WO2007093195A1 - Procede de recirculation des gaz d'echappement dans un moteur a combustion interne equipe d'un turbocompresseur de suralimentation entraine par les gaz d'echappement - Google Patents

Procede de recirculation des gaz d'echappement dans un moteur a combustion interne equipe d'un turbocompresseur de suralimentation entraine par les gaz d'echappement Download PDF

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Publication number
WO2007093195A1
WO2007093195A1 PCT/EP2006/004135 EP2006004135W WO2007093195A1 WO 2007093195 A1 WO2007093195 A1 WO 2007093195A1 EP 2006004135 W EP2006004135 W EP 2006004135W WO 2007093195 A1 WO2007093195 A1 WO 2007093195A1
Authority
WO
WIPO (PCT)
Prior art keywords
exhaust gas
gas recirculation
turbine
internal combustion
combustion engine
Prior art date
Application number
PCT/EP2006/004135
Other languages
German (de)
English (en)
Inventor
Wolfram Schmid
Siegfried Sumser
Original Assignee
Daimlerchrysler Ag
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 Daimlerchrysler Ag filed Critical Daimlerchrysler Ag
Publication of WO2007093195A1 publication Critical patent/WO2007093195A1/fr

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Classifications

    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • 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
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
    • 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
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
    • 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
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • 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
    • 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
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a method for exhaust gas recirculation for an internal combustion engine with exhaust gas turbocharger according to the preamble of claim 1.
  • the turbine housing is formed double-flow.
  • the regulation of the exhaust gas supply to a turbine wheel of the exhaust gas turbine via an axial slide which can completely cover one of the floods, so that the exhaust gas supply takes place via an upstream flood connection via a single flood on the turbine wheel.
  • the slide is a simple sleeve without affecting the flow in terms of a variable turbine geometry.
  • Such control of the amount of exhaust gas is customary in the non-fired operating range of the internal combustion engine in which the internal combustion engine is to act as an engine brake (turbo brake).
  • the relatively low exhaust gas quantity in engine braking operation is supplied to the turbine wheel via the smaller flow, which is dimensioned correspondingly to the smaller exhaust gas flow with its inlet cross section, so that a relatively high rotational speed of the turbine wheel and a compressor connected to the turbine wheel via a shaft can be maintained. Due to the relatively high Speed of the compressor also results in the engine braking operation, a compression of the intake air and thus a corresponding engine braking performance.
  • turbocharger with a variable turbine geometry to adjust the flow to the turbine wheel accordingly.
  • the use of the variable turbine geometry for the purpose of the engine brake is known.
  • additional use of the variable turbine geometry for efficient exhaust gas recirculation is not known in order to be able to comply with future NOx limit values which require high exhaust gas recirculation rates of more than 50% even in the partial load range of the internal combustion engine.
  • the inventive method for exhaust gas recirculation for an internal combustion engine with exhaust gas turbocharger with the characterizing features of claim 1 has the advantage that with an existing variable turbine geometry of the exhaust gas turbine for the purpose of engine brake in a simple manner, an exhaust gas recirculation is feasible at the high exhaust gas recirculation rates of more than 50% can be accomplished.
  • the drawing shows in a schematically simplified, partial sectional view of an internal combustion engine 1, which is a diesel engine with engine brake, in particular for use for commercial vehicles, is.
  • the invention is in principle but also transferable to gasoline engines.
  • the internal combustion engine 1 has an exhaust gas turbocharger 2 with a turbine 3 in the exhaust gas line 4.
  • the turbine 3 has a turbine wheel 5, which is designed as a radial turbine and transmits the movement of the turbine wheel 5 via a shaft 7 to a compressor wheel 8 of a compressor 9.
  • the turbine 3 has a turbine housing 19, which is formed with two floods 14, 15 and inflow channels 16, 17, respectively.
  • the two floods 14, 15 and inflow channels 16, 17 are separated from each other by a housing-fixed partition wall 18 of the turbine housing 19.
  • each flood 14, 15 and inflow channel 16, 17, the exhaust gas can be supplied separately to the turbine wheel 5.
  • the exhaust gas feed takes place via the exhaust gas line 4, which is divided into two independently formed exhaust gas lines, a first exhaust gas line 20 and a second exhaust line 21 is.
  • the first exhaust gas line 20 is the first flow 14 and the second exhaust gas 21 is associated with the second flow 15.
  • Each exhaust pipe 20, 21 is associated with a defined number of cylinder outlets of the internal combustion engine 1.
  • the internal combustion engine 1 six cylinders, wherein a first cylinder bank 23, three cylinders and a second cylinder bank 24, also has three cylinders. It is conceivable in addition to the uniform distribution of the cylinder banks and a non-uniform.
  • the first exhaust pipe 20 leads from the cylinder bank 23 assigned here to the first inflow channel 16 of the first flow 14.
  • the second exhaust pipe 21 leads from the second cylinder bank 24 assigned to it to the second inflow duct 17 of the second flow 15.
  • a two exhaust gas lines 20, 21 connecting bridging line 25 is provided.
  • a first control element 30 is housed, which can control the exhaust gas flow in the bypass line 25.
  • the first control element 30 is designed, for example, as a flow-controlling valve (blow-by valve) or as an adjustable throttle body or flap.
  • a blow-off line 40 In the open position of the first control element 30, an overflow with pressure equalization between the exhaust gas lines 20, 21 is possible.
  • no pressure equalization takes place between the exhaust gas lines 20, 21 from the second exhaust gas line 21 to the turbine 3 branches off a blow-off line 40, in which a third control 33 is introduced, which also serves as the flow control valve or throttle body or Flap is formed.
  • the internal combustion engine 1 has an exhaust gas recirculation, which comprises a return line 35, optionally an exhaust gas cooler 36 and a second control element 32.
  • the second control element 32 can be designed as a flow-controlling valve (exhaust gas recirculation valve) or as a throttle element or flap and is arranged upstream of the first flow 14 and, for example, upstream of the exhaust gas cooler 36 in the return line 35.
  • a design of the second control element 32 is provided as a switching valve, which can not assume an intermediate position, but only an open and a closed position.
  • the return line 35 opens into an intake tract 6 of the internal combustion engine 1 downstream of a charge air cooler 37 for the intake air.
  • the intake duct 6 comprises the compressor 9 with the compressor wheel 8, the ambient air with the pressure pl sucks and compressed to an increased pressure p2. Downstream of the compressor 9, the charge air cooler 37 is arranged in the intake tract 6, through which the compressed air flows. After leaving the intercooler 37, the air on the boost pressure P 2 S, with which it is optionally introduced with mixed exhaust gas from the return line 35 into the cylinder inlet of the internal combustion engine 1.
  • the second, larger flood 15 is dimensioned or designed so that a desired charge pressure can be achieved in the fired operation.
  • the first, smaller tide 14 is dimensioned or designed so that a required exhaust gas recirculation rate can be achieved, whereby a certain engine braking power is ensured in engine braking operation.
  • the ratio of the inlet cross-section or shark cross-section of the first flood 14 per 1 1 stroke volume of the internal combustion engine 1 should be in a range of
  • the exhaust gas flow in the two differently sized flows 14, 15 of the asymmetrically designed turbine housing 19 can be controlled by a sleeve-shaped, axially movable slide 50.
  • the slider 50 has rigid vanes, which form a guide grid, to which the vanes are arranged distributed over the circumference accordingly.
  • Such a slider 50 is known for example from DE 198 16 645 Al, the disclosure of which is expressly part of the description.
  • the slider 50 is shown in its closed position indicated, in which at least both floods 14, 15 are covered by a Leitgitter Siemens of the slider 50.
  • the sleeve-shaped slide 50 surrounds with its Leitgitter Scheme the turbine wheel 5 and is previously inserted only in non-fired operation of the internal combustion engine more or less via an actuator 70 to selectively guide the amount of exhaust gas on the turbine wheel 5 via the Leitgitterschaufeln, creating an optimal adaptation of Amount of exhaust gas takes place, which leads to an increase in the exhaust gas turbocharger speed.
  • An increase in the exhaust gas turbocharger speed in turn leads to an increase in the Compressor capacity of the compressor and thus to increase the boost pressure p2s, which in turn increases the motor brake line in non-fired operation of the internal combustion engine 1.
  • the slide 50 with the guide grille also in the fired operation of the internal combustion engine or between the turbine wheel 5 and two floods 14, 15, in order then to set by the then increasing pressure before turbine 3 p31 and p32, which is larger as the boost pressure P2s, to obtain an effective, with high exhaust rates of more than 50% labeled exhaust gas recirculation.
  • the operation of the slider 50 is carried out in the usual manner by means of an actuator 70, z. B. by lever mechanism or electric, hydraulic or pneumatic actuator or the like.
  • the exhaust gas is introduced from the two exhaust gas lines 21, 22 with open first control element 30 and open second control element 32 via the return line 35 into the intake tract 6.
  • Exhaust gas recirculation can be carried out in the normal fired operation of the internal combustion engine from low to high speeds.
  • a guide grid 60 with adjustable guide vanes is known, for example, from DE 197 52 534 C1 or from DE 199 05 637 C1, the disclosure of which is expressly to be part of the application.
  • Similar to the valve solution is provided to narrow the guide vanes with the guide grid 60 by a corresponding actuator 70 in the fired operation of the internal combustion engine 1 in its flow area so that an increased back pressure before turbine 3 p31 and p32 results, which is greater than the boost pressure p2s.
  • exhaust gas recirculation is possible in the normal fired operation of the internal combustion engine from low to high speeds.
  • the actuation of the adjustable guide vanes of the guide grid 60 is carried out in the usual manner by means of an actuator 70, for. B. by lever mechanism or electric, hydraulic or pneumatic actuator or the like.
  • the exhaust gas is introduced from the two exhaust gas lines 21, 22 with open first control element 30 and open second control element 32 via the return line 35 into the intake tract 6.
  • Exhaust gas recirculation can be carried out in the normal fired operation of the internal combustion engine from low to high speeds.
  • the first control element 30 or the second control element 32 can also assume a corresponding flow position between an open position and a closed position. All control elements 30, 32, 33 can be adjusted to their desired position via control signals which can be generated in a regulating and control device (not shown in detail), for example an electronic engine control unit, in order to enable control of the flow rate.
  • control of the actuators 70 for the slide 50 or for the guide grid 60 with adjustable guide vanes is also possible via the regulating and control device.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

Pour pouvoir respecter les futures valeurs limites de NOx, l'invention propose un procédé de recirculation des gaz d'échappement pour un moteur à combustion interne (1) doté d'un turbocompresseur de suralimentation (2) entraîné par les gaz d'échappement. La turbine (3) entraînée par les gaz d'échappement comporte deux parcours d'écoulement (14, 15) séparés montés en amont de la roue (5) de la turbine (3) entraînée par les gaz d'échappement et tous deux reliés à un conduit (20, 21) de gaz d'échappement pour être alimentés en gaz d'échappement. Une géométrie variable (50; 60) de turbine envoie les gaz d'échappement dans la turbine (3) entraînée par les gaz d'échappement. Pour la recirculation des gaz d'échappement, une conduite de recirculation des gaz d'échappement (35) est réalisée par un élément de commande (32) pour amener les gaz d'échappement vers le conduit d'alimentation (6) du moteur à combustion interne (3).
PCT/EP2006/004135 2005-05-06 2006-05-03 Procede de recirculation des gaz d'echappement dans un moteur a combustion interne equipe d'un turbocompresseur de suralimentation entraine par les gaz d'echappement WO2007093195A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005021173.9 2005-05-06
DE102005021173A DE102005021173A1 (de) 2005-05-06 2005-05-06 Verfahren zur Abgasrückführung für eine Brennkraftmaschine mit Abgasturbolader

Publications (1)

Publication Number Publication Date
WO2007093195A1 true WO2007093195A1 (fr) 2007-08-23

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ID=36726309

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/004135 WO2007093195A1 (fr) 2005-05-06 2006-05-03 Procede de recirculation des gaz d'echappement dans un moteur a combustion interne equipe d'un turbocompresseur de suralimentation entraine par les gaz d'echappement

Country Status (2)

Country Link
DE (1) DE102005021173A1 (fr)
WO (1) WO2007093195A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT502997B1 (de) * 2005-12-20 2013-09-15 Man Truck & Bus Oesterreich Ag Vorrichtung zur steigerung der bremsleistung einer mehrzylindrigen brennkraftmaschine eines fahrzeugs während des motorbremsbetriebes
FR2945579B1 (fr) * 2009-05-15 2013-03-22 Inst Francais Du Petrole Procede et dispositif de controle de la quantite de gaz d'echappement recircules a l'admission d'un moteur a combustion interne suralimente
US8893493B2 (en) * 2010-01-14 2014-11-25 GM Global Technology Operations LLC Engine exhaust system and method of operation
DE102012014189A1 (de) 2012-07-18 2014-01-23 Mtu Friedrichshafen Gmbh Brennkraftmaschine mit Abgasturbolader

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4179892A (en) * 1977-12-27 1979-12-25 Cummins Engine Company, Inc. Internal combustion engine with exhaust gas recirculation
DE19857234A1 (de) * 1998-12-11 2000-06-29 Daimler Chrysler Ag Vorrichtung zur Abgasrückführung
DE10132672A1 (de) * 2001-07-05 2003-01-16 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine
DE10152804A1 (de) * 2001-10-25 2003-05-08 Daimler Chrysler Ag Brennkraftmaschine mit einem Abgasturbolader und einer Abgasrückführungsvorrichtung

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4179892A (en) * 1977-12-27 1979-12-25 Cummins Engine Company, Inc. Internal combustion engine with exhaust gas recirculation
DE19857234A1 (de) * 1998-12-11 2000-06-29 Daimler Chrysler Ag Vorrichtung zur Abgasrückführung
DE10132672A1 (de) * 2001-07-05 2003-01-16 Daimler Chrysler Ag Abgasturbolader für eine Brennkraftmaschine
DE10152804A1 (de) * 2001-10-25 2003-05-08 Daimler Chrysler Ag Brennkraftmaschine mit einem Abgasturbolader und einer Abgasrückführungsvorrichtung

Also Published As

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DE102005021173A1 (de) 2006-11-09

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