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WO2008145503A1 - Système de recyclage des gaz d'échappement pour moteur à combustion interne suralimenté - Google Patents

Système de recyclage des gaz d'échappement pour moteur à combustion interne suralimenté Download PDF

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Publication number
WO2008145503A1
WO2008145503A1 PCT/EP2008/055734 EP2008055734W WO2008145503A1 WO 2008145503 A1 WO2008145503 A1 WO 2008145503A1 EP 2008055734 W EP2008055734 W EP 2008055734W WO 2008145503 A1 WO2008145503 A1 WO 2008145503A1
Authority
WO
WIPO (PCT)
Prior art keywords
fresh gas
internal combustion
combustion engine
valve
exhaust gas
Prior art date
Application number
PCT/EP2008/055734
Other languages
German (de)
English (en)
Inventor
Adam Loch
Original Assignee
Mahle International 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
Priority claimed from DE102007025179A external-priority patent/DE102007025179A1/de
Application filed by Mahle International Gmbh filed Critical Mahle International Gmbh
Publication of WO2008145503A1 publication Critical patent/WO2008145503A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/109—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps having two or more flaps
    • 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
    • F02B29/08—Modifying distribution valve timing for charging purposes
    • F02B29/083—Cyclically operated valves disposed upstream of the cylinder intake valve, controlled by external means
    • 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
    • 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
    • F02M26/40—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with timing means in the recirculation passage, e.g. cyclically operating valves or regenerators; with arrangements involving pressure pulsations
    • 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
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/10209—Fluid connections to the air intake system; their arrangement of pipes, valves or the like
    • F02M35/10222—Exhaust gas recirculation [EGR]; Positive crankcase ventilation [PCV]; Additional air admission, lubricant or fuel vapour admission
    • 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
    • F02B29/0437—Liquid cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F02D2009/0201—Arrangements; Control features; Details thereof
    • F02D2009/0272—Two or more throttles disposed in series
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0025—Controlling engines characterised by use of non-liquid fuels, pluralities of fuels, or non-fuel substances added to the combustible mixtures
    • F02D41/0047—Controlling exhaust gas recirculation [EGR]
    • F02D41/0065—Specific aspects of external EGR control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/04—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning exhaust conduits
    • 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
    • F02M26/14—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system
    • F02M26/15—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system in relation to engine exhaust purifying apparatus
    • 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
    • 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 present invention relates to an internal combustion engine system, in particular in a motor vehicle.
  • an internal combustion engine system includes an internal combustion engine, e.g. a diesel engine or a gasoline engine, a fresh gas system for supplying fresh gas to the internal combustion engine, an exhaust system for discharging exhaust gas from the internal combustion engine, and an exhaust gas recirculation system for removing exhaust gas from the exhaust system and for introducing the exhaust gas taken into the fresh gas system.
  • the exhaust gas recirculation is performed to lower the pollutant emission and fuel consumption values of the internal combustion engine.
  • the present invention is concerned with the problem of providing for an internal combustion engine system of the type mentioned in an improved embodiment, which is characterized in particular by an improved exhaust gas recirculation.
  • the invention is based on the general idea to arrange in the fresh gas system upstream and downstream of the discharge point each a fresh gas valve for controlling a flow-through cross section of the fresh gas system.
  • each a fresh gas valve for controlling a flow-through cross section of the fresh gas system.
  • the two Frischgasventilen arranged on both sides of the discharge point can be generated by appropriate control of the fresh gas valves in the region of the discharge pressure oscillations having relatively large negative amplitudes.
  • the pressure difference between the discharge point and removal point can be selectively increased and in particular be set to a desired differential pressure value in order to realize a desired exhaust gas recirculation rate.
  • an improved mixing between fresh gas and recirculated exhaust gas can be achieved between the two fresh gas valves, which has an advantageous effect on the operation of the internal combustion engine.
  • both fresh gas valves are controlled to generate pressure oscillations in the fresh gas.
  • both fresh gas valves are controlled to generate pressure oscillations in the fresh gas.
  • Fig. 1 shows a circuit diagram-like schematic diagram of an internal combustion engine system.
  • an internal combustion engine system 1 which can be arranged in particular in a motor vehicle, an internal combustion engine 2, a fresh gas system 3, an exhaust system 4 and an exhaust gas recirculation system 5.
  • the engine system 1 may have a Kraftstoffein- injection system.
  • the internal combustion engine 2 may be a diesel engine or a gasoline engine or the like.
  • the internal combustion engine 2 can be designed as a pure naturally aspirated engine or - as here - as a supercharged engine.
  • the internal combustion engine system 1 is additionally equipped, for example, with an exhaust gas turbocharger 6, the turbine 7 of which is arranged in the exhaust system 4 and the compressor 8 in the fresh gas system 3.
  • the internal combustion engine 2 has an engine block with cylinders which contain combustion chambers in which the combustion reactions take place during operation of the internal combustion engine 2 and the exhaust gas is produced.
  • the fuel injection system is used for supplying fuel to the combustion chambers of the internal combustion engine 2. It can be configured in particular as a common rail system and / or have a plurality of fuel injectors.
  • the fresh gas system 3 serves to supply fresh gas, which is preferably air, to the internal combustion engine 2.
  • the fresh gas system 3 has a fresh gas line 9, which is connected to the internal combustion engine 2 or to the engine.
  • Torblock is connected and is arranged in the present case, the compressor 8.
  • the exhaust system 4 serves to discharge exhaust gas from the internal combustion engine 2.
  • the exhaust system 4 comprises an exhaust pipe 10 which is connected to the internal combustion engine 2 or to the engine block and which contains the turbine 7 in the present case.
  • the exhaust gas recirculation system 5 is configured to remove exhaust gas from the exhaust system 4 at a removal point 11 and to introduce this removed exhaust gas at a discharge point 12 into the fresh gas system 3.
  • the exhaust system 5 an exhaust pipe 13 which is connected on the one hand via the removal point 11 to the exhaust pipe 10 and on the other hand via the discharge point 12 to the fresh gas line 9.
  • a first fresh gas valve 14 is arranged in the fresh gas line 3 or in the fresh gas line 9 upstream of the discharge point 12, with which a flow-through cross section of the fresh gas system 3 can be controlled.
  • a second fresh gas valve 15 is arranged in the fresh gas system 3 or in the fresh gas line 9 downstream of the discharge point 12, which is also configured to control a flow-through cross section of the fresh gas system 3.
  • the controllable through the cross section with the help of the respective Frischgasventils 14,15teurströmbare cross section through a line cross section 16 of the fresh gas line 9 upstream of the first fresh gas valve 14 or by a line cross section 17 of the fresh gas line 9 downstream of the discharge point 12 or downstream of the second fresh gas valve 15 may be formed.
  • the cross section controllable with the aid of the respective gas valve 14, 15 can be a cross section in the interior of the respective fresh gas valve 14, 15, which can be formed in a region of the respective fresh gas valve 14, forming a section of the fresh gas line 9.
  • the fresh gas system 3 may have a heat exchanger 18, which is integrated in a cooling circuit 19.
  • this heat exchanger 18 is in particular a so-called intercooler.
  • this heat exchanger 18 is disposed downstream of the introduction point 12 and downstream of the second fresh gas valve 15.
  • the cooling circuit 19 may be, for example, the cooling circuit of the internal combustion engine 2.
  • a return valve 20 can be arranged upstream of the introduction point 12, with which a flow-through cross section of the exhaust gas recirculation system 5 or the return line 13 can be controlled.
  • the return valve 20 can be a passively operating, simple non-return check valve, in order to avoid erroneous flows of fresh gas in the direction of the exhaust system 4.
  • the return valve 20 may be an actively controllable valve.
  • the abstraction Gas recirculation system 5 also equipped with a heat exchanger 21, which is also involved in a cooling circuit, which may in principle be the same cooling circuit 19, in which also the optional heat exchanger 18 is integrated.
  • the heat exchanger 21 is thus integrated into the cooling circuit of the internal combustion engine 2.
  • the heat exchanger 21 is arranged upstream of the return valve 20 in the exhaust gas recirculation system 5 or in the return line 13.
  • the exhaust system 4 has upstream of the removal point 11, a component 22, which may preferably be a particulate filter. This ensures that only purified exhaust gases are recycled to the fresh gas system 3.
  • the component 22 may be a basically any other component of the exhaust system 4, such as e.g. a catalyst or silencer.
  • the exhaust system 4 can optionally have an exhaust valve 23, which is arranged downstream of the removal point 11 in the exhaust system 4 or in the exhaust line 10 and with which a cross-section of the exhaust system 4 can be controlled.
  • a control 24 is provided, which is connected via corresponding control lines 25 with the fresh gas valves 14,15.
  • the controller 24 is expediently provided for actuating the respective valve 20,23.
  • the controller 24 may communicate with a motor controller such that the controller 24 knows the current operating state of the internal combustion engine 2 or knows the exhaust gas recirculation quantity dependent on the current operating state of the internal combustion engine 2.
  • the controller 24 operates the valves 14, 15, 20, 23 depending on the current Laczu ⁇ stands of the engine 2 and to generate the currently required exhaust gas recirculation amount.
  • the controller 24 may now be configured such that it controls at least one of the two fresh gas valves 14, 15 to lower the pressure in the fresh gas in the region of the introduction point 12. This is achieved, for example, by closing the first fresh gas valve 14.
  • the controller 24 controls at least one of the fresh gas valves 14,15 for generating pressure oscillations in the fresh gas. Pressure oscillations can be generated in the fresh gas flow by periodically opening and closing the respective fresh gas valve 14, 15, wherein flow dynamic effects are utilized. These pressure oscillations have negative amplitudes in which the pressure in the fresh gas drops below the pressure in the exhaust gas which prevails in the exhaust gas recirculation system 5 in the region of the introduction point 12.
  • the controller 24 may in principle be designed so that it controls both fresh gas valves 14,15 for generating the pressure oscillations in the fresh gas.
  • a targeted tuning of the actuation processes and the positioning of the fresh gas valves 14,15 relative to the discharge point 12 can be achieved in terms of absolute value relatively large negative amplitudes within the pressure oscillations.
  • controller 24 it is also possible to design the controller 24 so that it controls only one of the fresh gas valves 14, 15 for generating pressure oscillations in the fresh gas, while it controls the respective other fresh gas valve 14, 15 for amplifying negative amplitudes of the pressure oscillations in the region of the introduction point 12 ,
  • the controller 24 controls only one of the fresh gas valves 14, 15 for generating pressure oscillations in the fresh gas, while it controls the respective other fresh gas valve 14, 15 for amplifying negative amplitudes of the pressure oscillations in the region of the introduction point 12 .
  • the controller 24 controls only one of the fresh gas valves 14, 15 for generating pressure oscillations in the fresh gas, while it controls the respective other fresh gas valve 14, 15 for amplifying negative amplitudes of the pressure oscillations in the region of the introduction point 12 .
  • the controller 24 controls only one of the fresh gas valves 14, 15 for generating pressure oscillations in the fresh gas, while it controls the respective other fresh gas valve 14, 15 for amplifying negative amplitudes of the pressure oscillation
  • At least one of the fresh gas valves 14,15 may be configured as a discontinuous working valve.
  • both fresh gas valves 14,15 are designed as discontinuously operating valves.
  • a valve member e.g. a butterfly flap, with preferably opposite directions of movement at least between two predetermined control positions switchable.
  • a discontinuously operating fresh gas valve 14, 15 may have, for example as a valve member, a flap pivotable about an axis of rotation, which can be switched between a closed position and an open position.
  • the valve member rotates when closing preferably in one direction of rotation and when opening in the other direction.
  • it is characteristic of a discontinuously operating valve that the respective valve member remains in the respectively set control position for a certain time, so that the valve member is in motion only in the time-limited, fast-running switching operations.
  • At least one of the fresh gas valves 14, 15 may be a continuously operating valve.
  • both fresh gas valves 14,15 are designed as continuously operating valves.
  • At a continuously operating valve passes through the respective valve member with the same direction of movement at least two different control positions.
  • a continuously operating fresh gas valve 14, 15 may have, for example, a flap or a rotary valve as a valve member which can be driven to rotate about a rotational axis. Characterizing here is for the continuously operating fresh gas valve 14, 15, that the respective valve member rotates in the operation of the valve permanently with the same direction of rotation and thereby passes at a predetermined, but in particular variable, rotational speed, for example, a closing angle range and an opening angle range.
  • At least one of the fresh gas valves 14, 15 may be configured as a fast-switching valve.
  • both fresh gas valves 14, 15 configured as fast-switching valves.
  • the respective desired change in the flow-through cross section of the fresh gas system 3 can be realized within relatively short switching times or control times.
  • the fresh gas valve 14, 15 are adjusted in the millisecond range between a blocking position or a position with a minimum flow-through cross section and an open position or a position with a maximum open cross-section.
  • the fast-switching fresh gas valve 14, 15 can be switched in the same frequency range, in which the charge cycle operations of the internal combustion engine 2 take place.
  • a synchronization of the respective fresh gas valve 14, 15 can be adapted to pressure fluctuations in the fresh gas, which occur anyway due to the gas exchange processes in the fresh gas system 3. For example, this pressure amplitudes in the oscillating fresh gas flow can be selectively increased.
  • both fresh gas valves 14, 15 designed to be dynamically controlled.
  • the respective fresh gas valve 14, 15 can thereby be actuated dynamically as a function of the rotational speed and / or the load of the internal combustion engine 2.
  • the controller 24 may be coupled to an engine control, not shown here, or integrated into it.
  • the return valve 20 can be used.
  • positive pressure amplitudes may also occur in the region of the introduction point 12, in which the pressure in the fresh gas may exceed the pressure in the exhaust gas at the removal point 11.
  • the return valve 20 may be configured as a passive non-return valve.
  • the return valve 20 if it is designed as an actively operating switching valve, the exhaust gas recirculation system 5 or its return line 13 in the vicinity of the discharge point 12 to prevent unwanted backflows.
  • the return valve 20 can be controlled to generate pressure oscillations in the exhaust gas, which can be coupled in a suitable manner with the pressure oscillations in the fresh gas in order to additionally improve the exhaust gas recirculation.
  • the exhaust valve 23 may be provided and be controlled to improve the exhaust gas recirculation. For example, by throttling the exhaust pipe 10 upstream of the exhaust valve 23, the pressure in the exhaust gas can be increased, which reduces the pressure gradient between see withdrawal point 11 and discharge point 12 increased. Likewise, with the help of the exhaust valve 23 can generate pressure oscillations in the exhaust gas, which are tuned to the pressure oscillation in the fresh gas, thereby the exhaust gas recirculation can be increased.
  • the exhaust gas valve 23 and / or the recirculation valve 20, like the fresh gas valves 14, 15, can be configured as dynamically controllable valves and / or as high-speed valves and / or as valves operating continuously or discontinuously.
  • the controller 24 may be provided to design the controller 24 in such a way that it activates the fresh gas valves 14, 15 in such a way that a negative pressure is established in a volume located between the two fresh gas valves 14, 15. gas recirculation system 5 more or less can be compensated.
  • the controller 24 may be provided to design the controller 24 in such a way that it activates the fresh gas valves 14, 15 in such a way that a negative pressure is established in a volume located between the two fresh gas valves 14, 15. gas recirculation system 5 more or less can be compensated.
  • the controller 24 may be provided to design the controller 24 in such a way that it activates the fresh gas valves 14, 15 in such a way that a negative pressure is established in a volume located between the two fresh gas valves 14, 15. gas recirculation system 5 more or less can be compensated.
  • the controller 24 may be provided to design the controller 24 in such a way that it activates the fresh gas valves 14, 15 in such a way that a negative pressure is established in a volume located
  • the inlet chamber 26 is characterized in that on the one hand it has the point of introduction 12 and on the other hand has a chamber cross section 27 which is larger than the line cross sections 16, 17 of the fresh gas line 9 upstream or downstream of the inlet chamber 26 Help such an introduction chamber 26, which increases the volume between the two fresh gas valves 14, 15, the exhaust gas recirculation can be realized more uniformly. Likewise, more exhaust gas can be recycled within a shorter time, which favors the utilization of negative pressure amplitudes occurring only for a short time.
  • the amount of exhaust gas flowing into the introduction chamber 26 can be controlled by means of the controller 24 by corresponding actuations of the return valve 20.
  • a lead body 28 is disposed in the introduction chamber 26.
  • This has a perforated wall 29, for example of a perforated plate, and a body cross-section 30.
  • the conduit body 28 bounded inside the inlet chamber 26 by means of its perforated wall 29 an annular space 31 against an interior 32. While the interior 32 a from the first fresh gas valve 14 for The second fresh gas valve 15 forms the leading gas path, the annular space 31 communicates with the point of introduction 12.
  • the inlet chamber 26 may form a certain flow resistance for the fresh gas due to its opposite the line cross sections 16, 17 enlarged chamber cross section. With the help of the line body 28, this flow resistance for the fresh gas flow in the fresh gas line 9 can be reduced.
  • the perforated wall 29 ensures the supply of recirculated exhaust gas to the fresh gas flow.
  • the line body 28 is configured such that its body cross section 30 corresponds to the respective line cross section 16, 17.
  • the two line cross sections 16, 17 are the same size.
  • the body cross section 30 is then also the same size and also constant.
  • the fresh gas system 3 comprises a line section 33 which contains the inlet point 12 and the two fresh gas valves 14, 15.
  • This line section 33 is configured as a separately producible unit, which is completely assembled, in particular in the context of pre-assembly.
  • the line section 33 is installed, for example via corresponding flanges 34 in the fresh gas system 3 and in the rest of the fresh gas line 9 and, for example. connected via a corresponding connecting piece 35 in the region of the point of introduction 12 to the exhaust gas recirculation system 5 and at the return line 13.

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

Abstract

La présente invention concerne un système de moteur à combustion interne (1), notamment dans un véhicule à moteur, comprenant un moteur à combustion interne (2), un système d'admission (3) destiné à alimenter en gaz frais le moteur à combustion interne (2), un système d'échappement (4), destiné à évacuer les gaz d'échappement du moteur à combustion interne (2), ainsi qu'un système de recyclage des gaz d'échappement (5), destiné à prélever les gaz d'échappement du système d'échappement (4) et à injecter les gaz d'échappement prélevés dans le système d'admission (3) en un point d'injection (12). L'objectif de l'invention est d'améliorer le recyclage des gaz d'échappement. A cet effet, le système d'admission (3) présente, en amont du point d'injection (12), une première soupape d'admission (14), permettant de commander une section d'écoulement du système d'admission (3), et, en aval dudit point d'injection (12), une seconde soupape d'admission (15), permettant de commander une section d'écoulement du système d'admission (3).
PCT/EP2008/055734 2007-05-29 2008-05-09 Système de recyclage des gaz d'échappement pour moteur à combustion interne suralimenté WO2008145503A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007025179.5 2007-05-29
DE102007025179A DE102007025179A1 (de) 2007-02-23 2007-05-29 Brennkraftmaschinensystem

Publications (1)

Publication Number Publication Date
WO2008145503A1 true WO2008145503A1 (fr) 2008-12-04

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PCT/EP2008/055734 WO2008145503A1 (fr) 2007-05-29 2008-05-09 Système de recyclage des gaz d'échappement pour moteur à combustion interne suralimenté

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WO (1) WO2008145503A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110139134A1 (en) * 2009-12-12 2011-06-16 Elsaesser Alfred Internal combustion engine system and associated operating method
WO2011077069A1 (fr) * 2009-12-22 2011-06-30 Perkins Engines Company Limited Période de transition pour l'aide à la régénération
EP2418369A1 (fr) * 2010-08-13 2012-02-15 Nederlandse Organisatie voor toegepast -natuurwetenschappelijk onderzoek TNO Système de contrôle de la température de gaz d'échappement d'un moteur à combustion interne avec un dispositif de post-traitement de gaz d'échappement et moteur d'entraînement l'incluant
US8291881B2 (en) 2009-12-22 2012-10-23 Perkins Engine Company Limited Piston for internal combustion engine
US8776501B2 (en) 2009-12-22 2014-07-15 Perkins Engines Company Limited Regeneration assist calibration

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EP1420159A2 (fr) * 2002-11-15 2004-05-19 Isuzu Motors Limited Système d'EGR pour un moteur à combustion interne ayant un turbocompresseur à suralimentation
EP1712760A2 (fr) * 2005-04-13 2006-10-18 Ricardo, Inc. Commande variable et indirecte de soupape pour un moteur à combustion interne
WO2006129371A1 (fr) * 2005-06-03 2006-12-07 Hitachi, Ltd. Melangeur de gaz egr
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110139134A1 (en) * 2009-12-12 2011-06-16 Elsaesser Alfred Internal combustion engine system and associated operating method
EP2333289A3 (fr) * 2009-12-12 2013-09-04 MAHLE International GmbH Système moteurs à combustion interne et procédé de fonctionnement associé
US8701637B2 (en) 2009-12-12 2014-04-22 Mahle International Gmbh Internal combustion engine exhaust gas recirculation apparatus and method of operation
WO2011077069A1 (fr) * 2009-12-22 2011-06-30 Perkins Engines Company Limited Période de transition pour l'aide à la régénération
US8291881B2 (en) 2009-12-22 2012-10-23 Perkins Engine Company Limited Piston for internal combustion engine
US8776501B2 (en) 2009-12-22 2014-07-15 Perkins Engines Company Limited Regeneration assist calibration
EP2418369A1 (fr) * 2010-08-13 2012-02-15 Nederlandse Organisatie voor toegepast -natuurwetenschappelijk onderzoek TNO Système de contrôle de la température de gaz d'échappement d'un moteur à combustion interne avec un dispositif de post-traitement de gaz d'échappement et moteur d'entraînement l'incluant
WO2012021061A1 (fr) * 2010-08-13 2012-02-16 Nederlandse Organisatie Voor Toegepast-Natuurwetenschappelijk Onderzoek Tno Système permettant de réguler la température du gaz d'échappement d'un moteur à combustion interne doté d'un dispositif de post-traitement de gaz d'échappement, et moteur d'entraînement comprenant ce système

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