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WO2008145502A1 - Charge air valve system for use in an internal combustion engine - Google Patents

Charge air valve system for use in an internal combustion engine Download PDF

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Publication number
WO2008145502A1
WO2008145502A1 PCT/EP2008/055731 EP2008055731W WO2008145502A1 WO 2008145502 A1 WO2008145502 A1 WO 2008145502A1 EP 2008055731 W EP2008055731 W EP 2008055731W WO 2008145502 A1 WO2008145502 A1 WO 2008145502A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
fresh gas
internal combustion
combustion engine
exhaust gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/EP2008/055731
Other languages
German (de)
French (fr)
Inventor
Adam Loch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
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 DE102007025178.7A external-priority patent/DE102007025178B4/en
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of WO2008145502A1 publication Critical patent/WO2008145502A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • 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
    • 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
    • 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
    • F02M26/01—Internal exhaust gas recirculation, i.e. wherein the residual exhaust gases are trapped in the cylinder or pushed back from the intake or the exhaust manifold into the combustion chamber without the use of additional passages
    • 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
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D11/00—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated
    • F02D11/06—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance
    • F02D11/10—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type
    • F02D2011/101—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type characterised by the means for actuating the throttles
    • F02D2011/102—Arrangements for, or adaptations to, non-automatic engine control initiation means, e.g. operator initiated characterised by non-mechanical control linkages, e.g. fluid control linkages or by control linkages with power drive or assistance of the electric type characterised by the means for actuating the throttles at least one throttle being moved only by an electric actuator
    • 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
    • F02D2041/0017—Controlling intake air by simultaneous control of throttle and exhaust gas recirculation
    • 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
    • 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
    • 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
    • Y02T10/40—Engine management systems

Definitions

  • the present invention relates to an internal combustion engine system, in particular in a motor vehicle.
  • the invention also relates to a method for generating an exhaust gas recirculation amount to be set in an internal combustion engine system, in particular in a motor vehicle.
  • An internal combustion engine system usually comprises an internal combustion engine, for example a diesel engine or a gasoline engine, a fresh gas system for supplying fresh gas to the internal combustion engine, an exhaust system for removing exhaust gas from the internal combustion engine and an exhaust gas recirculation system for removing exhaust gas from the exhaust system at a removal point and Introducing the extracted exhaust gas into the fresh gas system at a discharge point.
  • an exhaust gas recirculation With the help of an exhaust gas recirculation, the values for pollutant emissions and fuel consumption of the internal combustion engine can be lowered.
  • the present invention is concerned with the problem of providing an improved embodiment for an internal combustion engine system or for a method of the aforementioned type, which is characterized in particular by improved exhaust gas recirculation.
  • the invention is based on the general idea to generate pressure oscillations in the fresh gas line, in which pressure drops can be achieved in the region of negative amplitudes, which increase the pressure difference between the sampling point and the point of introduction.
  • the respective introduction point is positioned upstream of the respective fresh gas valve on or in the fresh gas system.
  • Such a construction may be advantageous in certain configurations of the fresh gas system.
  • the connection of the exhaust gas recirculation system can be problematic downstream of the respective fresh gas valve to the fresh gas system for reasons of space.
  • INS special if the respective fresh gas valve should be positioned relatively close to the inlet side of the internal combustion engine due to additional functionalities.
  • the fresh gas valve can be designed so that it can be controlled dynamically.
  • a dynamically controllable or controlled fresh gas valve is present when, for example, by means of a corresponding valve control, the switching states of the fresh gas valve are adjusted depending on operating conditions of the internal combustion engine or are adjustable.
  • the fresh gas valve can be actuated dynamically as a function of load and / or rotational speed of the internal combustion engine so as to be able to dynamically adjust the fresh gas pressure at the point of introduction to the demand for recirculating exhaust gas which changes as a function of the operating state of the internal combustion engine.
  • the fresh gas valve can be designed as a fast-switching valve.
  • a fast-switching valve is understood to mean a valve which is adjustable within a comparatively short time between two extreme control positions.
  • a quick-switching valve between a control position with maximum open cross-section and a control position with minimum open or closed cross-section with switching times in the two-digit or even in the single-digit millisecond range adjustable.
  • Such fast-switching de valves are basically known as so-called air cycle valves, which are used in fresh gas lines that supply individual cylinders with fresh gas, to effect by utilizing flow dynamic effects a pulse charging of the respective cylinder.
  • FIG. 1 is a greatly simplified, schematics-like schematic diagram of an internal combustion engine system
  • Fig. 2 is a diagram for illustrating the time course of the pressure in the fresh gas system and in the exhaust gas recirculation system.
  • an internal combustion engine system 1 which is preferably arranged in a motor vehicle, comprises an internal combustion engine 2, a fresh gas system 3, an exhaust system 4 and an exhaust gas recirculation system 5.
  • the internal combustion engine system 1 may comprise a fuel injection system.
  • the internal combustion engine 2 is a conventional internal combustion engine of the piston construction, such as a diesel engine, a gasoline engine or a natural gas engine, which burns a fuel with fresh gas, in particular air, and thereby generates exhaust gas during operation.
  • 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 is used for supplying fresh gas to the internal combustion engine 2.
  • the fresh gas system 3 a fresh gas line 6, which is connected to the internal combustion engine 2 and to the engine block.
  • a charging device 7 is arranged to achieve a pressure increase in the fresh gas. It may be in this charging device 7 is preferably a compressor 7 of an exhaust gas turbocharger 8 or any other charging device 7. If such a charging device 7 is provided, in addition downstream of a heat exchanger 9 can be integrated into the fresh gas system 3, for cooling the charged fresh gas and is commonly referred to as intercooler.
  • the heat exchanger 9 can in this case be incorporated into a cooling circuit 10, which may be a cooling circuit of the internal combustion engine 2 expediently.
  • the invention can in principle also be realized in a non-supercharged internal combustion engine 2.
  • the exhaust system 4 is used for discharging exhaust gas from the internal combustion engine 2 and has for this purpose an exhaust pipe 11 which is connected to the internal combustion engine 2 and to the engine block.
  • the exhaust system 4 includes a turbine 12 of the exhaust gas turbocharger 8 for driving the compressor 7.
  • the exhaust system 4 may include at least one component 13 for treating exhaust gas.
  • This component 13 can be, for example, an oxidation catalytic converter, a particulate filter, a NO x storage catalytic converter or an SCR catalytic converter or any combination of these components 13.
  • this is a particulate filter 13.
  • the exhaust system 4 may have an exhaust valve 14, which is designed so that Thus, a flow-through cross-section of the exhaust system 4 and the exhaust pipe 11 is controllable.
  • the exhaust gas recirculation system 5 serves to remove exhaust gas from the exhaust system 4 and to introduce the extracted exhaust gas into the fresh gas system 3.
  • the exhaust gas recirculation system 5 comprises an exhaust gas recirculation line 15, which is connected via a removal point 16 to the exhaust system 4 and via at least one discharge point 17 to the fresh gas system 3.
  • the exhaust gas recirculation system 5 may have a heat exchanger 18, by means of which the recirculated exhaust gas can be cooled.
  • the heat exchanger 18, which can also be referred to as a return cooler, connected to a cooling circuit 19, which may be in particular the cooling circuit of the internal combustion engine 2.
  • the exhaust gas recirculation system 5 may include a recirculation valve 20, which is expediently configured so that a return flow from the fresh gas system 3 through the exhaust gas recirculation system 5 into the exhaust system 4 can be avoided.
  • the return valve 20 may be a passive non-return check valve, which opens from or at a predetermined pressure difference in the direction of the fresh gas system 3 and always blocks in the opposite direction.
  • this active return valve 20 may be controlled from or at a predetermined pressure difference for setting the respectively desired exhaust gas recirculation amount.
  • the fresh gas system 3 has at least one fresh gas valve 21, which is configured so that a flow-through cross section of the fresh gas system 3 and the fresh gas line 6 is controllable.
  • the fresh gas valve 21 realize a closed position and an open position for the fresh gas system 3. In the closed position, the fresh gas line 6 is blocked or opened with a minimum flow-through cross-section, while the fresh gas line 6 is fully open in the open position of the fresh gas valve 21 or has its maximum flow cross-section.
  • the respective introduction point 17 with respect to the fresh gas flow in the fresh gas system 3 is arranged upstream of the at least one fresh gas valve 21.
  • the fresh gas til 21 and the heat exchanger 9 to form a unitary assembly together.
  • the heat exchanger 9 can in principle also be arranged between the introduction point 17 and the fresh gas valve 21.
  • the positioning of the inlet 17 upstream of the heat exchanger 9 is advantageous because the fresh gas-exhaust mixture formed in the exhaust gas recirculation must flow through the heat exchanger 9 and thereby intensively mixed or homogenized. In principle, however, it is also possible to arrange the heat exchanger 9 upstream of the discharge point 17 in the fresh gas system 3.
  • a valve control 22 is expediently provided, which is connected in a suitable manner, for example via control lines, with the fresh gas valve 21.
  • the valve control 22 may also be connected to the exhaust valve 14 and / or to the recirculation valve 20, as far as these valves are controllable or present.
  • the valve controller 22 can be coupled in a suitable manner, for example via a signal line, to the internal combustion engine 2 or to a motor controller be.
  • the valve control 22 may be integrated in such a motor control.
  • the valve control 22 is expediently coupled to the engine control in such a way that the valve control 22 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.
  • Driving force for the return of exhaust gas from the exhaust system 4 to the fresh gas system 3 is the pressure drop between the sampling point 16 and the at least one discharge point 17.
  • a high-pressure feedback system is shown in which the removal point 16 at the High pressure side of the turbine 12 is located while the discharge point 17 is located on the high pressure side of the compressor 7.
  • low-pressure high-pressure return systems are also conceivable in which exhaust gas is taken off from the low-pressure side of the turbine 12 and introduced on the high-pressure side of the compressor 7. Pure low-pressure feedback systems are also conceivable.
  • the pressure in the fresh gas downstream of the compressor 7 may be similar to that in the exhaust gas upstream of the turbine 12.
  • the valve control 22 the fresh gas valve 21 selectively control so that in the fresh gas system 3, at least upstream of the fresh gas valve 21 pressure swing training.
  • Such pressure oscillations can be generated with the help of the fresh gas valve 21, for example, in that the fresh gas valve 21 is actuated with certain, comparatively short switching times for opening and closing the flow-through cross section of the fresh gas system 3.
  • resonance effects can be exploited here.
  • with the help of the fresh gas valve 21 and pressure oscillations that can be present anyway in the fresh gas system 3 due to gas exchange processes of the internal combustion engine 2 strengthen selectively, so as to obtain the desired pressure oscillations.
  • the pressure oscillations generated with the aid of the fresh gas valve 21 can have a pressure profile designated by the graph 23.
  • This pressure curve 23 represents the change in the pressure p in the fresh gas, which is dependent on the time t, at least upstream of the fresh gas valve 21 and at least at the point of introduction 17. Without limiting the generality, a sinusoidal oscillation curve 23 is shown here.
  • the diagram also includes a designated pressure curve 24, which can be set in the exhaust system 4, at least at the sampling point 16.
  • This pressure curve 24 in the exhaust gas is comparatively linear or constant. It is clear that in the exhaust gas pressure oscillations can basically arise, which are due to the charge cycle operations of the internal combustion engine 2. The resulting amplitudes However, in comparison to the amplitudes generated in the fresh gas by means of the fresh gas valve 21, the dimensions are small and are omitted for a simplified illustration in FIG. 2.
  • Recognizable possesses the pressure curve 23 of the pressure oscillations in the fresh gas in the range of negative amplitudes, ie in the range of vibration minima, each hatched here a vibration region 25 in which the pressure in the fresh gas is smaller than the pressure in the exhaust gas. Accordingly, these vibration regions 25 are each below the pressure curve 24 in the exhaust gas.
  • the fresh gas valve 21 is designed to be dynamically controlled. This makes it possible in particular to actuate the fresh gas valve 21 as a function of the dynamically changing operating state of the internal combustion engine 2 so as to adapt the exhaust gas recirculation rate or the exhaust gas recirculation quantity to the dynamically changing demand by the dynamic control of the fresh gas pressure at the introduction point 17.
  • the fresh gas valve 21 can thereby be actuated dynamically as a function of the rotational speed and / or the load of the internal combustion engine 2.
  • the fresh gas valve 21 is preferably configured as a fast-switching valve that realizes the desired changes in the flow-through cross section of the fresh gas system 3 within relatively short switching times or control times.
  • the fresh gas valve 21 in MiI- lise Genrum be adjusted between its closed position and its open position.
  • the fast-switching fresh gas valve 21 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 fresh gas valve 21 to pressure fluctuations in the fresh gas can be adapted, which occur anyway due to the charge exchange processes in the fresh gas system 3.
  • this positive and negative pressure amplitudes in the oscillating fresh gas flow can be selectively increased.
  • the respective fresh gas valve 21 may be designed as a discontinuously operating valve, in which a valve member, for example a butterfly valve, with opposite directions of movement at least between two predetermined control positions can be switched.
  • a discontinuous fresh gas valve 21 for example, as a valve member having a pivotable about an axis flap, which is switchable between a closed position and an open position.
  • the respective valve member rotates when closing in one direction 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 only in motion during the time-limited, rapidly executing switching operations.
  • the respective fresh gas valve 21 may be a continuously operating valve in which the respective valve member passes through at least two different control positions with the same direction of movement.
  • a continuously operating fresh gas valve 21 may have, for example, a flap or a rotary valve as a valve member which can be driven to rotate about a rotational axis.
  • Characteristic for the continuously operating fresh gas valve 21 is that the respective valve member rotates permanently in the operation of the valve with the same direction of rotation and thereby passes at a predetermined rotational speed, for example, a closing angle range and an opening angle range.
  • a predetermined rotational speed for example, a closing angle range and an opening angle range.
  • a method for generating an exhaust gas recirculation quantity to be set in an internal combustion engine system 1 can take place, for example, as follows:
  • the valve control 22 can generate the fresh gas valve 21 to control pressure oscillations, in which the frequency and / or the amplitude depends on the respective exhaust gas recirculation amount to be set.
  • the data required for this purpose such as frequency, amplitude, switching times, can be stored in characteristic maps as a function of the respective exhaust gas recirculation quantity or as a function of load or speed of the internal combustion engine 2.
  • the valve control 22 can selectively control the optionally present exhaust gas valve 14 such that pressure oscillations or pressure pulses are formed in the exhaust system 4 in the region of the removal point 16, which is preferably located between the component 13 and the exhaust valve 14, or adjusts an increase in pressure.
  • the valve controller 22 can control the optional return valve 20 so that a false flow of fresh gas via the return system 5 in the exhaust system 4 is prevented.
  • the controllable recirculation valve 20 can also be specifically controlled so that it adjusts the respective desired exhaust gas recirculation amount in the presence of a predetermined pressure difference between the sampling point 16 Einleitstelle 17.
  • the controllable return valve 20 can control a much larger flow-through cross section, which reduces the flow resistance accordingly.

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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

The invention relates to an internal combustion engine system (1), especially for use in a motor vehicle, which comprises an internal combustion engine (2), a charge air system (3) for supplying charge air to the internal combustion engine (2), an exhaust gas system (4) for discharging exhaust gas from the internal combustion engine (2), an exhaust gas recirculation system (5) for removing exhaust gas from the exhaust gas system (4) and for passing the exhaust gas into the charge air system (3) in at least one inlet point (17) and a charge air valve (21), arranged in the charge air system (3), for controlling a flow area of the charge air system (3). The invention is characterized in that the charge air valve (21) is arranged in the charge air system (3) downstream of the at least one inlet point (17).

Description

FRISCHGASVENTILANORDNUNG IN EINER BRENNKRAFTMASCHINE FRESH GAS VALVE ASSEMBLY IN AN INTERNAL COMBUSTION ENGINE

Die vorliegende Erfindung betrifft ein Brennkraftmaschinensystem, insbesondere in einem Kraftfahrzeug. Die Erfindung betrifft außerdem ein Verfahren zum Erzeugen einer einzustellenden Abgasrückführmenge bei einem Brennkraftmaschinensystem, insbesondere in einem Kraftfahrzeug.The present invention relates to an internal combustion engine system, in particular in a motor vehicle. The invention also relates to a method for generating an exhaust gas recirculation amount to be set in an internal combustion engine system, in particular in a motor vehicle.

Üblicherweise umfasst ein Brennkraftmaschinensystem eine Brennkraftmaschine, zum Beispiel einen Dieselmotor oder einen Benzinmotor, eine Frischgasanlage zum Zuführen von Frischgas zur Brennkraftmaschine, eine Abgasanlage zum Abführen von Abgas von der Brennkraftmaschine sowie eine Ab- gasrückführanlage zum Entnehmen von Abgas aus der Abgasanlage an einer Entnahmestelle und zum Einleiten des entnommenen Abgases in die Frischgasanlage an einer Einleitstelle. Mit Hilfe einer Abgasrückführung können die Werte für Schadstoffemissionen und Kraftstoffverbrauch der Brennkraftmaschine gesenkt werden.An internal combustion engine system usually comprises an internal combustion engine, for example a diesel engine or a gasoline engine, a fresh gas system for supplying fresh gas to the internal combustion engine, an exhaust system for removing exhaust gas from the internal combustion engine and an exhaust gas recirculation system for removing exhaust gas from the exhaust system at a removal point and Introducing the extracted exhaust gas into the fresh gas system at a discharge point. With the help of an exhaust gas recirculation, the values for pollutant emissions and fuel consumption of the internal combustion engine can be lowered.

Zur Realisierung einer Abgasrückführung ist ein Druckgefälle zwischen der Entnahmestelle und der Einleitstelle erforderlich. Insbesondere bei aufgeladenen Brennkraftmaschinen kann die Bereitstellung eines ausreichenden Druckgefälles problematisch sein.To realize an exhaust gas recirculation a pressure gradient between the sampling point and the discharge point is required. Especially with supercharged internal combustion engines the provision of a sufficient pressure gradient be problematic.

Die vorliegende Erfindung beschäftigt sich mit dem Problem, für ein Brennkraftmaschinensystem beziehungsweise für ein Verfahren der eingangs genannten Art eine verbesserte Ausführungsform anzugeben, die sich insbesondere durch eine verbesserte Abgasrückführung auszeichnet.The present invention is concerned with the problem of providing an improved embodiment for an internal combustion engine system or for a method of the aforementioned type, which is characterized in particular by improved exhaust gas recirculation.

Dieses Problem wird erfindungsgemäß durch die Gegenstände der unabhängigen Ansprüche gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der abhängigen Ansprüche.This problem is solved according to the invention by the subject matters of the independent claims. Advantageous embodiments are the subject of the dependent claims.

Die Erfindung beruht auf dem allgemeinen Gedanken, in der Frischgasleitung Druckschwingungen zu erzeugen, bei denen im Bereich negativer Amplituden Druckabsenkungen erzielbar sind, welche die Druckdifferenz zwischen Entnahmestelle und Einleitstelle vergrößern.The invention is based on the general idea to generate pressure oscillations in the fresh gas line, in which pressure drops can be achieved in the region of negative amplitudes, which increase the pressure difference between the sampling point and the point of introduction.

Erfindungsgemäß wird nun vorgeschlagen, die in der Frischgasanlage erzeugten Druckschwingungen stromauf des jeweiligen Frischgasventils auf die Abgasrückführanlage zu übertragen. Mit anderen Worten, die jeweilige Einleitstelle wird stromauf des jeweiligen Frischgasventils an oder in der Frischgasanlage positioniert. Eine derartige Bauweise kann bei bestimmten Konfigurationen der Frischgasanlage vorteilhaft sein. Beispielsweise kann die Anbindung der Abgasrückführanlage stromab des jeweiligen Frischgasventils an die Frischgasanlage aus Bauraumgründen problematisch sein. Ins- besondere dann, wenn das jeweilige Frischgasventil aufgrund zusätzlicher Funktionalitäten relativ nah an der Einlassseite der Brennkraftmaschine positioniert werden soll.According to the invention it is now proposed to transmit the pressure oscillations generated in the fresh gas system upstream of the respective fresh gas valve to the exhaust gas recirculation system. In other words, the respective introduction point is positioned upstream of the respective fresh gas valve on or in the fresh gas system. Such a construction may be advantageous in certain configurations of the fresh gas system. For example, the connection of the exhaust gas recirculation system can be problematic downstream of the respective fresh gas valve to the fresh gas system for reasons of space. INS special if the respective fresh gas valve should be positioned relatively close to the inlet side of the internal combustion engine due to additional functionalities.

Gemäß einer vorteilhaften Weiterbildung kann das Frischgasventil so ausgestaltet sein, dass es dynamisch ansteuerbar ist. Ein dynamisch ansteuerbares beziehungsweise angesteuertes Frischgasventil liegt dann vor, wenn beispielsweise mittels einer entsprechenden Ventilsteuerung die Schaltzustände des Frischgasventils in Abhängigkeit von Betriebszuständen der Brennkraftmaschine eingestellt werden beziehungsweise einstellbar sind. Beispielsweise kann das Frischgasventil dynamisch in Abhängigkeit von Last- und/oder Drehzahl der Brennkraftmaschine betätigt werden, um so den Frischgasdruck an der Einleitstelle dynamisch an den sich in Abhängigkeit des Betriebszustands der Brennkraftmaschine ändernden Bedarf an rückzuführendem Abgas anpassen zu können.According to an advantageous development, the fresh gas valve can be designed so that it can be controlled dynamically. A dynamically controllable or controlled fresh gas valve is present when, for example, by means of a corresponding valve control, the switching states of the fresh gas valve are adjusted depending on operating conditions of the internal combustion engine or are adjustable. For example, the fresh gas valve can be actuated dynamically as a function of load and / or rotational speed of the internal combustion engine so as to be able to dynamically adjust the fresh gas pressure at the point of introduction to the demand for recirculating exhaust gas which changes as a function of the operating state of the internal combustion engine.

Des weiteren kann das Frischgasventil als schnellschaltendes Ventil ausgestaltet sein. Unter einem schnellschaltenden Ventil wird im vorliegenden Zusammenhand ein Ventil verstanden, das innerhalb einer vergleichsweise kurzen Zeit zwischen zwei extremen Steuerstellungen verstellbar ist. Beispielsweise ist ein derartiges schnellschaltendes Ventil zwischen einer Steuerstellung mit maximal geöffnetem durchströmbaren Querschnitt und einer Steuerstellung mit minimal geöffnetem beziehungsweise mit geschlossenem Querschnitt mit Schaltzeiten im zweistelligen oder sogar im einstelligen Millisekundenbereich verstellbar. Derartige schnellschalten- de Ventile sind grundsätzlich als sogenannte Lufttaktventile bekannt, die in Frischgasleitungen, die einzelne Zylinder mit Frischgas versorgen, dazu verwendbar sind, durch Ausnutzung strömungsdynamischer Effekte eine Impulsaufladung des jeweiligen Zylinders zu bewirken.Furthermore, the fresh gas valve can be designed as a fast-switching valve. In the present context, a fast-switching valve is understood to mean a valve which is adjustable within a comparatively short time between two extreme control positions. For example, such a quick-switching valve between a control position with maximum open cross-section and a control position with minimum open or closed cross-section with switching times in the two-digit or even in the single-digit millisecond range adjustable. Such fast-switching de valves are basically known as so-called air cycle valves, which are used in fresh gas lines that supply individual cylinders with fresh gas, to effect by utilizing flow dynamic effects a pulse charging of the respective cylinder.

Weitere wichtige Merkmale und Vorteile der Erfindung ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der zugehörigen Figurenbeschreibung anhand der Zeichnungen.Other important features and advantages of the invention will become apparent from the dependent claims, from the drawings and from the associated figure description with reference to the drawings.

Es versteht sich, dass die vorstehend genannten und die nachstehend noch zu erläuternden Merkmale nicht nur in der jeweils angegebenen Kombination, sondern auch in anderen Kombinationen oder in Alleinstellung verwendbar sind, ohne den Rahmen der vorliegenden Erfindung zu verlassen.It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Bevorzugte Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und werden in der nachfolgenden Beschreibung näher erläutert, wobei sich gleiche Bezugszeichen auf gleiche oder ähnliche oder funktional gleiche Bauteile beziehen .Preferred embodiments of the invention are illustrated in the drawings and will be described in more detail in the following description, wherein like reference numerals refer to the same or similar or functionally identical components.

Es zeigen, jeweils schematisch,Show, in each case schematically,

Fig. 1 eine stark vereinfachte, schaltplanartige Prinzipdarstellung eines Brennkraftmaschinensystems, Fig. 2 ein Diagramm zur Veranschaulichung des zeitlichen Verlaufs des Drucks in der Frischgasanlage und in der Abgasrückführanlage .1 is a greatly simplified, schematics-like schematic diagram of an internal combustion engine system, Fig. 2 is a diagram for illustrating the time course of the pressure in the fresh gas system and in the exhaust gas recirculation system.

Entsprechend Fig. 1 umfasst ein Brennkraftmaschinensystem 1, das vorzugsweise in einem Kraftfahrzeug angeordnet ist, eine Brennkraftmaschine 2, eine Frischgasanlage 3, eine Abgasanlage 4 sowie eine Abgasrückführanlage 5. Außerdem kann das Brennkraftmaschinensystem 1 eine Kraftstoffeinspritzanlage aufweisen. Bei der Brennkraftmaschine 2 handelt es sich um einen üblichen Verbrennungsmotor der Kolbenbauweise, wie zum Beispiel ein Dieselmotor, ein Benzinmotor oder ein Erdgasmotor, der im Betrieb einen Kraftstoff mit Frischgas, insbesondere Luft, verbrennt und dabei Abgas erzeugt. Die Brennkraftmaschine 2 weist einen Motorblock mit Zylindern auf, die Brennräume enthalten, in denen im Betrieb der Brennkraftmaschine 2 die Verbrennungsreaktionen ablaufen und das Abgas entsteht.According to FIG. 1, an internal combustion engine system 1, which is preferably arranged in a motor vehicle, comprises an internal combustion engine 2, a fresh gas system 3, an exhaust system 4 and an exhaust gas recirculation system 5. In addition, the internal combustion engine system 1 may comprise a fuel injection system. The internal combustion engine 2 is a conventional internal combustion engine of the piston construction, such as a diesel engine, a gasoline engine or a natural gas engine, which burns a fuel with fresh gas, in particular air, and thereby generates exhaust gas during operation. 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.

Die Kraftstoffeinspritzanlage dient zum Zuführen von Kraftstoff zu Brennräumen der Brennkraftmaschine 2. Sie kann insbesondere als Common-Rail-System ausgestaltet sein und/oder mehrere Kraftstoff-Injektoren aufweisen.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.

Die Frischgasanlage 3 dient zum Zuführen von Frischgas zur Brennkraftmaschine 2. Hierzu weist die Frischgasanlage 3 eine Frischgasleitung 6 auf, die an die Brennkraftmaschine 2 bzw. an den Motorblock angeschlossen ist. Sofern es sich, wie hier, um eine aufgeladene Brennkraftmaschine 2 handelt, ist in der Frischgasanlage 3 eine Ladeeinrichtung 7 angeordnet, um im Frischgas eine Druckerhöhung zu erzielen. Dabei kann es sich bei dieser Ladeeinrichtung 7 vorzugsweise um einen Verdichter 7 eines Abgasturboladers 8 handeln oder um eine beliebige andere Ladeeinrichtung 7. Sofern eine derartige Ladeeinrichtung 7 vorgesehen ist, kann zusätzlich stromab davon ein Wärmeübertrager 9 in die Frischgasanlage 3 eingebunden sein, der zum Kühlen des aufgeladenen Frischgases dient und üblicherweise als Ladeluftkühler bezeichnet wird. Der Wärmeübertrager 9 kann hierbei in einen Kühlkreis 10 eingebunden sein, bei dem es sich zweckmäßig um einen Kühlkreis der Brennkraftmaschine 2 handeln kann. Die Erfindung ist grundsätzlich auch bei einer nicht aufgeladenen Brennkraftmaschine 2 realisierbar.The fresh gas system 3 is used for supplying fresh gas to the internal combustion engine 2. For this purpose, the fresh gas system 3, a fresh gas line 6, which is connected to the internal combustion engine 2 and to the engine block. If, as here, it is a supercharged internal combustion engine 2, in the fresh gas system 3, a charging device 7 is arranged to achieve a pressure increase in the fresh gas. It may be in this charging device 7 is preferably a compressor 7 of an exhaust gas turbocharger 8 or any other charging device 7. If such a charging device 7 is provided, in addition downstream of a heat exchanger 9 can be integrated into the fresh gas system 3, for cooling the charged fresh gas and is commonly referred to as intercooler. The heat exchanger 9 can in this case be incorporated into a cooling circuit 10, which may be a cooling circuit of the internal combustion engine 2 expediently. The invention can in principle also be realized in a non-supercharged internal combustion engine 2.

Die Abgasanlage 4 dient zum Abführen von Abgas von der Brennkraftmaschine 2 und weist hierzu eine Abgasleitung 11 auf, die an die Brennkraftmaschine 2 bzw. an den Motorblock angeschlossen ist. Im vorliegenden Fall enthält die Abgasanlage 4 eine Turbine 12 des Abgasturboladers 8 zum Antreiben des Verdichters 7. Optional kann die Abgasanlage 4 zumindest eine Komponente 13 zum Behandeln von Abgas enthalten. Bei dieser Komponente 13 kann es sich beispielsweise um einen Oxidationskatalysator, um ein Partikelfilter, um einen NOx- Speicherkatalysator oder um einen SCR-Katalysator oder um eine beliebige Kombination dieser Komponenten 13 handeln. Vorzugsweise handelt es sich dabei jedoch um ein Partikelfilter 13. Zusätzlich oder optional kann die Abgasanlage 4 ein Abgasventil 14 aufweisen, das so ausgestaltet ist, dass damit ein durchströmbarer Querschnitt der Abgasanlage 4 beziehungsweise der Abgasleitung 11 steuerbar ist.The exhaust system 4 is used for discharging exhaust gas from the internal combustion engine 2 and has for this purpose an exhaust pipe 11 which is connected to the internal combustion engine 2 and to the engine block. In the present case, the exhaust system 4 includes a turbine 12 of the exhaust gas turbocharger 8 for driving the compressor 7. Optionally, the exhaust system 4 may include at least one component 13 for treating exhaust gas. This component 13 can be, for example, an oxidation catalytic converter, a particulate filter, a NO x storage catalytic converter or an SCR catalytic converter or any combination of these components 13. Preferably, however, this is a particulate filter 13. Additionally or optionally, the exhaust system 4 may have an exhaust valve 14, which is designed so that Thus, a flow-through cross-section of the exhaust system 4 and the exhaust pipe 11 is controllable.

Die Abgasrückführanlage 5 dient dazu, der Abgasanlage 4 Abgas zu entnehmen und das entnommene Abgas in die Frischgasanlage 3 einzuleiten. Hierzu umfasst die Abgasrückführanlage 5 eine Abgasrückführleitung 15, die über eine Entnahmestelle 16 an die Abgasanlage 4 und über zumindest eine Einleitstelle 17 an die Frischgasanlage 3 angeschlossen ist. In dem in Fig. 1 gezeigten, bevorzugten Beispiel ist nur eine derartige Einleitstelle 17 dargestellt, bei anderen Ausführungsformen können auch zwei oder mehr Einleitstellen 17 vorgesehen sein. Die Abgasrückführanlage 5 kann einen Wärmeübertrager 18 aufweisen, mit dessen Hilfe das rückzuführende Abgas gekühlt werden kann. Hierzu ist der Wärmeübertrager 18, der auch als Rückführkühler bezeichnet werden kann, an einen Kühlkreis 19 angeschlossen, bei dem es sich insbesondere um den Kühlkreis der Brennkraftmaschine 2 handeln kann. Zusätzlich oder optional kann die Abgasrückführanlage 5 ein Rückführventil 20 enthalten, das zweckmäßig so ausgestaltet ist, dass damit eine Rückströmung von der Frischgasanlage 3 durch die Abgasrückführanlage 5 in die Abgasanlage 4 vermieden werden kann. Bei einer einfachen Ausführungsform kann es sich beim Rückführventil 20 um ein passiv arbeitendes Rückschlagsperrventil handeln, das ab beziehungsweise bei einer vorbestimmten Druckdifferenz in Richtung zur Frischgasanlage 3 öffnet und in der Gegenrichtung stets sperrt. Bei einer anderen Ausführungsform kann es sich um ein aktives beziehungsweise steuerbares Rückführventil 20 handeln, mit dessen Hilfe der durchströmbare Querschnitt der Abgasrückführanlage 5 beziehungsweise der Rückführleitung 15 steuerbar ist. Beispielsweise kann dieses aktive Rückführventil 20 ab oder bei einer vorbestimmten Druckdifferenz zum Einstellen der jeweils gewünschten Abgasrückführmenge angesteuert werden.The exhaust gas recirculation system 5 serves to remove exhaust gas from the exhaust system 4 and to introduce the extracted exhaust gas into the fresh gas system 3. For this purpose, the exhaust gas recirculation system 5 comprises an exhaust gas recirculation line 15, which is connected via a removal point 16 to the exhaust system 4 and via at least one discharge point 17 to the fresh gas system 3. In the preferred example shown in Fig. 1, only one such introduction point 17 is shown, in other embodiments, two or more discharge points 17 may be provided. The exhaust gas recirculation system 5 may have a heat exchanger 18, by means of which the recirculated exhaust gas can be cooled. For this purpose, the heat exchanger 18, which can also be referred to as a return cooler, connected to a cooling circuit 19, which may be in particular the cooling circuit of the internal combustion engine 2. Additionally or optionally, the exhaust gas recirculation system 5 may include a recirculation valve 20, which is expediently configured so that a return flow from the fresh gas system 3 through the exhaust gas recirculation system 5 into the exhaust system 4 can be avoided. In a simple embodiment, the return valve 20 may be a passive non-return check valve, which opens from or at a predetermined pressure difference in the direction of the fresh gas system 3 and always blocks in the opposite direction. In another embodiment, it may be an active or controllable return valve 20, with its Help the durchströmbare cross section of the exhaust gas recirculation system 5 and the return line 15 is controllable. For example, this active return valve 20 can be controlled from or at a predetermined pressure difference for setting the respectively desired exhaust gas recirculation amount.

Die Frischgasanlage 3 weist zumindest ein Frischgasventil 21 auf, das so ausgestaltet ist, dass damit ein durchströmbarer Querschnitt der Frischgasanlage 3 beziehungsweise der Frischgasleitung 6 steuerbar ist. Beispielsweise kann das Frischgasventil 21 eine Schließstellung und eine Offenstellung für die Frischgasanlage 3 realisieren. In der Schließstellung ist die Frischgasleitung 6 gesperrt beziehungsweise mit einem minimalen durchströmbaren Querschnitt geöffnet, während die Frischgasleitung 6 in der Offenstellung des Frischgasventils 21 voll geöffnet ist beziehungsweise seinen maximal durchströmbaren Querschnitt aufweist.The fresh gas system 3 has at least one fresh gas valve 21, which is configured so that a flow-through cross section of the fresh gas system 3 and the fresh gas line 6 is controllable. For example, the fresh gas valve 21 realize a closed position and an open position for the fresh gas system 3. In the closed position, the fresh gas line 6 is blocked or opened with a minimum flow-through cross-section, while the fresh gas line 6 is fully open in the open position of the fresh gas valve 21 or has its maximum flow cross-section.

Erfindungswesentlich ist nun, dass die jeweilige Einleitstelle 17 bezüglich der Frischgasströmung in der Frischgasanlage 3 stromauf des wenigstens einen Frischgasventils 21 angeordnet ist. Hierdurch ist es insbesondere möglich, die Positionierung der Einleitstelle 17 vergleichsweise unabhängig von der Einbausituation des Frischgasventils 21 zu wählen. Beispielsweise kann es erforderlich sein, das Frischgasventil 21 relativ nah an der Einlassseite der Brennkraftmaschine 2 anzuordnen, wodurch die Positionierung der Einleitstelle 17 stromab des Frischgasventils 21 problematisch ist. Ebenso ist es grundsätzlich denkbar, das Frischgasven- til 21 und den Wärmeübertrager 9 zu einer einheitlichen Baugruppe zusammen zu fassen. Um das rückzuführende Abgas dennoch stromauf des Wärmeübertragers 9 in die Frischgasanlage 3 einleiten zu können, ist es daher vorteilhaft, die Einleitstelle 17 stromauf des Frischgasventils 21 anzuordnen. Ferner führt die Einleitung des rückgeführten Abgases stromauf des Frischgasventils 21 dazu, dass auch das Frischgasventil 21 vom Frischgas-Abgas-Gemisch durchströmt wird, was die Durchmischung des Gemischs verbessert.It is now essential to the invention that the respective introduction point 17 with respect to the fresh gas flow in the fresh gas system 3 is arranged upstream of the at least one fresh gas valve 21. This makes it possible in particular to select the positioning of the introduction point 17 comparatively independently of the installation situation of the fresh gas valve 21. For example, it may be necessary to arrange the fresh gas valve 21 relatively close to the inlet side of the internal combustion engine 2, whereby the positioning of the introduction point 17 downstream of the fresh gas valve 21 is problematic. Likewise, it is conceivable in principle that the fresh gas til 21 and the heat exchanger 9 to form a unitary assembly together. In order nevertheless to be able to introduce the recirculated exhaust gas upstream of the heat exchanger 9 into the fresh gas system 3, it is therefore advantageous to arrange the inlet 17 upstream of the fresh gas valve 21. Further, the introduction of the recirculated exhaust gas upstream of the fresh gas valve 21 causes the fresh gas valve 21 is flowed through by the fresh gas-exhaust gas mixture, which improves the mixing of the mixture.

Der Wärmeübertrager 9 kann grundsätzlich auch zwischen der Einleitstelle 17 und dem Frischgasventil 21 angeordnet sein. Die Positionierung der Einleitstelle 17 stromauf des Wärmeübertragers 9 ist von Vorteil, da das bei der Abgasrückführung gebildete Frischgas-Abgas-Gemisch so den Wärmeübertrager 9 durchströmen muss und dabei intensiv durchmischt beziehungsweise homogenisiert wird. Grundsätzlich ist es jedoch auch möglich, den Wärmeübertrager 9 stromauf der Einleitstelle 17 in der Frischgasanlage 3 anzuordnen.The heat exchanger 9 can in principle also be arranged between the introduction point 17 and the fresh gas valve 21. The positioning of the inlet 17 upstream of the heat exchanger 9 is advantageous because the fresh gas-exhaust mixture formed in the exhaust gas recirculation must flow through the heat exchanger 9 and thereby intensively mixed or homogenized. In principle, however, it is also possible to arrange the heat exchanger 9 upstream of the discharge point 17 in the fresh gas system 3.

Zur Betätigung des Frischgasventils 21 ist zweckmäßig eine Ventilsteuerung 22 vorgesehen, die auf geeignete Weise, z.B. über Steuerleitungen, mit dem Frischgasventil 21 verbunden ist. Die Ventilsteuerung 22 kann außerdem mit dem Abgasventil 14 und/oder mit dem Rückführventil 20 verbunden sein, soweit diese Ventile steuerbar beziehungsweise vorhanden sind. Optional kann die Ventilsteuerung 22 auf geeignete Weise, z.B. über eine Signalleitung, mit der Brennkraftmaschine 2 beziehungsweise mit einer Motorsteuerung gekoppelt sein. Beispielsweise kann die Ventilsteuerung 22 in eine derartige Motorsteuerung integriert sein. Jedenfalls ist die Ventilsteuerung 22 zweckmäßig mit der Motorsteuerung so gekoppelt, dass die Ventilsteuerung 22 den aktuellen Betriebszustand der Brennkraftmaschine 2 kennt beziehungsweise die vom aktuellen Betriebszustand der Brennkraftmaschine 2 abhängige Abgasrückführmenge kennt.For actuation of the fresh gas valve 21, a valve control 22 is expediently provided, which is connected in a suitable manner, for example via control lines, with the fresh gas valve 21. The valve control 22 may also be connected to the exhaust valve 14 and / or to the recirculation valve 20, as far as these valves are controllable or present. Optionally, the valve controller 22 can be coupled in a suitable manner, for example via a signal line, to the internal combustion engine 2 or to a motor controller be. For example, the valve control 22 may be integrated in such a motor control. In any case, the valve control 22 is expediently coupled to the engine control in such a way that the valve control 22 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.

Antriebskraft für die Rückführung von Abgas von der Abgasanlage 4 zur Frischgasanlage 3 ist das Druckgefälle zwischen der Entnahmestelle 16 und der zumindest einen Einleitstelle 17. Bei der gezeigten Ausführungsform mit aufgeladener Brennkraftmaschine 2 ist ein Hochdruck-Rückführsystem dargestellt, bei dem sich die Entnahmestelle 16 an der Hochdruckseite der Turbine 12 befindet, während sich die Einleitstelle 17 auf der Hochdruckseite des Verdichters 7 befindet. Grundsätzlich sind auch Niederdruck-Hochdruck- Rückführsysteme denkbar, bei denen Abgas auf der Niederdruckseite der Turbine 12 entnommen und auf der Hochdruckseite des Verdichters 7 eingeleitet wird. Auch reine Niederdruck-Rückführsysteme sind denkbar. Je nach Betriebszustand der Brennkraftmaschine 2, der im wesentlichen durch die Parameter Last und Drehzahl bestimmt ist, kann der Druck im Frischgas stromab des Verdichters 7 ähnlich hoch sein wie im Abgas stromauf der Turbine 12. Um bei derartigen Betriebszu- ständen die jeweils gewünschte Abgasrückführmenge realisieren zu können, kann die Ventilsteuerung 22 das Frischgasventil 21 gezielt so ansteuern, dass sich in der Frischgasanlage 3 zumindest stromauf des Frischgasventils 21 Druckschwin- gungen ausbilden. Derartige Druckschwingungen lassen sich mit Hilfe des Frischgasventils 21 beispielsweise dadurch erzeugen, dass das Frischgasventil 21 mit bestimmten, vergleichsweise kurzen Schaltzeiten zum Öffnen und Schließen des durchströmbaren Querschnitts der Frischgasanlage 3 angesteuert wird. Zur Ausbildung besonders ausgeprägter Druckschwingungen lassen sich hierbei Resonanzeffekte ausnutzen. Zusätzlich oder alternativ lassen sich mit Hilfe des Frischgasventils 21 auch Druckschwingungen, die in der Frischgasanlage 3 aufgrund von Ladungswechselvorgängen der Brennkraftmaschine 2 ohnehin vorhanden sein können, gezielt verstärken, um so die gewünschten Druckschwingungen zu erhalten .Driving force for the return of exhaust gas from the exhaust system 4 to the fresh gas system 3 is the pressure drop between the sampling point 16 and the at least one discharge point 17. In the embodiment shown with supercharged internal combustion engine 2, a high-pressure feedback system is shown in which the removal point 16 at the High pressure side of the turbine 12 is located while the discharge point 17 is located on the high pressure side of the compressor 7. In principle, low-pressure high-pressure return systems are also conceivable in which exhaust gas is taken off from the low-pressure side of the turbine 12 and introduced on the high-pressure side of the compressor 7. Pure low-pressure feedback systems are also conceivable. Depending on the operating state of the internal combustion engine 2, which is essentially determined by the parameters load and rotational speed, the pressure in the fresh gas downstream of the compressor 7 may be similar to that in the exhaust gas upstream of the turbine 12. In order to realize the respectively desired exhaust gas recirculation quantity in such operating states to be able to, the valve control 22, the fresh gas valve 21 selectively control so that in the fresh gas system 3, at least upstream of the fresh gas valve 21 pressure swing training. Such pressure oscillations can be generated with the help of the fresh gas valve 21, for example, in that the fresh gas valve 21 is actuated with certain, comparatively short switching times for opening and closing the flow-through cross section of the fresh gas system 3. To form particularly pronounced pressure oscillations, resonance effects can be exploited here. Additionally or alternatively, with the help of the fresh gas valve 21 and pressure oscillations that can be present anyway in the fresh gas system 3 due to gas exchange processes of the internal combustion engine 2, strengthen selectively, so as to obtain the desired pressure oscillations.

Gemäß Fig. 2 können die mit Hilfe des Frischgasventils 21 erzeugten Druckschwingungen einen im Diagramm mit 23 bezeichneten Druckverlauf aufweisen. Dieser Druckverlauf 23 repräsentiert die von der Zeit t abhängige Veränderung des Drucks p im Frischgas zumindest stromauf des Frischgasventils 21 und wenigstens an der Einleitstelle 17. Ohne Beschränkung der Allgemeinheit ist hier ein sinusartiger Schwingungsverlauf 23 dargestellt. Das Diagramm enthält außerdem einen mit 24 bezeichneten Druckverlauf, der sich in der Abgasanlage 4, zumindest an der Entnahmestelle 16 einstellen kann. Dieser Druckverlauf 24 im Abgas ist vergleichsweise linear beziehungsweise konstant. Es ist klar, dass auch im Abgas grundsätzlich Druckschwingungen entstehen können, die auf die Ladungswechselvorgänge der Brennkraftmaschine 2 zurückzuführen sind. Die dabei entstehenden Ampli- tuden sind jedoch im Vergleich zu den mit Hilfe des Frischgasventils 21 im Frischgas erzeugten Amplituden klein und für eine vereinfachte Darstellung in Fig. 2 weggelassen.According to FIG. 2, the pressure oscillations generated with the aid of the fresh gas valve 21 can have a pressure profile designated by the graph 23. This pressure curve 23 represents the change in the pressure p in the fresh gas, which is dependent on the time t, at least upstream of the fresh gas valve 21 and at least at the point of introduction 17. Without limiting the generality, a sinusoidal oscillation curve 23 is shown here. The diagram also includes a designated pressure curve 24, which can be set in the exhaust system 4, at least at the sampling point 16. This pressure curve 24 in the exhaust gas is comparatively linear or constant. It is clear that in the exhaust gas pressure oscillations can basically arise, which are due to the charge cycle operations of the internal combustion engine 2. The resulting amplitudes However, in comparison to the amplitudes generated in the fresh gas by means of the fresh gas valve 21, the dimensions are small and are omitted for a simplified illustration in FIG. 2.

Erkennbar besitzt der Druckverlauf 23 der Druckschwingungen im Frischgas im Bereich negativer Amplituden, also im Bereich der Schwingungsminima, jeweils einen hier schraffierten Schwingungsbereich 25, in dem der Druck im Frischgas jeweils kleiner ist als der Druck im Abgas. Dementsprechend liegen dieser Schwingungsbereiche 25 jeweils unterhalb des Druckverlaufs 24 im Abgas.Recognizable possesses the pressure curve 23 of the pressure oscillations in the fresh gas in the range of negative amplitudes, ie in the range of vibration minima, each hatched here a vibration region 25 in which the pressure in the fresh gas is smaller than the pressure in the exhaust gas. Accordingly, these vibration regions 25 are each below the pressure curve 24 in the exhaust gas.

Besonders vorteilhaft ist eine Ausführungsform, bei welcher das Frischgasventil 21 dynamisch ansteuerbar ausgestaltet ist. Hierdurch ist es insbesondere möglich, das Frischgasventil 21 in Abhängigkeit des sich dynamisch verändernden Betriebszustands der Brennkraftmaschine 2 zu betätigen, um so durch die dynamische Steuerung des Frischgasdrucks an der Einleitstelle 17 die Abgasrückführrate beziehungsweise die Abgasrückführmenge an den sich dynamisch ändernden Bedarf anzupassen. Insbesondere kann dadurch das Frischgasventil 21 dynamisch in Abhängigkeit der Drehzahl und/oder der Last der Brennkraftmaschine 2 betätigt werden.Particularly advantageous is an embodiment in which the fresh gas valve 21 is designed to be dynamically controlled. This makes it possible in particular to actuate the fresh gas valve 21 as a function of the dynamically changing operating state of the internal combustion engine 2 so as to adapt the exhaust gas recirculation rate or the exhaust gas recirculation quantity to the dynamically changing demand by the dynamic control of the fresh gas pressure at the introduction point 17. In particular, the fresh gas valve 21 can thereby be actuated dynamically as a function of the rotational speed and / or the load of the internal combustion engine 2.

Das Frischgasventil 21 ist vorzugsweise als schnellschaltendes Ventil ausgestaltet, das innerhalb relativ kurzer Schaltzeiten oder Steuerzeiten die gewünschten Veränderungen des durchströmbaren Querschnitts der Frischgasanlage 3 realisiert. Beispielsweise kann das Frischgasventil 21 im MiI- lisekundenbereich zwischen seiner Schließstellung und seiner Offenstellung verstellt werden. Insbesondere kann das schnellschaltende Frischgasventil 21 im gleichen Frequenzbereich geschaltet werden, in dem auch die Ladungswechselvorgänge der Brennkraftmaschine 2 stattfinden. Hierdurch ist beispielsweise eine Synchronisation des Frischgasventils 21 an Druckschwankungen im Frischgas anpassbar, die aufgrund der Ladungswechselvorgänge in der Frischgasanlage 3 ohnehin auftreten. Beispielsweise können dadurch positive und negative Druckamplituden in der schwingenden Frischgasströmung gezielt verstärkt werden.The fresh gas valve 21 is preferably configured as a fast-switching valve that realizes the desired changes in the flow-through cross section of the fresh gas system 3 within relatively short switching times or control times. For example, the fresh gas valve 21 in MiI- lisekundenbereich be adjusted between its closed position and its open position. In particular, the fast-switching fresh gas valve 21 can be switched in the same frequency range in which the charge cycle operations of the internal combustion engine 2 take place. As a result, for example, a synchronization of the fresh gas valve 21 to pressure fluctuations in the fresh gas can be adapted, which occur anyway due to the charge exchange processes in the fresh gas system 3. For example, this positive and negative pressure amplitudes in the oscillating fresh gas flow can be selectively increased.

Das jeweilige Frischgasventil 21 kann als diskontinuierlich arbeitendes Ventil ausgestaltet sein, bei dem ein Ventilglied, zum Beispiel eine Schmetterlingsklappe, mit entgegengesetzten Bewegungsrichtungen zumindest zwischen zwei vorbestimmten Steuerstellungen umschaltbar ist. Ohne Beschränkung der Allgemeinheit kann ein derartiges diskontinuierlich arbeitendes Frischgasventil 21 beispielsweise als Ventilglied eine um eine Drehachse verschwenkbare Klappe aufweisen, die zwischen einer Schließstellung und einer Offenstellung umschaltbar ist. Dabei dreht das jeweilige Ventilglied beim Schließen in der einen Drehrichtung und beim Öffnen in der anderen Drehrichtung. Des weiteren ist für ein diskontinuierlich arbeitendes Ventil kennzeichnend, dass das jeweilige Ventilglied in der jeweils eingestellten Steuerstellung für eine gewisse Zeit verbleibt, so dass das Ventilglied nur bei den zeitlich begrenzten, schnell ablaufenden Schaltvorgängen in Bewegung ist. Alternativ kann es sich bei dem jeweiligen Frischgasventil 21 um ein kontinuierlich arbeitendes Ventil handeln, bei dem das jeweilige Ventilglied mit gleicher Bewegungsrichtung zumindest zwei verschiedene Steuerstellungen durchläuft. Ohne Beschränkung der Allgemeinheit kann ein derartiges kontinuierlich arbeitendes Frischgasventil 21 beispielsweise eine Klappe oder einen Drehschieber als Ventilglied aufweisen, das um eine Drehachse rotierend antreibbar ist. Charakteristisch ist hierbei für das kontinuierlich arbeitende Frischgasventil 21, dass das jeweilige Ventilglied im Betrieb des Ventils permanent mit der gleichen Rotationsrichtung dreht und dabei mit einer vorbestimmten Drehgeschwindigkeit zum Beispiel einen Schließwinkelbereich und einen Öffnungswinkelbereich durchfährt. Auch mit Hilfe eines derartigen kontinuierlich arbeitenden Frischgasventils 21 lassen sich extrem kurze Schaltzeiten erzielen, wobei jedoch permanent eine Querschnittsveränderung stattfinden kann und das jeweilige Ventilglied permanent in Bewegung ist. Durch Variation der Drehgeschwindigkeit lassen sich auch bei einem derartigen kontinuierlich arbeitenden Frischgasventil 21 die Schaltzeiten einstellen.The respective fresh gas valve 21 may be designed as a discontinuously operating valve, in which a valve member, for example a butterfly valve, with opposite directions of movement at least between two predetermined control positions can be switched. Without limiting the generality, such a discontinuous fresh gas valve 21, for example, as a valve member having a pivotable about an axis flap, which is switchable between a closed position and an open position. The respective valve member rotates when closing in one direction and when opening in the other direction. Furthermore, 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 only in motion during the time-limited, rapidly executing switching operations. Alternatively, the respective fresh gas valve 21 may be a continuously operating valve in which the respective valve member passes through at least two different control positions with the same direction of movement. Without limiting the generality, such a continuously operating fresh gas valve 21 may have, for example, a flap or a rotary valve as a valve member which can be driven to rotate about a rotational axis. Characteristic for the continuously operating fresh gas valve 21 is that the respective valve member rotates permanently in the operation of the valve with the same direction of rotation and thereby passes at a predetermined rotational speed, for example, a closing angle range and an opening angle range. Even with the aid of such a continuously operating fresh gas valve 21, extremely short switching times can be achieved, but a change in cross section can take place permanently and the respective valve member is permanently in motion. By varying the rotational speed can be adjusted even with such a continuously operating fresh gas valve 21, the switching times.

Ein Verfahren zum Erzeugen einer einzustellenden Abgasrück- führmenge bei einem Brennkraftmaschinensystem 1 kann beispielsweise wie folgt ablaufen:A method for generating an exhaust gas recirculation quantity to be set in an internal combustion engine system 1 can take place, for example, as follows:

Um unterschiedliche Abgasrückführmengen einzustellen, kann die Ventilsteuerung 22 das Frischgasventil 21 zur Erzeugung von Druckschwingungen ansteuern, bei denen die Frequenz und/oder die Amplitude von der jeweils einzustellenden Ab- gasrückführmenge abhängt. Die hierzu erforderlichen Daten, wie Frequenz, Amplitude, Schaltzeiten, können in Kennfeldern in Abhängigkeit der jeweiligen Abgasrückführmenge beziehungsweise in Abhängigkeit von Last oder Drehzahl der Brennkraftmaschine 2 hinterlegt sein.In order to set different exhaust gas recirculation quantities, the valve control 22 can generate the fresh gas valve 21 to control pressure oscillations, in which the frequency and / or the amplitude depends on the respective exhaust gas recirculation amount to be set. The data required for this purpose, such as frequency, amplitude, switching times, can be stored in characteristic maps as a function of the respective exhaust gas recirculation quantity or as a function of load or speed of the internal combustion engine 2.

Grundsätzlich kann die Ventilsteuerung 22 das gegebenenfalls vorhandene Abgasventil 14 gezielt so ansteuern, dass sich in der Abgasanlage 4 im Bereich der Entnahmestelle 16, die sich bevorzugt zwischen der Komponente 13 und dem Abgasventil 14 befindet, Druckschwingungen beziehungsweise Druckimpulse ausbilden oder eine Druckerhöhung einstellt. Des weiteren kann die Ventilsteuerung 22 das gegebenenfalls vorhandene Rückführventil 20 so ansteuern, dass eine Fehlströmung von Frischgas über die Rückführanlage 5 in die Abgasanlage 4 verhindert wird. Außerdem kann das steuerbare Rückführventil 20 gezielt auch so angesteuert werden, dass es bei Vorliegen einer vorbestimmten Druckdifferenz zwischen Entnahmestelle 16 Einleitstelle 17 die jeweils gewünschte Abgasrückführmenge einstellt. Im Unterschied zu einem passiv arbeitenden Rückschlagsperrventil kann das ansteuerbare Rückführventil 20 einen deutlich größeren durchströmbaren Querschnitt steuern, was die Strömungswiderstände entsprechend reduziert. In principle, the valve control 22 can selectively control the optionally present exhaust gas valve 14 such that pressure oscillations or pressure pulses are formed in the exhaust system 4 in the region of the removal point 16, which is preferably located between the component 13 and the exhaust valve 14, or adjusts an increase in pressure. Furthermore, the valve controller 22 can control the optional return valve 20 so that a false flow of fresh gas via the return system 5 in the exhaust system 4 is prevented. In addition, the controllable recirculation valve 20 can also be specifically controlled so that it adjusts the respective desired exhaust gas recirculation amount in the presence of a predetermined pressure difference between the sampling point 16 Einleitstelle 17. In contrast to a passive non-return check valve, the controllable return valve 20 can control a much larger flow-through cross section, which reduces the flow resistance accordingly.

Claims

Ansprüche claims 1. Brennkraftmaschinensystem, insbesondere in einem Kraftfahrzeug,1. internal combustion engine system, in particular in a motor vehicle, - mit einer Brennkraftmaschine (2),with an internal combustion engine (2), - mit einer Frischgasanlage (3) zum Zuführen von Frischgas zur Brennkraftmaschine (2),- With a fresh gas system (3) for supplying fresh gas to the internal combustion engine (2), - mit einer Abgasanlage (4) zum Abführen von Abgas von der Brennkraftmaschine (2),- With an exhaust system (4) for discharging exhaust gas from the internal combustion engine (2), - mit einer Abgasrückführanlage (5) zum Entnehmen von Abgas aus der Abgasanlage (4) und zum Einleiten des Abgases in die Frischgasanlage (3) an wenigstens einer Einleitstelle- With an exhaust gas recirculation system (5) for removing exhaust gas from the exhaust system (4) and for introducing the exhaust gas into the fresh gas system (3) at least one discharge point (17),(17) - mit wenigstens einem in der Frischgasanlage (3) angeordneten Frischgasventil (21) zum Steuern eines durchströmbaren Querschnitts der Frischgasanlage (3) ,- With at least one in the fresh gas system (3) arranged fresh gas valve (21) for controlling a flow-through cross section of the fresh gas system (3), - wobei das wenigstens eine Frischgasventil (21) in der Frischgasanlage (3) stromab der wenigstens einen Einleitstelle (17) angeordnet ist.- Wherein the at least one fresh gas valve (21) in the fresh gas system (3) downstream of the at least one introduction point (17) is arranged. 2. Brennkraftmaschinensystem nach Anspruch 1, dadurch gekennzeichnet,2. Internal combustion engine system according to claim 1, characterized - dass eine Ventilsteuerung (22) zur Betätigung des wenigstens einen Frischgasventils (21) vorgesehen ist, - dass die Ventilsteuerung (22) und das wenigstens eine Frischgasventil (21) so ausgestaltet sind, dass mit der Ventilsteuerung (22) das wenigstens eine Frischgasventilin that a valve control (22) is provided for actuating the at least one fresh gas valve (21), - That the valve control (22) and the at least one fresh gas valve (21) are designed so that the at least one fresh gas valve with the valve control (22) (21) zum Erzeugen von Druckschwingungen in der Frischgasanlage (3) zumindest stromauf des wenigstens einen Frischgasventils (21) ansteuerbar ist, deren Frequenz und/oder Amplitude von der jeweils einzustellenden Abgasrückführ- menge abhängt .(21) for generating pressure oscillations in the fresh gas system (3) at least upstream of the at least one fresh gas valve (21) can be controlled, whose frequency and / or amplitude depends on the amount of exhaust gas to be set each. 3. Brennkraftmaschinensystem nach Anspruch 1 oder 2, dadurch gekennzeichnet,3. Internal combustion engine system according to claim 1 or 2, characterized - dass das Frischgasventil (21) dynamisch ansteuerbar ist, und/oder- That the fresh gas valve (21) is dynamically controlled, and / or - dass das Frischgasventil (21) als schnellschaltendes Ventil ausgestaltet ist, und/oder- That the fresh gas valve (21) is designed as a fast-switching valve, and / or - dass das Frischgasventil (21) als diskontinuierlich arbeitendes Ventil, dessen Ventilglied mit entgegengesetzten Bewegungsrichtungen zumindest zwischen zwei vorbestimmten Steuerstellungen umschaltbar ist, oder als kontinuierlich arbeitendes Ventil ausgestaltet ist, dessen Ventilglied mit gleicher Bewegungsrichtung zumindest zwei verschiedene Steuerstellungen durchläuft.- That the fresh gas valve (21) as a discontinuous working valve whose valve member is reversible with opposite directions of movement at least between two predetermined control positions, or designed as a continuously operating valve whose valve member with the same direction of movement passes through at least two different control positions. 4. Brennkraftmaschinensystem nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass die Einleitstelle (17) stromauf eines in der Frischgasanlage (3) angeordneten Wärmeübertragers (9) angeordnet ist. 4. Internal combustion engine system according to one of claims 1 to 3, characterized in that the introduction point (17) is arranged upstream of a in the fresh gas system (3) arranged heat exchanger (9). 5. Brennkraftmaschinensystem nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass in der Abgasrückführanlage (5) ein Rückführventil (20) zum Steuern eines durchströmbaren Querschnitts der Abgasrückführanlage (5) stromauf der Einleitstelle (17) angeordnet ist.5. Internal combustion engine system according to one of claims 1 to 4, characterized in that in the exhaust gas recirculation system (5) a return valve (20) for controlling a flow-through cross section of the exhaust gas recirculation system (5) upstream of the discharge point (17) is arranged. 6. Brennkraftmaschinensystem nach Anspruch 5, dadurch gekennzeichnet,6. Internal combustion engine system according to claim 5, characterized in that - dass das Rückführventil (20) als passiv arbeitendes Rückschlagsperrventil ausgestaltet ist, das bei oder ab einer vorbestimmten Druckdifferenz in Richtung zur Frischgasanlage (3) hin öffnet, oder- That the return valve (20) is designed as a passive non-return check valve that opens at or from a predetermined pressure difference in the direction of the fresh gas system (3) out, or - dass das Rückführventil (20) als aktiv ansteuerbares Schaltventil ausgestaltet ist, das bei oder ab einer vorbestimmten Druckdifferenz zum Einstellen der jeweils einzustellenden Abgasrückführmenge ansteuerbar ist.- That the return valve (20) is designed as an actively controllable switching valve, which is controllable at or from a predetermined pressure difference for setting the respective exhaust gas recirculation amount to be set. 7. Brennkraftmaschinensystem nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass zumindest zwei parallel durchströmbare Frischgasventile (21) vorgesehen sind.7. Internal combustion engine system according to one of claims 1 to 6, characterized in that at least two fresh gas valves (21) which can be flowed through in parallel are provided. 8. Brennkraftmaschinensystem nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass in der Abgasanlage (4) stromab einer Entnahmestelle (16), über welche die Abgasrückführanlage (5) an die Abgasanlage (4) angeschlossen ist, zumindest ein Abgasventil (14; zum Steuern eines durchströmbaren Querschnitts der Abgasanlage (4) angeordnet ist.8. Internal combustion engine system according to one of claims 1 to 7, characterized in that in the exhaust system (4) downstream of a removal point (16), via which the exhaust gas recirculation system (5) is connected to the exhaust system (4), at least one exhaust valve (14) is arranged for controlling a flow-through cross section of the exhaust system (4). 9. Brennkraftmaschinensystem nach einem der vorhergehenden Ansprüche, gekennzeichnet durch eine Kraftstoffeinspritzan- lage zum Versorgen der Brennkraftmaschine (2) mit Kraftstoff.9. internal combustion engine system according to one of the preceding claims, characterized by a fuel injection system for supplying the internal combustion engine (2) with fuel. 10. Verfahren zum Erzeugen einer einzustellenden Abgas- rückführmenge bei einem Brennkraftmaschinensystem 1, insbesondere in einem Kraftfahrzeug, umfassend10. A method for generating an adjusted exhaust gas recirculation amount in an internal combustion engine system 1, in particular in a motor vehicle, comprising - eine Brennkraftmaschine (2),an internal combustion engine (2), - eine Frischgasanlage (3) zum Zuführen von Frischgas zur Brennkraftmaschine (2),- A fresh gas system (3) for supplying fresh gas to the internal combustion engine (2), - eine Abgasanlage (4) zum Abführen von Abgas von der Brennkraftmaschine (2),an exhaust system (4) for discharging exhaust gas from the internal combustion engine (2), - eine Abgasrückführanlage (5) zum Entnehmen von Abgas aus der Abgasanlage (4) und zum Einleiten des entnommenen Abgases in die Frischgasanlage (3) ,- An exhaust gas recirculation system (5) for removing exhaust gas from the exhaust system (4) and for introducing the exhaust gas removed in the fresh gas system (3), - wenigstens ein in der Frischgasanlage (2) angeordnetes Frischgasventil (21) zum Steuern eines durchströmbaren Querschnitts der Frischgasanlage (3) ,- At least one in the fresh gas system (2) arranged fresh gas valve (21) for controlling a flow-through cross-section of the fresh gas system (3), - bei dem das wenigstens eine Frischgasventil (21) zum Erzeugen von Druckschwingungen in der Frischgasanlage (3) zumindest stromauf des Frischgasventils (21) angesteuert wird, bei dem die Druckschwingungen zum Erzeugen einer Abgas- rückführmenge in die Abgasrückführanlage (5) eingeleitet werden, bei dem die Frequenz und/oder die Amplitude der Druckschwingungen in Abhängigkeit der jeweils einzustellenden Abgasrückführmenge eingestellt wird/werden, bei dem die Druckschwingungen zum Erzeugen der jeweiligen Abgasrückführmenge stromauf des wenigstens einen Frischgasventils (21) von der Frischgasanlage (3) in die Abgasrückführanlage (5) eingeleitet werden. in which the at least one fresh gas valve (21) for generating pressure oscillations in the fresh gas system (3) is actuated at least upstream of the fresh gas valve (21), in which the pressure oscillations for generating an exhaust gas recirculation amount are introduced into the exhaust gas recirculation system (5), in which the frequency and / or the amplitude of the pressure oscillations is / are set as a function of the respective exhaust gas recirculation quantity to be set, at which the pressure oscillations for generating the respective exhaust gas recirculation quantity upstream of the at least one fresh gas valve (21) are introduced from the fresh gas system (3) in the exhaust gas recirculation system (5).
PCT/EP2008/055731 2007-05-29 2008-05-09 Charge air valve system for use in an internal combustion engine Ceased WO2008145502A1 (en)

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