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WO2019016331A1 - Système de recirculation des gaz d'échappement à refroidissement à eau - Google Patents

Système de recirculation des gaz d'échappement à refroidissement à eau Download PDF

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Publication number
WO2019016331A1
WO2019016331A1 PCT/EP2018/069675 EP2018069675W WO2019016331A1 WO 2019016331 A1 WO2019016331 A1 WO 2019016331A1 EP 2018069675 W EP2018069675 W EP 2018069675W WO 2019016331 A1 WO2019016331 A1 WO 2019016331A1
Authority
WO
WIPO (PCT)
Prior art keywords
egr
cooling fluid
injection valve
fluid injection
line
Prior art date
Application number
PCT/EP2018/069675
Other languages
German (de)
English (en)
Inventor
Michael Fischer
Philipp KREUTZIGER
Yong Sun
Dipankar SAHOO
Original Assignee
Tenneco Gmbh
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 Tenneco Gmbh filed Critical Tenneco Gmbh
Publication of WO2019016331A1 publication Critical patent/WO2019016331A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/35—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with means for cleaning or treating the recirculated gases, e.g. catalysts, condensate traps, particle filters or heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/33—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage controlling the temperature of the recirculated gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers

Definitions

  • the invention relates to an EGR system with an EGR line, an EGR cooler within the EGR line and an EGR valve on the EGR line and with at least one injection valve for a cooling medium for supplying the recirculated exhaust gas with a cooling fluid.
  • EGR system with an EGR line, an EGR cooler within the EGR line and an EGR valve on the EGR line and with at least one injection valve for a cooling medium for supplying the recirculated exhaust gas with a cooling fluid.
  • These can include z.
  • the EGR system is an exhaust gas recirculation line.
  • An EGR system typically consists of at least one exhaust gas recirculation (EGR) line branching off the exhaust line and flowing into the intake manifold, an exhaust gas recirculation (EGR) cooler within the EGR passage and an exhaust gas recirculation damper (EGR) the AGR line.
  • EGR exhaust gas recirculation
  • HP-EGR high-pressure EGR
  • LP-EGR low-pressure EGR
  • MP-EGR maximum-pressure EGR
  • the EGR line opens downstream of the compressor.
  • the EGR line flows upstream of the compressor.
  • a particulate filter is specified in particular in that particles which are larger than 15-25 nm and in particular larger than 10 nm are retained. Ideally, the retained particle sizes could become even smaller.
  • the particulate filter may have a catalytically active coating to avoid soiling such as fouling by HC and / or NOx and to improve the purity of the EGR system. This has an advantageous effect on the effectiveness of the system.
  • the water is used initially for cleaning the EGR cooler, but also for cooling the recirculated exhaust gas and for EGR supplementation.
  • FR 2 993 933 A1 describes a WGS system in which water vapor is catalyzed by means of the catalyst for the generation of hydrogen.
  • the recirculated, hydrogen-enriched exhaust gas is cooled by means of the cooler.
  • DE 10 2015 108 224 A1 describes a classic EGR system with various EGR variants, a high-pressure EGR and a plurality of low-pressure EGR variants.
  • a particle filter is arranged within the respective EGR line.
  • the particulate filter in the high-pressure EGR has a catalytic coating for the conversion of HC, CO and NOx.
  • the particle filter is preceded by a 3-way catalytic converter.
  • EP 3 098 406 A1 describes an EGR system using water for cleaning.
  • WO 2014/080266 A1 likewise discloses an EGR system.
  • the recirculated exhaust gas is supplied in the intake manifold with water.
  • the object of the invention is to design and arrange an EGR system such that improved and more efficient cooling of the recirculated exhaust gas is possible.
  • the object is achieved according to the invention in that a particle filter is provided, which is placed upstream of the cooling fluid injection valve, wherein the at least one cooling fluid injection valve is placed upstream of the EGR cooler with a distance a to the EGR cooler.
  • a particle filter is provided, which is placed upstream of the cooling fluid injection valve, wherein the at least one cooling fluid injection valve is placed upstream of the EGR cooler with a distance a to the EGR cooler.
  • further flow elements such as mixers and / or evaporators can be used to increase the evaporation of the injected water without fear of disadvantageous deposit formation on these components.
  • the aforementioned EGR system and the associated EGR cooling are applicable to a gasoline engine and also to a diesel engine. It may also be advantageous for this purpose if the at least one cooling fluid injection valve is placed with an injection axis within the EGR line.
  • placement within the EGR duct placement within the damper housing of the EGR damper or within the filter housing of the particulate filter is also possible.
  • various evaporator elements and / or mixer elements placed in the EGR passage may be directly supplied with coolant or may be in direct communication with the exhaust flow enriched with coolant.
  • the advantages according to the invention relating to an improved, thus optimal cooling of the recirculated exhaust gas are advantageous.
  • such an advantageous cooling by application of the cooling according to the invention can also find application for a low-pressure EGR or a maximum pressure EGR.
  • the EGR line is formed catalyst-free, thus no further catalyst in the EGR line or the exhaust pipe is provided.
  • the EGR passage opens into the intake passage upstream of the intake manifold.
  • the particulate filter has a filter housing which is connected to the EGR line via a connection zone, wherein at least one cooling fluid injection valve is placed in the filter housing downstream of the particulate filter or in the connection zone.
  • the EGR flap has a flap housing, via which the EGR flap is connected to the EGR line, wherein at least one cooling fluid injection valve is placed in the valve housing.
  • the line cross-section in the injection region is increased in order to reduce the local gas flow velocity and thus increase the residence time / evaporation time.
  • an extended line cross section or flow cross section is applicable.
  • the significantly reduced flow velocity ensures a longer residence time of the coolant.
  • the introduction or distribution and evaporation of injected coolant, in particular water can advantageously be carried out.
  • the latter also applies to extended flow cross-sections relating to the particle filter housing.
  • the line cross-section in the injection area is increased in order to reduce the local gas flow rate and thus to increase the residence time / evaporation time.
  • the injection can be carried out so that an impact of the injected fluid is avoided or kept low on cold outer or housing walls.
  • the internal components are structured or have a particular surface texture or roughness to maximize heat exchange between the cooling fluid and the exhaust gas flow.
  • the heating is produced by microwave, UV or plasma radiation.
  • turbulence generating means may be provided on the outer walls, which allow a separation of the flow from the respective wall.
  • the cooling fluid injection valve is placed such that the particle filter or the particle filter substrate is wetted on the back.
  • the particle filter is in this case wetted on the back side in the region of the flow outlet.
  • the cooling fluid injection valve has at least one injection nozzle which ensures an average cooling fluid droplet size of at most 10 to 100 micrometers.
  • the smallest possible droplet size is advantageous for the achievable evaporation rate of the added or injected cooling fluid.
  • the relevant part of the cooling fluid evaporates before it enters the EGR cooler, so that according to the invention the cooling power to be provided by the EGR cooler is lower or the EGR temperature achieved thereby is minimized.
  • the injection axis of at least one part of the cooling fluid injection valves is aligned at right angles or radially to an exhaust gas main flow direction V and / or if the injection axis of at least a part of the cooling fluid injection valves is opposite to the main exhaust gas flow direction V is aligned.
  • the radial or oppositely directed injection nozzle can achieve an increased degree of evaporation of the cooling fluid. The latter, in particular, because the supplied cooling liquid droplets have an increased acceleration process with regard to the relative speed to the EGR exhaust gas flow. It may be advantageous if the particulate filter has a 3-way catalyst coating, which HC and CO oxidizable and NOx is reduced.
  • the distance a of the cooling fluid injection valve to the EGR cooler and / or the placement of the cooling fluid injection valve along the EGR line and / or the placement of the cooling fluid injection valve on the filter housing and / or the placement of the cooling fluid injection valve on the valve body and / or the selection of the evaporator elements of the type are designed according to such that with respect to the registered by the cooling fluid injection valve Cooling fluid or water, a vaporization rate of at least 20% to 30%, preferably of at least 80% to 90% is reached before the treated with cooling fluid or water exhaust gas reaches the EGR cooler.
  • the input cooling fluid is used to cool the EGR exhaust gas flow.
  • a cleaning of the downstream cooler by means of added fluid such as water is not necessary because the exhaust gas is already cleaned against the background of the upstream particle filter. Against this background, a slight cooling fluid excess, and therefore an evaporation rate of less than 100%, makes sense, in order to achieve an evaporation buffer, and thus always a maximum evaporation capacity overall. An excessive cooling fluid excess, which is ultimately led into the EGR cooler, but just is not necessary.
  • a cooling fluid mass flow c is introduced by the cooling fluid injection valve and an exhaust gas mass flow e is conducted in the EGR line, wherein for a ratio R between the cooling fluid mass flow c and the exhaust gas mass flow e is:
  • the quantity ratio of cooling fluid or water vapor on the one hand and exhaust gas on the other hand is based on moles.
  • Figure 1 is a schematic diagram of an exhaust system of an engine with HP and
  • FIG. 2a-6 Schematic diagrams of parts of the EGR pipe with corresponding
  • An exhaust system 5.2 shown in FIG. 1 is associated with an internal combustion engine 5.1 and has a compressor 5.4 and a turbine 5.5, a fresh air cooler 5.3 arranged downstream of the compressor 5.4 in the fresh air line and a throttle valve 5.8 and a 3-way catalytic converter 5.6 and a particle filter 5.7 in FIG the main exhaust gas line.
  • a high pressure EGR system 1 and a low pressure EGR system 1 ' are also shown.
  • an EGR line 1.1 branches off upstream of the turbine 5.5 and discharges in the fresh air line downstream of the compressor 5.4.
  • a particle filter 3 and downstream of the particle filter 3 are arranged within the EGR line 1.1.
  • a cooling fluid injection valve 2.1 Downstream of valve 2.1 is provided an EGR Radiator 1.2, to which an EGR valve 1.3 connects, the latter upstream of the mouth of the EGR line 1.1 in the fresh air line.
  • a low-pressure EGR line 1.1 ' branches off downstream of the turbine 5.5 and ends in the fresh air line upstream of the compressor 5.4. Also in the low-pressure EGR line 1.1 'are a particulate filter 3', a downstream cooling fluid injection valve 2.1 ', an EGR cooler 1.2' and an EGR valve 1.3 'are provided.
  • a plurality of cooling fluid injection valves 2.1, 2.2, 2.3 are provided in the EGR line 1.1 downstream of the particle filter 3, via which a cooling fluid, in particular water, is injected.
  • the respective cooling fluid injection valve 2.1, 2.2, 2.3 has an injection valve axis 2.1a, 2.2a, 2.3a, which is employed with respect to a main flow direction V of the exhaust gas flow at an angle of approximately 45 °. While the injection valve axis 2.1a extends in the direction of the main flow axis V with respect to said angle of attack, the injection valve axes 2.2a and 2.3a are arranged opposite to the main flow direction V.
  • the farthest downstream cooling fluid injection valve has a distance a to the EGR cooler .2 or its valve housing 1.4 with respect to an injection nozzle (not shown).
  • a connection zone 1.5 is provided, which is not taken into account in the determination of the distance a. In the case of consideration of such a connection zone 1.5, the distance a would be reduced accordingly.
  • the distance a should be at least 30 to 100 mm.
  • the cooling fluid injection valve 2.3 is also arranged in a connection zone 3.2 of the particle filter 3 backward part of the Particle filter 3 or its substrate occurs and is vaporized there via the effluent exhaust gas.
  • each evaporator element is also a mixer element, thus having a mixing effect and also each mixer element also has a further evaporation effect, so that regardless of the placement of Figure 2b and the graphic embodiment both evaporator elements and mixer elements are equivalent used.
  • an EGR valve 1.3 is additionally provided between the particulate filter 3 and the EGR cooler 1.2.
  • the EGR valve 1.3 is arranged in an EGR housing 1.4.
  • the cooling fluid injection valve 2.2 is provided on the flap housing 1.4 for the purpose of introducing cooling fluid into the area of the exhaust flap.
  • a further cooling fluid injection valve 2.3 is provided, which is also arranged on the valve housing 1.4.
  • the injection valve axis 2.2a likewise runs in the main flow direction V, while the injection valve axis 2.3a runs counter to the main flow direction V.
  • connection zone 3.2 of the particle filter 3 and in a corresponding connection zone (not further shown) of the flap housing 1.4 there is an enlarged flow cross-section compared to the EGR line 1.1, which is associated with a delayed or reduced flow velocity of the EGR gas , This is accompanied by an increased residence time of the cooling fluid injected there, which in turn leads to an improved evaporation rate of the same.
  • FIG. 3 b in contrast to exemplary embodiment FIG. 3 a, different evaporator elements 4. 1 or mixer elements 4. 2 are again provided within the EGR line.
  • Evaporator 4.1 On Evaporator 4.1 is located immediately downstream of the particulate filter 3, while a mixer element 4.2 is placed within the downstream EGR line l .1.
  • an evaporator element 4.1 is provided downstream of the EGR flap 1.3 and another mixer element 4.2 in the region of the connection zone 1.5 of the EGR cooler 1.2.
  • the distance a is defined by the distance of the most downstream cooling fluid injection valve 2.3 to the EGR cooler 1.2.
  • an evaporator element 4.1 of larger design is provided downstream of the particle filter 3.
  • This is an EGR line section, which causes a backflow with respect to the exhaust main flow V. Through this backflow (marked here by arrow), an increased flow path is generated, which in turn promotes the evaporation taking place in the exhaust gas.
  • two cooling fluid injection valves 2.1, 2.3 are provided, which are placed immediately downstream of the particulate filter 3.
  • the respective injection valve axis 2.1a, 2.3a runs at right angles or radially to the main flow direction V.
  • the evaporator element 4.1 is placed downstream of an EGR flap 1.3.
  • the evaporator element 4.1 has a common housing together with the EGR flap 1.3.
  • a cooling fluid injection valve 2.4 is provided downstream of the particulate filter 3 within a connection zone 3.2 of the same.
  • a cooling fluid injection valve 2.4 is provided with an injection valve axis 2.4a and also a cooling fluid injection valve 2.1 is provided in the exhaust valve housing.
  • Between the particle filter 3 and the EGR valve 1.3 are an evaporator element 4.1 and a mixer element 4.2.
  • Another mixer element 4.2 is placed in the EGR line 1.1 between the evaporator element 4.1 and the EGR cooler 1.2.
  • an injection zone is provided immediately downstream of the particle filter 3, formed by two cooling fluid injection valves 1, 2.2 whose injection valve axes 2.1a, 2.2a are arranged at right angles to the main flow direction V.
  • a conical or funnel-shaped mixer element 4.2 is provided within the connection zone 3.2 of a particulate filter housing 3.1.
  • a further evaporator element 4.1 is provided within the subsequent EGR line 1.1.
  • the distance a is also defined by the distance between the downstream cooling fluid injection valve and the EGR cooler 1.2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

L'invention concerne un système de recirculation des gaz d'échappement (1) pourvu d'une conduite (1.1) de recirculation des gaz d'échappement, d'un refroidisseur (1.2) de recirculation des gaz d'échappement à l'intérieur de la conduite (1.1) de recirculation des gaz d'échappement et d'un clapet (1.3) de recirculation des gaz d'échappement sur la conduite (1.1) de recirculation des gaz d'échappement et d'au moins une soupape d'injection de fluide de refroidissement (2.1) destinée à alimenter les gaz d'échappement amenés à recirculer en fluide de refroidissement. Un filtre à particules (3) est placé en amont de la soupape d'injection de fluide de refroidissement (2.1), la ou les soupapes d'injection de fluide de refroidissement (2.1) étant placées en amont du refroidisseur (1.2) de recirculation des gaz d'échappement à une distance a du refroidisseur (1.2) de recirculation des gaz d'échappement.
PCT/EP2018/069675 2017-07-20 2018-07-19 Système de recirculation des gaz d'échappement à refroidissement à eau WO2019016331A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017116353 2017-07-20
DE102017116353.0 2017-07-20

Publications (1)

Publication Number Publication Date
WO2019016331A1 true WO2019016331A1 (fr) 2019-01-24

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WO (1) WO2019016331A1 (fr)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0596855A1 (fr) * 1992-11-02 1994-05-11 AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH.Prof.Dr.Dr.h.c. Hans List Moteur à combustion interne à turbocompresseur à gaz d'échappement
US5785030A (en) * 1996-12-17 1998-07-28 Dry Systems Technologies Exhaust gas recirculation in internal combustion engines
DE112007000779T5 (de) * 2006-03-30 2009-04-16 Caterpillar Inc., Peoria Steuersystem und Steuerverfahren zur Abschätzung einer Turboladerleistung
FR2993933A1 (fr) 2012-07-26 2014-01-31 Peugeot Citroen Automobiles Sa Moteur a combustion interne muni d'un systeme de recirculation des gaz d'echappement a production d'hydrogene augmentee
WO2014080266A1 (fr) 2012-11-20 2014-05-30 Nostrum Energy Pte. Ltd. Système de recirculation des gaz d'échappement à refroidissement interne pour moteur à combustion interne, et procédé correspondant
DE102015119204A1 (de) 2014-11-11 2016-05-12 Ford Global Technologies, Llc Verfahren und system für egr-steuerung
DE102015108224A1 (de) 2014-12-17 2016-06-23 Tenneco Gmbh AGR-System mit Partikelfilter für Ottomotor
EP3098406A1 (fr) 2014-01-09 2016-11-30 Mitsubishi Heavy Industries, Ltd. Dispositif de traitement de gaz d'échappement, navire et procédé d'alimentation en eau
DE102016208208A1 (de) * 2016-05-12 2017-11-16 Volkswagen Aktiengesellschaft Verbrennungsmotor und Kraftfahrzeug

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0596855A1 (fr) * 1992-11-02 1994-05-11 AVL Gesellschaft für Verbrennungskraftmaschinen und Messtechnik mbH.Prof.Dr.Dr.h.c. Hans List Moteur à combustion interne à turbocompresseur à gaz d'échappement
US5785030A (en) * 1996-12-17 1998-07-28 Dry Systems Technologies Exhaust gas recirculation in internal combustion engines
DE112007000779T5 (de) * 2006-03-30 2009-04-16 Caterpillar Inc., Peoria Steuersystem und Steuerverfahren zur Abschätzung einer Turboladerleistung
FR2993933A1 (fr) 2012-07-26 2014-01-31 Peugeot Citroen Automobiles Sa Moteur a combustion interne muni d'un systeme de recirculation des gaz d'echappement a production d'hydrogene augmentee
WO2014080266A1 (fr) 2012-11-20 2014-05-30 Nostrum Energy Pte. Ltd. Système de recirculation des gaz d'échappement à refroidissement interne pour moteur à combustion interne, et procédé correspondant
EP3098406A1 (fr) 2014-01-09 2016-11-30 Mitsubishi Heavy Industries, Ltd. Dispositif de traitement de gaz d'échappement, navire et procédé d'alimentation en eau
DE102015119204A1 (de) 2014-11-11 2016-05-12 Ford Global Technologies, Llc Verfahren und system für egr-steuerung
DE102015108224A1 (de) 2014-12-17 2016-06-23 Tenneco Gmbh AGR-System mit Partikelfilter für Ottomotor
DE102016208208A1 (de) * 2016-05-12 2017-11-16 Volkswagen Aktiengesellschaft Verbrennungsmotor und Kraftfahrzeug

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