors 1 durch die Abgasleitung 10 tangential in die Sekundär­brennkammer 9 ein und bewirkt dort eine Drallströmung. Im Falle von zwei oder mehreren Abgasleitungen, wie sie z. B. bei V-Motoren üblich sind, werden eventuell vorhandene Un­terschiede der Abgastemperatur und des Partikelgehaltes zwischen den verschiedenen Abgasleitungen 10 durch die Drallströmung in der Sekundärbrennkammer 9 ausgeglichen. Diese Homogenisierung des Abgasstromes führt zu einer gleichmäßigen Beladung und damit zur optimalen Ausnutzung des Partikelfilters.In normal engine operation, the exhaust gas of the diesel engine 1 enters tangentially into the secondary combustion chamber 9 through the exhaust gas line 10 and causes a swirl flow there. In the case of two or more exhaust pipes, as z. B. are common in V-engines, any differences in the exhaust gas temperature and the particle content between the different exhaust pipes 10 are compensated for by the swirl flow in the secondary combustion chamber 9. This homogenization of the exhaust gas flow leads to an even loading and thus to the optimal use of the particle filter.

Dabei steigt der Abgasgegendruck des Dieselmotors 1 an. Wenn der Abgasgegendruck eine bestimmte Höhe erreicht hat, wird automatisch, während des normalen Betriebes des Die­selmotors 1 der Brenner 3 eingeschaltet, um das Partikel­filter 7 zu regenerieren.The exhaust gas back pressure of the diesel engine 1 increases. When the exhaust gas back pressure has reached a certain level, the burner 3 is automatically switched on during the normal operation of the diesel engine 1 in order to regenerate the particle filter 7.

Dadurch erhält die Luftdrallzerstäuberdüse 5 über die Brennstoffleitung 18 Brennstoff und über die Gasleitung 4 Luft.As a result, the air swirl atomizer nozzle 5 receives fuel via the fuel line 18 and air via the gas line 4.

Der Brennstoff wird von einer nicht abgebildeten Quelle, z. B. der Kraftstoff-Förderpumpe des Dieselmotors 1 unter relativ geringem Druck angeliefert. Seine Menge richtet sich nach der momentanen Last bzw. Abgastemperatur und Drehzahl des Dieselmotors 1.The fuel is from a source not shown, e.g. B. the fuel delivery pump of the diesel engine 1 is delivered under relatively low pressure. Its amount depends on the current load or exhaust gas temperature and speed of the diesel engine 1.

Die Luft, die ebenfalls einen relativ niedrigen Druck hat, wird entweder von einem Dieselmotor angetriebenen Verdrän­gergebläse 15 oder von einem Druckbehälter 20 über ein Magnetventil 21 und über eine überkritische Düse 19 zur Luftdrallzerstäuberdüse gefördert.The air, which also has a relatively low pressure, is either conveyed by a diesel engine-driven displacement fan 15 or by a pressure vessel 20 via a solenoid valve 21 and via a supercritical nozzle 19 to the air swirl atomizer nozzle.

Die Lösung mit dem Druckbehälter 20 bietet sich bei Fahr­zeugen mit Druckluftbremse und entsprechend dimensionier­ten Luftkompressor an. Diese konstruktiv einfache Lösung liefert auch bei nicht ganz konstantem Behälterdruck einen weitgehend konstanten Luftdruck vor der Luftdrallzerstäu­berdüse 5.The solution with the pressure container 20 is suitable for vehicles with a compressed air brake and an appropriately dimensioned air compressor. This structurally simple solution delivers a largely constant air pressure in front of the air swirl atomizer nozzle 5 even when the tank pressure is not quite constant.

Demgegenüber ist der Druck, den das Verdrängergebläse 15 liefert, von der Drehzahl des Dieselmotors 1 abhängig, wo­bei ein Abblaseventil 11 zur Druckbegrenzung vorgesehen ist.In contrast, the pressure that the displacement blower 15 supplies depends on the speed of the diesel engine 1, a blow-off valve 11 being provided to limit the pressure.

Die der Luftdrallzerstäuberdüse 5 zugeführte Luftmenge und damit auch die zu ihrer Förderung und Aufheizung benötigte Energie ist relativ gering, da bei dem erfindungsgemäßen Partikelfiltersystem 1 der Restsauerstoff des Dieselmotor­abgases zur Regeneration des Partikelfilters 7 mit heran­gezogen wird.The amount of air supplied to the air swirl atomizer nozzle 5 and thus also the energy required for its promotion and heating is relatively small, since in the particle filter system 1 according to the invention the residual oxygen of the diesel engine exhaust gas is also used to regenerate the particle filter 7.

Der Restsauerstoffgehalt im Abgas eines Dieselmotors liegt zwischen ca. 7 % bei Vollast und ca. 18 % im Leerlauf. Die 7 % Restsauerstoffgehalt bei Vollast reichen gerade aus, um eine Regeneration in angemessener Zeit zu verwirkli­chen, vorausgesetzt, die Abgastemperatur erreicht in die­sem Lastpunkt die Regenerationstemperatur. Dies ist nur bei Dieselmotoren mit relativ hoher Nenndrehzahl der Fall. Bei Stadtbusmotoren, bei denen Partikelfilter in erster Linie zur Anwendung kommen, wird die Nenndrehzahl aus Ver­brauchs- und Emissionsgründen relativ niedrig gewählt, wo­durch auch die maximale Abgastemperatur relativ niedrig bleibt. Deshalb muß hier auch im Vollastpunkt der Nenn­drehzahl, dem Punkt des kleinsten Leistungsbedarfs des Brenners 3, dieser arbeiten, um die Regenerationstempera­tur zu erreichen. Da in diesem Betriebspunkt nur die er­forderlich Mindestsauerstoffmenge im Abgas vorliegt, darf dem Abgas kein Sauerstoff entzogen werden. Deshalb ist in diesem Betriebspunkt das Brennstoff-Luftgemisch des Brenners 3 ungefähr stöchiometrisch. Auf diese Weise wird die Regenerationstemperatur mit der geringst möglichen Zu­satzluftmenge und ohne Inanspruchnahme des Restsauerstoff­gehaltes des Abgases erreicht.The residual oxygen content in the exhaust gas of a diesel engine is between approx. 7% at full load and approx. 18% when idling. The 7% residual oxygen content at full load is just sufficient to carry out regeneration in a reasonable time, provided that the exhaust gas temperature reaches the regeneration temperature at this load point. This is only the case for diesel engines with a relatively high nominal speed. In city bus engines, where particle filters are primarily used, the nominal speed is chosen to be relatively low for reasons of fuel consumption and emissions, which also means that the maximum exhaust gas temperature remains relatively low. Therefore, the burner 3 must also work at the full load point of the nominal speed, the point of the lowest power requirement, in order to reach the regeneration temperature. Since only the required minimum amount of oxygen is present in the exhaust gas at this operating point, no oxygen may be extracted from the exhaust gas. Therefore, the fuel-air mixture of the burner 3 is approximately stoichiometric at this operating point. In this way, the regeneration temperature is achieved with the lowest possible amount of additional air and without using the residual oxygen content of the exhaust gas.

In allen anderen Betriebspunkten des Dieselmotors 1 ist eine höhere Brennerleistung und damit eine größere Brenn­stoffmenge erforderlich, was bei gleichibleibender oder ab­nehmender Luftmenge ein unterstöchiometrisches Gemisch im Brenner 3 zur Folge hat. Der fehlende Sauerstoff wird dann vom Motorabgas geliefert, dessen Restsauerstoffgehalt mit der jeweils erforderlichen Brennerleistung steigt.In all other operating points of the diesel engine 1, a higher burner output and thus a larger amount of fuel are required, which results in a substoichiometric mixture in the burner 3 with a constant or decreasing amount of air. The missing oxygen is then supplied by the engine exhaust, the residual oxygen content of which increases with the burner output required.

In der Luftdrallzerstäuberdüse 5 bildet die zugeführte Druckluft eine Drallströmung, die an einer Schneide zu einer feinen Zerstäubung des Brennstoffs führt.In the air swirl atomizer nozzle 5, the compressed air supplied forms a swirl flow, which leads to fine atomization of the fuel at a cutting edge.

Das Brennstoff-Luftgemisch tritt mit Drall aus der Luft­drallzerstäuberdüse 5 in die Primärbrennkammer 6 ein und wird dort mit Hilfe einer nicht abgebildeten Hoch­spannungszündvorrichtung gezündet.The fuel-air mixture enters the primary combustion chamber 6 with swirl from the air swirl atomizer nozzle 5 and is ignited there with the aid of a high-voltage ignition device (not shown).

Aufgrund der Drallströmung in der Primärbrennkammer 6 bil­det sich in deren Achse eine Unterdruckzone. Dadurch strö­men die brennenden Gase in Richtung Luftdrallzerstäuber­düse 5 zurück und bilden einen Toruswirbel.Due to the swirl flow in the primary combustion chamber 6, a vacuum zone is formed in its axis. As a result, the burning gases flow back in the direction of the air swirl atomizing nozzle 5 and form a torus vortex.

Auf diesen Toruswirbel trifft das frisch eingeblasene Ge­misch und wird durch Mehrfachrezirkulation intensiv auf­bereitet.The freshly blown mixture hits this torus vortex and is intensively processed by multiple recirculation.

Der stationäre Toruswirbel wirkt außerdem als Flammenhal­ter, wodurch eine stabile Flamme in der Primärbrennkammer 6 gewährleistet ist.The stationary torus vortex also acts as a flame holder, which ensures a stable flame in the primary combustion chamber 6.

Die Stabilität der Flamme hängt auch von Druckschwankungen in der Primärbrennkammer 6 ab, die vom Abgasstrom des Die­selmotors 1 herrühren. Diese Druckschwankungen werden durch die Öffnungen 12 am Umfang der Primärbrennkammer 6 weitgehend abgeschwächt. Im Bereich der Öffnungen 12 herrscht aufgrund der Ejektorwirkung der Luftdrallzerstäu­berdüse 5 in der Primärbrennkammer 6 ein Unterdruck, durch den das pulsierende Abgas aus der Sekundärbrennkammer 9 in die Primärbrennkammer 6 eintritt. Da die Abgasdruckschwan­kungen zugleich auch an der Öffnung 8 der Primärbrenn­kammer 6 wirksam sind, heben sie sich in ihrer Wirkung auf die Flamme in der Primärbrennkammer 6 weitgehend auf.The stability of the flame also depends on pressure fluctuations in the primary combustion chamber 6 which result from the exhaust gas flow from the diesel engine 1. These pressure fluctuations are largely weakened by the openings 12 on the circumference of the primary combustion chamber 6. In the area of the openings 12, there is a negative pressure in the primary combustion chamber 6 due to the ejector action of the air swirl atomizing nozzle 5, through which the pulsating exhaust gas from the secondary combustion chamber 9 enters the primary combustion chamber 6. Since the flue gas pressure fluctuations are also effective at the opening 8 of the primary combustion chamber 6, their effects on the flame in the primary combustion chamber 6 largely cancel each other out.

Außerdem tritt mit dem Abgas durch die Öffnungen 12 Rest­sauerstoff in die Primärbrennkammer 6 ein, was besonders bei sehr fettem Gemisch zu einer erwünschten Abmagerung führt, die ein gewünschtes Hinauswandern der Flamme aus der Primärbrennkammer 6 begrenzt und damit ein Abreißen und Verlöschen der Flamme verhindert.In addition, with the exhaust gas, residual oxygen enters the primary combustion chamber 6 through the openings 12, which, particularly in the case of a very rich mixture, leads to a desired emaciation, which limits the desired migration of the flame out of the primary combustion chamber 6 and thus prevents the flame from tearing off and extinguishing.

Eine weitere Möglichkeit, den Restsauerstoff des Abgases der Brennkraftmaschine schon in der Primärbrennkammer 6 zu verarbeiten, besteht darin, der Luftdrallzerstäuberdüse 5 anstelle von externer Luft Abgas aus der Abgasleitung 10 zuzuführen, wie in Fig. 4 dargestellt wird. Durch Öffnen eines Magnetventils 16 und gleichzeitiges Schließen einer Drosselklappe 17 wird über die Gasleitung 4 die erforder­liche Strömungsverbindung hergestellt. Die erforderliche Druckdifferenz zwischen Luftdrallzerstäuberdüse 5 und Primärbrennkammer 6 wird durch eine gewollte Undichtheit der Drosselklappe 17 erreicht, die entweder eine definier­te Bohrung oder einen definierten Spalt zur Abgasleitung 10 besitzt. Diese Art der Regeneration funktioniert nur beim Leerlauf, da nur in diesem Betriebspunkt ein aus­reichend hoher Restsauerstoffhehalt im Abgas vorliegt. Deshalb ist eine automatische Regeneration nicht möglich, so daß in diesem Fall die Regeneration durch Knopfdruck vom Fahrer ausgelöst werden muß.Another possibility of processing the residual oxygen of the exhaust gas of the internal combustion engine in the primary combustion chamber 6 is to supply exhaust gas from the exhaust gas line 10 to the air swirl atomizer nozzle 5 instead of external air, as shown in FIG. 4. By opening a solenoid valve 16 and simultaneously closing a throttle valve 17, the required flow connection is established via the gas line 4. The required pressure difference between the air swirl atomizer nozzle 5 and the primary combustion chamber 6 is achieved by a deliberate leak in the throttle valve 17, which either has a defined bore or a defined gap to the exhaust gas line 10 owns. This type of regeneration only works when idling, since only at this operating point is there a sufficiently high residual oxygen content in the exhaust gas. Therefore, automatic regeneration is not possible, so that in this case the regeneration must be triggered by the driver at the push of a button.

Die der Öffnung 8 der Primärbrennkammer 6 vorgelagerte Prallplatte 13 verhindert, daß beim Nichtzünden der Pri­märbrennkammer 6 unverbrannter Brennstoff auf das Parti­kelfilter 7 gelangt und dieses nach erfolgter Zündung durch Überhitzung gefährdet. Da die Prallplatte 13 im heißen Abgasstrom steht, ist sie selber heiß und wirkt bis zur Zündung des Kraftstoffluftgemisches als Oberflächen­vergaser für den Kraftstoff. Aufgrund ihrer geringen Ab­messung, bezogen auf den Durchmesser der Sekundärbrenn­kammer 9 beeinflußt sie die Gleichmäßigkeit der Strömung in der Sekundärbrennkammer 9 nicht.The baffle plate 13 located in front of the opening 8 of the primary combustion chamber 6 prevents unburned fuel from reaching the particle filter 7 when the primary combustion chamber 6 is not ignited and this is at risk of being overheated after ignition. Since the baffle plate 13 is in the hot exhaust gas flow, it is itself hot and acts as a surface carburetor for the fuel until the fuel-air mixture is ignited. Because of its small size, based on the diameter of the secondary combustion chamber 9, it does not influence the uniformity of the flow in the secondary combustion chamber 9.

Die Verbrennung eines zum Teil unterstöchiometrischen Ge­misches in der Primärbrennkammer 6 führt aufgrund der intensiven Gemischaufbereitung zu einer partikelfreien Teilverbrennung unter starker Bildung von CO, H₂ und Radikalen. Diese Gase verbinden sich in der Sekundärbrenn­kammer 9 mit einem Teil des Restsauerstoffs des Abgases, wobei die Vermischung des Abgases mit dem aus der Primär­brennkammer 6 austretenden Reaktionsgases erfindungsgemäß durch den entgegengesetzten Drehsinn des Dralls in der Primär- und Sekundärbrennkammer in Art einer Scherstrom­mischung erfolgt.The combustion of a partly substoichiometric mixture in the primary combustion chamber 6 leads to a particle-free partial combustion due to the intensive mixture preparation with strong formation of CO, H₂ and radicals. These gases combine in the secondary combustion chamber 9 with part of the residual oxygen in the exhaust gas, the mixing of the exhaust gas with the reaction gas emerging from the primary combustion chamber 6 taking place according to the invention by the opposite direction of rotation of the swirl in the primary and secondary combustion chamber in the manner of a shear current mixture.

Dieser intensive Mischvorgang bewirkt, daß die Sekundär­brennkammer 9 und damit auch die Stirnseite des Partikel­filters 7 gleichmäßig von Flammen beaufschlagt werden. Ausgehend von einzelnen Zündkeimen wird daher ein gleich­mäßiger und schonender Abbrand des Partikelbelages des Partikelfilters 7 erreicht.This intensive mixing process causes the secondary combustion chamber 9 and thus also the end face of the particle filter 7 to be evenly exposed to flames. Starting from individual ignition nuclei, therefore, a uniform and gentle combustion of the particle coating of the particle filter 7 is achieved.

Claims (20)

1. Verfahren zur Regeneration eines Partikelfilters (7), das in der Abgasleitung (10) einer Brennkraftmaschi­ne, insbesondere eines Dieselmotors (1) angeordnet ist, wobei die Regeneration durch Abbrennen des Partikelbelages im Vollstrom des Abgases erfolgt, mit einem dem Partikel­filter (7) zugeordneten Brenner (3), dem Brennstoff und sauerstoffhaltigen Gas zuführbar sind,
dadurch gekennzeichnet, daß das Verhältnis der Mengen des dem Brenner (3) zugeführten Brennstoffes und sauerstoff­haltigen Gases variierbar ist.1. A method for the regeneration of a particle filter (7) which is arranged in the exhaust pipe (10) of an internal combustion engine, in particular a diesel engine (1), the regeneration taking place by burning off the particle coating in the full flow of the exhaust gas, using a particle filter (7) assigned burner (3) to which fuel and oxygen-containing gas can be supplied,
characterized in that the ratio of the amounts of fuel and oxygen-containing gas fed to the burner (3) can be varied. 2. Verfahren nach Anspruch 1,
dadurch gekennzeichnet, daß das Verhältnis des dem Brenner (3) zugeführten Brennstoffs und sauerstoffhaltigen Gases in dem Betriebspunkt des Dieselmotors (1), bei dem der Leistungsbedarf des Brenners (3) zum Erreichen der Regene­rationstemperatur am niedrigsten ist, in etwa stöchiome­trisch und in allen übrigen Betriebspunkten des Dieselmo­tors (1) unterstöchiometrisch ist.2. The method according to claim 1,
characterized in that the ratio of the fuel and oxygen-containing gas supplied to the burner (3) at the operating point of the diesel engine (1) at which the power requirement of the burner (3) to reach the regeneration temperature is the lowest is approximately stoichiometric and in all others Operating points of the diesel engine (1) is substoichiometric. 3. Verfahren nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die dem Brenner (3) zugeführ­ten Mengen an Brennstoff und sauerstoffhaltigem Gas im ge­samten Betriebsbereich des Diesel(notors (1) variierbar sind.3. The method according to claim 1 or 2,
characterized in that the amounts of fuel and oxygen-containing gas supplied to the burner (3) can be varied in the entire operating range of the diesel (notor (1)). 4. Verfahren nach einem der Ansprüche 1 oder 2,
dadurch gekennzeichnet, daß die dem Brenner (3) zugeführte Menge des sauerstoffhaltigen Gases proportional zur Dreh­zahl des Dieselmotors (1) ist.4. The method according to any one of claims 1 or 2,
characterized in that the amount of oxygen-containing gas supplied to the burner (3) is proportional to the speed of the diesel engine (1). 5. Verfahren nach Anspruch 4,
dadurch gekennzeichnet, daß die dem Brenner (3) zugeführte Menge des sauerstoffhaltigen Gases proportional zur Dreh­zahl des Dieselmotors (1) ist und ab einer bestimmten Drehzahl des Dieselmotors (1) in etwa konstant gehalten wird.5. The method according to claim 4,
characterized in that the amount of oxygen-containing gas fed to the burner (3) is proportional to the speed of the diesel engine (1) and is kept approximately constant from a certain speed of the diesel engine (1). 6. Verfahren nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die dem Brenner (3) zugeführte Menge des sauerstoffhaltigen Gases im Gesamtbetriebsbe­reich des Dieselmotors (1) konstant gehalten wird.6. The method according to claim 1 or 2,
characterized in that the amount of oxygen-containing gas supplied to the burner (3) is kept constant in the overall operating range of the diesel engine (1). 7. Partikelfiltersystem mit einem Partikelfilter (7) im Hauptstrom einer Abgasleitung (10) eines Dieselmotors (1) und einem Brenner (3), wobei der Brenner (3) eine Luftdrallzerstäuberdüse (5) aufweist, der mittels einer Gasleitung (4) sauerstoffhaltiges Gas zuführbar ist, und an die sich eine Primärbrennkammer (6) mit einer Primär­drallströmung und eine Sekundärbrennkammer (9) anschlie­ßen, insbesondere nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die Abgasleitung (10) draller­zeugend an die Sekundärbrennkammer (9) angeschlossen ist und der Drehsinn der Drallströmung der Sekundärbrennkammer (9) dem Drehsinn der Drallströmung in der Primärbrenn­kammer (6) vorzugsweise entgegengerichtet ist.7. Particle filter system with a particle filter (7) in the main flow of an exhaust pipe (10) of a diesel engine (1) and a burner (3), the burner (3) having an air swirl atomizer nozzle (5) which by means of a gas line (4) contains oxygen-containing gas can be supplied and to which a primary combustion chamber (6) with a primary swirl flow and a secondary combustion chamber (9) are connected, in particular according to one of claims 1 to 6, characterized in that the exhaust gas line (10) is connected to the secondary combustion chamber (9) in a manner producing a swirl and the direction of rotation of the swirl flow of the secondary combustion chamber (9) is preferably opposite to the direction of rotation of the swirl flow in the primary combustion chamber (6). 8. Partikelfiltersystem nach Anspruch 7,
dadurch gekennzeichnet, daß die Abgasleitung (10) am Um­fang der Sekundärbrennkammer (9) angeschlossen ist.8. particle filter system according to claim 7,
characterized in that the exhaust pipe (10) is connected to the periphery of the secondary combustion chamber (9). 9. Partikelfiltersystem nach den Ansprüchen 7 oder 8, dadurch gekennzeichnet, daß die Abgasleitung (10) in den in Strömungsrichtung vorderen Teil der Sekundärbrennkammer (9) mündet.9. Particulate filter system according to claims 7 or 8, characterized in that the exhaust pipe (10) opens into the front part of the secondary combustion chamber (9) in the flow direction. 10. Partikelfiltersystem nach einem der Ansprüche 7 bis 9,
dadurch gekennzeichnet, daß bei mehreren Abgasleitungen (10) deren Einmündungen in die Sekundärbrennkammer (9) in gleichen Abständen angeordnet sind.10. Particulate filter system according to one of claims 7 to 9,
characterized in that in the case of a plurality of exhaust gas lines (10) their outlets into the secondary combustion chamber (9) are arranged at equal intervals. 11. Partikelfiltersystem nach einem der Ansprüche 7 bis 10,
dadurch gekennzeichnet, daß die Primärbrennkammer (6) vor­zugsweise innerhalb des in Strömungsrichtung vorderen Teils der Sekundärbrennkammer (9) angeordnet ist.11. Particle filter system according to one of claims 7 to 10,
characterized in that the primary combustion chamber (6) is preferably arranged within the part of the secondary combustion chamber (9) which is at the front in the flow direction. 12. partikelfiltersystem nach einem der Ansprüche 7 bis 11,
dadurch gekennzeichnet, daß am Umfang der Primärbrenn­kammer (6) Öffnungen (12) angeordnet sind.12. Particulate filter system according to one of claims 7 to 11,
characterized in that openings (12) are arranged on the circumference of the primary combustion chamber (6). 13. Partikelfiltersystem nach Anspruch 12,
dadurch gekennzeichnet, daß die Öffnungen (12) in Strö­mungsrichtung gesehen im ersten Drittel der Primärbrenn­kammer (6) angeordnet sind und ihr Querschnitt 5 bis 20 % des Querschnitts der Primärbrennkammer (6) beträgt.13. Particulate filter system according to claim 12,
characterized in that the openings (12), viewed in the direction of flow, are arranged in the first third of the primary combustion chamber (6) and their cross section is 5 to 20% of the cross section of the primary combustion chamber (6). 14. Partikelfiltersystem nach einem der Ansprüche 7 bis 13,
dadurch gekennzeichnet, daß eine Prallplatte (13) koaxial zur Austrittsöffnung (8) der Primärbrennkammer (6) dem Partikelfilter (7) vorgelagert angeordnet ist.14. Particulate filter system according to one of claims 7 to 13,
characterized in that a baffle plate (13) is arranged coaxially to the outlet opening (8) of the primary combustion chamber (6) upstream of the particle filter (7). 15. Partikelfiltersystem nach Anspruch 14,
dadurch gekennzeichnet, daß die Prallplatte 13 vorzugswei­se kreisförmig ist und ihr Durchmesser ca. 60 % und ihr Abstand zum Primärkammerende ca. 150 % des Durchmessers der Primärbrennkammer (6) beträgt.15. Particle filter system according to claim 14,
characterized in that the baffle plate 13 is preferably circular and its diameter is approximately 60% and its distance from the end of the primary chamber is approximately 150% of the diameter of the primary combustion chamber (6). 16. Partikelfiltersystem nach den Ansprüchen 14 und 15, dadurch gekennzeichnet, daß die Prallplatte (13) aus warm­festem Material besteht.16. Particulate filter system according to claims 14 and 15, characterized in that the baffle plate (13) consists of heat-resistant material. 17. Partikelfiltersystem nach einem der Ansprüche 7 bis 16,
dadurch gekennzeichnet, daß die Gasleitung (4) mit der Druckseite eines von der Brennkraftmaschine (1) angetrie­benen Verdrängergebläses (15) verbunden ist.17. Particle filter system according to one of claims 7 to 16,
characterized in that the gas line (4) is connected to the pressure side of a displacement blower (15) driven by the internal combustion engine (1). 18. Partikelfiltersystem nach Anspruch 17,
dadurch gekennzeichnet, daß in der Gasleitung (4) ein Ab­blaseventil (11) angeordnet ist.18. Particulate filter system according to claim 17,
characterized in that a blow-off valve (11) is arranged in the gas line (4). 19. Partikelfiltersystem nach einem der Ansprüche 7 bis 16,
dadurch gekennzeichnet, daß die Gasleitung (4) über ein Magnetventil (18) und eine Strömungsdrossel (19), die vor­zugsweise als eine überkritische Düse ausgebildet ist, mit einem Druckbehälter (20) von konstantem oder annähernd konstantem Druck verbunden ist.19. Particulate filter system according to one of claims 7 to 16,
characterized in that the gas line (4) is connected to a pressure vessel (20) of constant or approximately constant pressure via a solenoid valve (18) and a flow restrictor (19), which is preferably designed as a supercritical nozzle. 20. Partikelfiltersystem nach einem der Ansprüche 7 bis 16,
dadurch gekennzeichnet, daß die Gasleitung (4) über ein Magnetventil (16) mit der Abgasleitung (10) verbunden ist, und daß in Strömungsrichtung hinter dem Abzweig der Lei­tung (4) in der Abgasleitung (10) eine Drosselklappe (17) angeordnet ist.20. Particulate filter system according to one of claims 7 to 16,
characterized in that the gas line (4) is connected to the exhaust line (10) via a solenoid valve (16) and in that a throttle valve (17) is arranged in the flow direction behind the branch of the line (4) in the exhaust line (10).
EP89120374A 1988-11-04 1989-11-03 Particle filter system Expired - Lifetime EP0367280B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89120374T ATE79921T1 (en) 1988-11-04 1989-11-03 PARTICULATE FILTER SYSTEM.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3837472 1988-11-04
DE3837472A DE3837472C2 (en) 1988-11-04 1988-11-04 Particulate filter system

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EP0367280A1 true EP0367280A1 (en) 1990-05-09
EP0367280B1 EP0367280B1 (en) 1992-08-26
EP0367280B2 EP0367280B2 (en) 1998-04-08

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EP (1) EP0367280B2 (en)
AT (1) ATE79921T1 (en)
CA (1) CA2002331A1 (en)
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DE3837472A1 (en) 1990-05-10
CA2002331A1 (en) 1990-05-04
EP0367280B1 (en) 1992-08-26
DE58902147D1 (en) 1992-10-01
ATE79921T1 (en) 1992-09-15
EP0367280B2 (en) 1998-04-08
DE3837472C2 (en) 1998-09-24
US5094075A (en) 1992-03-10

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