WO2007093195A1 - Method for exhaust gas recirculation for an internal combustion engine having an exhaust gas turbocharger - Google Patents

Method for exhaust gas recirculation for an internal combustion engine having an exhaust gas turbocharger Download PDF

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

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
    • F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • F02B37/183—Arrangements of bypass valves or actuators therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/22—Control of the pumps by varying cross-section of exhaust passages or air passages, e.g. by throttling turbine inlets or outlets or by varying effective number of guide conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/12—Control of the pumps
    • F02B37/24—Control of the pumps by using pumps or turbines with adjustable guide vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/05—High pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust system upstream of the turbine and reintroduced into the intake system downstream of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
    • F02B29/04—Cooling of air intake supply
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/42—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders
    • F02M26/43—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories having two or more EGR passages; EGR systems specially adapted for engines having two or more cylinders in which exhaust from only one cylinder or only a group of cylinders is directed to the intake of the engine
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

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

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

Abstract

In order for it to be possible for future NOx limiting values to be adhered to, a method is proposed for exhaust gas recirculation for an internal combustion engine (1) having an exhaust gas turbocharger (2), wherein the exhaust gas turbine (3) comprises two separate flow manifolds (14, 15) which are positioned ahead of a turbine wheel (5) of the exhaust gas turbine (3) and is connected to in each case one exhaust gas line (20; 21) for supply with exhaust gas, and control of the exhaust gases to the exhaust gas turbine (3) is carried out via a variable turbine geometry (50; 60), wherein, for exhaust gas recirculation, an exhaust gas recirculation line (35) leads via a control element (32) to an intake section (6) of the internal combustion engine (3).

Description

Verfahren zur Abgasrückführung für eine Brennkraftmaschine mit Abgasturbolader Method for exhaust gas recirculation for an internal combustion engine with turbocharger
Die Erfindung geht aus von einem Verfahren zur Abgasrückführung für eine Brennkraftmaschine mit Abgasturbolader nach der Gattung des Anspruchs 1.The invention relates to a method for exhaust gas recirculation for an internal combustion engine with exhaust gas turbocharger according to the preamble of claim 1.
Es ist bereits ein Abgasturbolader bekannt (DE 199 24 228 C2), dessen Turbinengehäuse zweiflutig ausgebildet ist. Die Regelung der AbgasZuführung auf ein Turbinenrad der Abgasturbine erfolgt über einen Axialschieber, welcher eine der Fluten vollständig überdecken kann, so dass die AbgasZuführung über eine stromaufwärts befindliche Flutverbindung über eine einzige Flut auf das Turbinenrad erfolgt. Der Schieber ist eine einfache Hülse ohne die Strömung im Sinne einer variablen Turbinengeometrie zu beeinflussen. Eine derartige Steuerung der Abgasmenge ist im nichtbefeuerten Betriebsbereich der Brennkraftmaschine üblich, in welchem die Brennkraftmaschine als Motorbremse (Turbobrake) wirken soll. Die im Motorbremsbetrieb relativ geringe Abgasmenge wird über die kleinere Flut dem Turbinenrad zugeführt, die dem geringeren Abgasstrom mit ihrem Eintrittsquerschnitt entsprechend dimensioniert ist, so dass eine relativ hohe Drehzahl des Turbinenrades und eines über eine Welle mit dem Turbinenrad verbundenen Verdichters aufrecht erhalten werden kann. Durch die relativ hohe Drehzahl des Verdichterrades ergibt sich auch im Motorbremsbetrieb eine Verdichtung der angesaugten Luft und damit eine entsprechende Motorbremsleistung.It is already known an exhaust gas turbocharger (DE 199 24 228 C2), the turbine housing is formed double-flow. The regulation of the exhaust gas supply to a turbine wheel of the exhaust gas turbine via an axial slide, which can completely cover one of the floods, so that the exhaust gas supply takes place via an upstream flood connection via a single flood on the turbine wheel. The slide is a simple sleeve without affecting the flow in terms of a variable turbine geometry. Such control of the amount of exhaust gas is customary in the non-fired operating range of the internal combustion engine in which the internal combustion engine is to act as an engine brake (turbo brake). The relatively low exhaust gas quantity in engine braking operation is supplied to the turbine wheel via the smaller flow, which is dimensioned correspondingly to the smaller exhaust gas flow with its inlet cross section, so that a relatively high rotational speed of the turbine wheel and a compressor connected to the turbine wheel via a shaft can be maintained. Due to the relatively high Speed of the compressor also results in the engine braking operation, a compression of the intake air and thus a corresponding engine braking performance.
Es ist ferner bekannt, Abgasturbolader mit einer variablen Turbinengeometrie auszustatten, um die Strömung auf das Turbinenrad entsprechend anzupassen. Auch der Einsatz der variablen Turbinengeometrie zum Zwecke der Motorbremse ist bekannt. Ein zusätzlicher Einsatz der variablen Turbinengeometrie zur effizienten Abgasrückführung ist jedoch nicht bekannt, um künftige NOx-Grenzwerte einhalten zu können, die auch im Teillastbereich der Brennkraftmaschine hohe Abgasrückführraten von mehr als 50 % erfordern.It is also known to provide turbocharger with a variable turbine geometry to adjust the flow to the turbine wheel accordingly. The use of the variable turbine geometry for the purpose of the engine brake is known. However, additional use of the variable turbine geometry for efficient exhaust gas recirculation is not known in order to be able to comply with future NOx limit values which require high exhaust gas recirculation rates of more than 50% even in the partial load range of the internal combustion engine.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Verfahren zur Abgasrückführung für eine Brennkraftmaschine mit Abgasturbolader mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass mit einer vorhandenen variablen Turbinengeometrie der Abgasturbine zum Zwecke der Motorbremse in einfacher Art und Weise auch eine Abgasrückführung durchführbar ist, bei der hohe Abgasrückführraten von mehr als 50 % bewerkstelligt werden können.The inventive method for exhaust gas recirculation for an internal combustion engine with exhaust gas turbocharger with the characterizing features of claim 1 has the advantage that with an existing variable turbine geometry of the exhaust gas turbine for the purpose of engine brake in a simple manner, an exhaust gas recirculation is feasible at the high exhaust gas recirculation rates of more than 50% can be accomplished.
Durch die in Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des im Anspruch 1 angegebenen Verfahrens zur Abgasrückführung für eine Brennkraftmaschine mit einem Abgasturbolader möglich.The measures listed in dependent claims advantageous refinements and improvements of the claim 1 method for exhaust gas recirculation for an internal combustion engine with an exhaust gas turbocharger are possible.
Vorteilhaft ist dabei, dass durch zumindest ein Steuerelement sich sehr variabel eine Einstellung eines gewünschten AufStaudrucks an der Turbine erzielen lässt, wodurch sich neben der Einstellung der Motorbremsleistung auch die Abgasrückführrate gut einstellen lässt.It is advantageous that can be achieved by at least one control very variable setting of a desired AufStaudrucks on the turbine, whereby in addition to the setting of the engine braking power and the exhaust gas recirculation rate can be well adjusted.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert .An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Die Zeichnung zeigt in schematisch vereinfachter, teilweiser Schnittdarstellung eine Brennkraftmaschine 1, bei der es sich um einen Dieselmotor mit Motorbremse, insbesondere zum Einsatz für Nutzfahrzeuge, handelt. Die Erfindung ist prinzipiell aber auch auf Ottomotoren übertragbar. Die Brennkraftmaschine 1 weist einen Abgasturbolader 2 mit einer Turbine 3 im Abgasstrang 4 auf. Die Turbine 3 besitzt ein Turbinenrad 5, welches als Radialturbine ausgebildet ist und die Bewegung des Turbinenrades 5 über eine Welle 7 auf ein Verdichterrad 8 eines Verdichters 9 überträgt. Die Turbine 3 weist ein Turbinengehäuse 19 auf, welches zweiflutig mit zwei Fluten 14, 15 bzw. Einströmkanälen 16, 17 ausgebildet ist. Die beiden Fluten 14, 15 bzw. Einströmkanäle 16, 17 sind durch eine gehäusefeste Trennwand 18 des Turbinengehäuses 19 voneinander getrennt .The drawing shows in a schematically simplified, partial sectional view of an internal combustion engine 1, which is a diesel engine with engine brake, in particular for use for commercial vehicles, is. The invention is in principle but also transferable to gasoline engines. The internal combustion engine 1 has an exhaust gas turbocharger 2 with a turbine 3 in the exhaust gas line 4. The turbine 3 has a turbine wheel 5, which is designed as a radial turbine and transmits the movement of the turbine wheel 5 via a shaft 7 to a compressor wheel 8 of a compressor 9. The turbine 3 has a turbine housing 19, which is formed with two floods 14, 15 and inflow channels 16, 17, respectively. The two floods 14, 15 and inflow channels 16, 17 are separated from each other by a housing-fixed partition wall 18 of the turbine housing 19.
Über jede Flut 14, 15 bzw. Einströmkanal 16, 17 ist das Abgas separat zu dem Turbinenrad 5 zuführbar. Die AbgasZuführung erfolgt über den Abgasstrang 4, der in zwei unabhängig voneinander ausgebildete Abgas1eitungen, eine erste Abgas1eitung 20 und eine zweite Abgasleitung 21, aufgeteilt ist. Die erste Abgas1eitung 20 ist der ersten Flut 14 und die zweite Abgasleitung 21 ist der zweiten Flut 15 zugeordnet. Jede Abgasleitung 20, 21 ist einer definierten Anzahl von Zylinderauslässen der Brennkraftmaschine 1 zugeordnet. Im Ausführungsbeispiel weist die Brennkraftmaschine 1 sechs Zylinder auf, wobei eine erste Zylinderbank 23, drei Zylinder und eine zweite Zylinderbank 24, ebenfalls drei Zylinder aufweist. Denkbar ist neben der gleichförmigen Aufteilung der Zylinderbänke auch eine ungleichförmige. Die erste Abgasleitung 20 führt von der hier zugeordneten Zylinderbank 23 zum ersten Einströmkanal 16 der ersten Flut 14. Die zweite Abgasleitung 21 führt von der ihr zugeordneten zweiten Zylinderbank 24 zum zweiten Einströmkanal 17 der zweiten Flut 15.About each flood 14, 15 and inflow channel 16, 17, the exhaust gas can be supplied separately to the turbine wheel 5. The exhaust gas feed takes place via the exhaust gas line 4, which is divided into two independently formed exhaust gas lines, a first exhaust gas line 20 and a second exhaust line 21 is. The first exhaust gas line 20 is the first flow 14 and the second exhaust gas 21 is associated with the second flow 15. Each exhaust pipe 20, 21 is associated with a defined number of cylinder outlets of the internal combustion engine 1. In the exemplary embodiment, the internal combustion engine 1 six cylinders, wherein a first cylinder bank 23, three cylinders and a second cylinder bank 24, also has three cylinders. It is conceivable in addition to the uniform distribution of the cylinder banks and a non-uniform. The first exhaust pipe 20 leads from the cylinder bank 23 assigned here to the first inflow channel 16 of the first flow 14. The second exhaust pipe 21 leads from the second cylinder bank 24 assigned to it to the second inflow duct 17 of the second flow 15.
Zwischen den beiden Abgas1eitungen 20, 21 ist stromauf der Turbine 3 eine beide Abgas1eitungen 20, 21 verbindende Überbrückungsleitung 25 vorgesehen. In der Überbrückungsleitung 25 ist ein erstes Steuerelement 30 untergebracht, welches den Abgasstrom in der Überbrückungsleitung 25 steuern kann. Das erste Steuerelement 30 ist zum Beispiel als den Durchfluss steuerndes Ventil (Umblaseventil) oder als einstellbares Drosselorgan bzw. Klappe ausgebildet. In Offenstellung des ersten Steuerelements 30 ist ein Überströmen mit Druckausgleich zwischen den Abgas1eitungen 20, 21 möglich. Hingegen erfolgt in einer Schließstellung kein Druckausgleich zwischen den Abgas1eitungen 20, 21. Von der zweiten Abgasleitung 21 stromauf zur Turbine 3 zweigt eine Abblaseleitung 40 ab, in der ein drittes Steuerelement 33 eingebracht ist, welches ebenfalls als den Durchfluss steuerndes Ventil oder als Drosselorgan bzw. Klappe ausgebildet ist. In Offenstellung des dritten Steuerelements 33 wird der Abgasstrom um die zweite Flut 15 herum geführt und stromab des Turbinenrades 5 in eine anschließende Abgasleitung 10 geleitet.Between the two exhaust gas lines 20, 21 upstream of the turbine 3, a two exhaust gas lines 20, 21 connecting bridging line 25 is provided. In the bypass line 25, a first control element 30 is housed, which can control the exhaust gas flow in the bypass line 25. The first control element 30 is designed, for example, as a flow-controlling valve (blow-by valve) or as an adjustable throttle body or flap. In the open position of the first control element 30, an overflow with pressure equalization between the exhaust gas lines 20, 21 is possible. By contrast, no pressure equalization takes place between the exhaust gas lines 20, 21 from the second exhaust gas line 21 to the turbine 3 branches off a blow-off line 40, in which a third control 33 is introduced, which also serves as the flow control valve or throttle body or Flap is formed. In the open position of the third control element 33, the exhaust gas flow around the second flood 15 guided around and passed downstream of the turbine wheel 5 in a subsequent exhaust pipe 10.
Außerdem weist die Brennkraftmaschine 1 eine Abgasrückführung auf, die eine Rückführleitung 35, gegebenenfalls einen Abgaskühler 36 und ein zweites Steuerelement 32 umfasst. Das zweite Steuerelement 32 kann als ein den Durchfluss steuerndes Ventil (Abgasrückführventil) oder als Drosselorgan bzw. Klappe ausgebildet sein und ist stromauf der ersten Flut 14 und zum Beispiel stromauf des Abgaskühlers 36 in der Rückführleitung 35 angeordnet. Vorzugsweise ist eine Ausbildung des zweiten Steuerelements 32 als Schaltventil vorgesehen, das keine Zwischenstellung, sondern nur eine Offen- und eine Schließstellung einnehmen kann. Die Rückführleitung 35 mündet in einen Ansaugtrakt 6 der Brennkraftmaschine 1 stromab eines Ladeluftkühlers 37 für die Ansaugluft. Der Ansaugtrakt 6 umfasst den Verdichter 9 mit dem Verdichterrad 8, der Umgebungsluft mit dem Druck pl ansaugt und auf einen erhöhten Druck p2 verdichtet. Stromab des Verdichters 9 ist im Ansaugtrakt 6 der Ladeluftkühler 37 angeordnet, der von der verdichteten Luft durchströmt wird. Nach dem Verlassen des Ladeluftkühlers 37 weist die Luft den Ladedruck p2S auf, mit dem sie gegebenenfalls mit vermischtem Abgas aus der Rückführleitung 35 in den Zylindereinlass der Brennkraftmaschine 1 eingeleitet wird.In addition, the internal combustion engine 1 has an exhaust gas recirculation, which comprises a return line 35, optionally an exhaust gas cooler 36 and a second control element 32. The second control element 32 can be designed as a flow-controlling valve (exhaust gas recirculation valve) or as a throttle element or flap and is arranged upstream of the first flow 14 and, for example, upstream of the exhaust gas cooler 36 in the return line 35. Preferably, a design of the second control element 32 is provided as a switching valve, which can not assume an intermediate position, but only an open and a closed position. The return line 35 opens into an intake tract 6 of the internal combustion engine 1 downstream of a charge air cooler 37 for the intake air. The intake duct 6 comprises the compressor 9 with the compressor wheel 8, the ambient air with the pressure pl sucks and compressed to an increased pressure p2. Downstream of the compressor 9, the charge air cooler 37 is arranged in the intake tract 6, through which the compressed air flows. After leaving the intercooler 37, the air on the boost pressure P 2 S, with which it is optionally introduced with mixed exhaust gas from the return line 35 into the cylinder inlet of the internal combustion engine 1.
Vom Zylinderauslass herrscht in der ersten Abgasleitung 20, die der ersten Zylinderbank 23 zugeordnet ist, derFrom the cylinder outlet prevails in the first exhaust pipe 20, which is associated with the first cylinder bank 23, the
Abgasgegendruck p31; in der zweiten Abgasleitung 21, die der zweiten Zylinderbank 24 zugeordnet ist, liegt derExhaust back pressure p31; in the second exhaust pipe 21, which is associated with the second cylinder bank 24, is the
Abgasgegendruck p32 an. In der Turbine 3 wird das Abgas auf den niedrigen Druck p4 entspannt und im weiteren Verlauf über die an die Turbine 3 angeschlossene Abgasleitung 10 und einem nicht näher dargestellten Katalysator schließlich in die Umgebung abgeblasen.Exhaust back pressure p32 on. In the turbine 3, the exhaust gas is expanded to the low pressure p4 and in the further course via the connected to the turbine 3 exhaust pipe 10 and a not shown catalyst finally blown off into the environment.
Die zweite, größere Flut 15 wird so dimensioniert bzw. ausgelegt, dass ein gewünschter Ladedruck im befeuerten Betrieb erzielt werden kann. Die erste, kleinere Flut 14 wird so dimensioniert bzw. ausgelegt, dass eine geforderte Abgasrückführrate erzielt werden kann, wobei eine bestimmte Motorbremsleistung im Motorbremsbetrieb gewährleistet wird. Das Verhältnis des Eintrittsquerschnittes bzw. Haisquerschnittes von erster Flut 14 pro 1 1 Hubvolumen der Brennkraftmaschine 1 sollte dabei in einem Bereich vonThe second, larger flood 15 is dimensioned or designed so that a desired charge pressure can be achieved in the fired operation. The first, smaller tide 14 is dimensioned or designed so that a required exhaust gas recirculation rate can be achieved, whereby a certain engine braking power is ensured in engine braking operation. The ratio of the inlet cross-section or shark cross-section of the first flood 14 per 1 1 stroke volume of the internal combustion engine 1 should be in a range of
0.15 cm2/l bis 0.40 cm2/l liegen.0.15 cm 2 / l to 0.40 cm 2 / l lie.
Der Abgasstrom in den beiden unterschiedlich großen Fluten 14, 15 des asymmetrisch gestalteten Turbinengehäuses 19 kann von einem hülsenförmigen, axial beweglichen Schieber 50 gesteuert werden. Der Schieber 50 weist starre Leitschaufeln auf, die ein Leitgitter bilden, wozu die Leitschaufeln entsprechend über den Umfang verteilt angeordnet sind. Ein derartiger Schieber 50 ist zum Beispiel aus der DE 198 16 645 Al bekannt, dessen Offenbarung ausdrücklich Bestandteil der Beschreibung ist. In der Zeichnung ist der Schieber 50 in seiner Schließstellung angedeutet dargestellt, bei der zumindest beide Fluten 14, 15 von einem Leitgitterbereich des Schiebers 50 abgedeckt sind. Der hülsenförmige Schieber 50 umgibt mit seinem Leitgitterbereich das Turbinenrad 5 und wird bisher ausschließlich im nichtbefeuerten Betrieb der Brennkraftmaschine mehr oder weniger über einen Aktuator 70 eingeschoben, um über die Leitgitterschaufeln die Menge des Abgases gezielt auf das Turbinenrad 5 zu leiten, wodurch eine optimale Anpassung der Abgasmenge erfolgt, die zu einer Erhöhung der Abgasturboladerdrehzahl führt. Eine Erhöhung der Abgasturboladerdrehzahl führt wiederum zu einer Erhöhung der Verdichterleistung des Verdichters und damit zum Steigen des Ladedrucks p2s, was im nichtbefeuerten Betrieb der Brennkraftmaschine 1 wiederum die Motorbrems1eitung steigert.The exhaust gas flow in the two differently sized flows 14, 15 of the asymmetrically designed turbine housing 19 can be controlled by a sleeve-shaped, axially movable slide 50. The slider 50 has rigid vanes, which form a guide grid, to which the vanes are arranged distributed over the circumference accordingly. Such a slider 50 is known for example from DE 198 16 645 Al, the disclosure of which is expressly part of the description. In the drawing, the slider 50 is shown in its closed position indicated, in which at least both floods 14, 15 are covered by a Leitgitterbereich of the slider 50. The sleeve-shaped slide 50 surrounds with its Leitgitterbereich the turbine wheel 5 and is previously inserted only in non-fired operation of the internal combustion engine more or less via an actuator 70 to selectively guide the amount of exhaust gas on the turbine wheel 5 via the Leitgitterschaufeln, creating an optimal adaptation of Amount of exhaust gas takes place, which leads to an increase in the exhaust gas turbocharger speed. An increase in the exhaust gas turbocharger speed in turn leads to an increase in the Compressor capacity of the compressor and thus to increase the boost pressure p2s, which in turn increases the motor brake line in non-fired operation of the internal combustion engine 1.
Ferner ist es bekannt, bei hohen Motordrehzahlen bzw. hohen Abgasmengen die Abblaseinrichtung zu betätigen, die aus dem dritten Steuerelement 33 und der Abblaseleitung 40 besteht. In einer Offenstellung des dritten Steuerelements 33 erfolgt eine Umgehung des Turbinenrades 5 mit dem Abgas aus der zweiten Abgasleitung 21 in die Abblaseleitung 40. Das für die zweite Flut 15 vorgesehene Abgas wird über die Abblaseleitung 40 um das Turbinerad 5 herum geführt und in die Abgasleitung 10 geleitet. Die Menge ist dabei von dem dritten Steuerelement 33 entsprechend steuerbar, um so die Turbine 3 bzw. den Abgasturbolader 2 vor zu hohen Drehzahlen und zu hohen Ladedrücken zu schützen.Furthermore, it is known to operate at high engine speeds and high amounts of exhaust gas blower, which consists of the third control element 33 and the blow-off line 40. In an open position of the third control element 33, the turbine wheel 5 is bypassed with the exhaust gas from the second exhaust pipe 21 into the blow-off line 40. The exhaust gas provided for the second flow 15 is led around the turbine wheel 5 via the blow-off line 40 and into the exhaust pipe 10 directed. The amount is controlled accordingly by the third control element 33 so as to protect the turbine 3 and the exhaust gas turbocharger 2 against excessive rotational speeds and high boost pressures.
Erfindungsgemäß ist nun vorgesehen, den Schieber 50 mit dem Leitgitter auch im befeuerten Betrieb der Brennkraftmaschine einzuschieben bzw. zwischen dem Turbinenrad 5 und beiden Fluten 14, 15 einzubringen, um durch den sich dann einstellenden erhöhten Druck vor Turbine 3 p31 und p32, der größer ist als der Ladedruck P2s, eine effektive, mit hohen Abgasraten von mehr als 50 % gekennzeichnete Abgasrückführung zu erhalten. Die Betätigung des Schiebers 50 erfolgt in üblicher Weise mittels eines Aktuator 70, z. B. mittels Hebelmechanismus oder elektrischem, hydraulischem oder pneumatischem Stelltrieb oder dergleichen. Das Abgas wird aus den beiden Abgas1eitungen 21, 22 bei offenem ersten Steuerelement 30 und offenem zweiten Steuerelement 32 über die Rückführleitung 35 in den Ansaugtrakt 6 eingebracht. Eine Abgasrückführung ist dabei im normalen befeuerten Betrieb der Brennkraftmaschine von niedrigen bis hohen Drehzahlen durchführbar . Anstelle der aufgezeigten Schieberlösung ist es auch möglich, wie in der Zeichnung gestrichelt angedeutet ist, ein Leitgitter 60 mit verstellbaren Leitgitterschaufeln einzusetzen. Ein derartiges Leitgitter ist zum Beispiel aus der DE 197 52 534 Cl oder aus der DE 199 05 637 Cl bekannt, deren Offenbarung ausdrücklich Bestandteil der Anmeldung sein soll. Ähnlich der Schieberlösung ist vorgesehen, die Leitschaufeln mit dem Leitgitter 60 durch einen entsprechenden Aktuator 70 auch im befeuerten Betrieb der Brennkraftmaschine 1 in ihrem Durchströmquerschnitt so zu verengen, dass sich ein erhöhter Aufstaudruck vor Turbine 3 p31 und p32 ergibt, der größer ist als der Ladedruck P2s. Damit ist eine sehr effektive, mit hohen Abgasraten von mehr als 50 % gekennzeichnete Abgasrückführung möglich. Die Abgasrückführung ist dabei im normalen befeuerten Betrieb der Brennkraftmaschine von niedrigen bis hohen Drehzahlen möglich. Die Betätigung der verstellbaren Leitschaufeln des Leitgitters 60 erfolgt in üblicher Weise mittels eines Aktuator 70, z. B. mittels Hebelmechanismus oder elektrischem, hydraulischem oder pneumatischem Stelltrieb oder dergleichen. Das Abgas wird aus den beiden Abgasleitungen 21, 22 bei offenem ersten Steuerelement 30 und offenem zweiten Steuerelement 32 über die Rückführleitung 35 in den Ansaugtrakt 6 eingebracht. Eine Abgasrückführung ist dabei im normalen befeuerten Betrieb der Brennkraftmaschine von niedrigen bis hohen Drehzahlen durchführbar.According to the invention, it is now provided to insert the slide 50 with the guide grille also in the fired operation of the internal combustion engine or between the turbine wheel 5 and two floods 14, 15, in order then to set by the then increasing pressure before turbine 3 p31 and p32, which is larger as the boost pressure P2s, to obtain an effective, with high exhaust rates of more than 50% labeled exhaust gas recirculation. The operation of the slider 50 is carried out in the usual manner by means of an actuator 70, z. B. by lever mechanism or electric, hydraulic or pneumatic actuator or the like. The exhaust gas is introduced from the two exhaust gas lines 21, 22 with open first control element 30 and open second control element 32 via the return line 35 into the intake tract 6. Exhaust gas recirculation can be carried out in the normal fired operation of the internal combustion engine from low to high speeds. Instead of the indicated slide solution, it is also possible, as indicated by dashed lines in the drawing, to use a guide grid 60 with adjustable guide vanes. Such a guide grid is known, for example, from DE 197 52 534 C1 or from DE 199 05 637 C1, the disclosure of which is expressly to be part of the application. Similar to the valve solution is provided to narrow the guide vanes with the guide grid 60 by a corresponding actuator 70 in the fired operation of the internal combustion engine 1 in its flow area so that an increased back pressure before turbine 3 p31 and p32 results, which is greater than the boost pressure p2s. Thus, a very effective, with high exhaust gas rates of more than 50% characterized exhaust gas recirculation is possible. The exhaust gas recirculation is possible in the normal fired operation of the internal combustion engine from low to high speeds. The actuation of the adjustable guide vanes of the guide grid 60 is carried out in the usual manner by means of an actuator 70, for. B. by lever mechanism or electric, hydraulic or pneumatic actuator or the like. The exhaust gas is introduced from the two exhaust gas lines 21, 22 with open first control element 30 and open second control element 32 via the return line 35 into the intake tract 6. Exhaust gas recirculation can be carried out in the normal fired operation of the internal combustion engine from low to high speeds.
Zur Variation der Rückführrate des Abgases kann das erste Steuerelement 30 oder das zweite Steuerelement 32 auch eine entsprechende Durchflussstellung zwischen einer Offenstellung und einer Schließstellung einnehmen. Sämtliche Steuerelemente 30, 32, 33 können über Stellsignale, die in einer nicht näher dargestellten Regel- und Steuereinrichtung, zum Beispiel einem elektronischen Motorsteuergerät, erzeugbar sind, in ihre gewünschte Position verstellt werden, um so eine Steuerung der Durchflussmenge zu ermöglichen. In gleicher Weise ist über die Regel- und Steuereinrichtung auch eine Ansteuerung der Aktuatoren 70 für den Schieber 50 oder für das Leitgitter 60 mit verstellbaren Leitschaufeln möglich. To vary the recirculation rate of the exhaust gas, the first control element 30 or the second control element 32 can also assume a corresponding flow position between an open position and a closed position. All control elements 30, 32, 33 can be adjusted to their desired position via control signals which can be generated in a regulating and control device (not shown in detail), for example an electronic engine control unit, in order to enable control of the flow rate. In the same way, control of the actuators 70 for the slide 50 or for the guide grid 60 with adjustable guide vanes is also possible via the regulating and control device.

Claims

Patentansprüche claims
1. Verfahren zur Abgasrückführung für eine1. Method for exhaust gas recirculation for a
Brennkraftmaschine mit Abgasturbolader, wobei der Abgasturbolader eine Abgasturbine umfasst, die zwei separate, einem Turbinenrad der Abgasturbine vorgelagerte Strömungsfluten mit unterschiedlichem Querschnitt aufweist, dadurch gekennzeichnet, dass jede Strömungsflut (14; 15) mit jeweils einer Abgasleitung (20; 21) zur Versorgung mit Abgas verbunden ist, und über eine variable Turbinengeometrie (50; 60) eine Steuerung der Abgase auf die Abgasturbine (3) durchgeführt wird, wobei zur Abgasrückführung eine Abgasrückführleitung (35) von der zur kleineren Strömungsflut (14) gehörenden Abgasleitung (20) aus über ein Steuerelement (32) zu einem Ansaugtrakt (6) der Brennkraftmaschine (3) führt, wobei die variable Turbinengeometrie (50; 60) zusätzlich zur Betriebsweise der Brennkraftmaschine (1) als Motorbremse auch in einem befeuerten Betrieb der Brennkraftmaschine betätigt wird, wonach das Steuerelement (32) in seine Offenstellung gebracht wird und die Abgase in den Ansaugtrakt (6) der Brennkraftmaschine rückgeführt werden. Internal combustion engine with exhaust gas turbocharger, wherein the exhaust gas turbocharger comprises an exhaust gas turbine, which has two separate flow passages having a different cross section upstream of a turbine wheel of the exhaust gas turbine, characterized in that each flow passage (14, 15) is provided with an exhaust pipe (20, 21) for the supply of exhaust gas A control of the exhaust gases is performed on the exhaust gas turbine (3) via a variable turbine geometry (50; 60), wherein an exhaust gas recirculation line (35) from the exhaust line (20) belonging to the smaller flow flow (14) is connected to the exhaust gas recirculation Control element (32) leads to an intake tract (6) of the internal combustion engine (3), wherein the variable turbine geometry (50; 60) is actuated in addition to the mode of operation of the internal combustion engine (1) as an engine brake also in a fired operation of the internal combustion engine, after which the control ( 32) is brought into its open position and the exhaust gases in the intake (6) of the internal combustion engine are returned.
2. Verfahren zur Abgasrückführung nach Anspruch 1, dadurch gekennzeichnet, dass es sich bei der variablen Turbinengeometrie um einen Schieber (50) mit Leitgitter und Leitgitterschaufeln handelt, der zwischen den Fluten (14, 15) und dem Turbinenrad (5) eingebracht wird.2. A method for exhaust gas recirculation according to claim 1, characterized in that it is in the variable turbine geometry to a slide (50) with guide grid and Leitgitterschaufeln, which is introduced between the floods (14, 15) and the turbine wheel (5).
3. Verfahren zur Abgasrückführung nach Anspruch 1 , dadurch gekennzeichnet, dass es sich bei der variablen Turbinengeometrie um ein Leitgitter (60) mit verstellbaren Leitgitterschaufeln handelt, das zwischen den Fluten (14, 15) und dem Turbinenrad (5) eingebracht wird.3. A method for exhaust gas recirculation according to claim 1, characterized in that it is in the variable turbine geometry to a guide grid (60) with adjustable Leitgitterschaufeln, which is introduced between the floods (14, 15) and the turbine wheel (5).
4. Verfahren zur Abgasrückführung nach Anspruch 2 oder 3 , dadurch gekennzeichnet, dass im Abgasrückführbetrieb ein weiteres, den Durchfluss steuerndes Steuerelement (30) in einer beide Abgas1eitungen (20, 21) stromauf der Strömungsfluten (14, 15) verbindenden Überbrückungsleitung (25) geöffnet wird.4. A method for exhaust gas recirculation according to claim 2 or 3, characterized in that in the exhaust gas recirculation another, the flow controlling control (30) in a both Abgas1eitungen (20, 21) upstream of the flow passages (14, 15) connecting the bypass line (25) opens becomes.
5. Verfahren zur Abgasrückführung nach Anspruch 2 oder 3 , dadurch gekennzeichnet, dass zum Schutz des Abgasturboladers (2) ausgehend von der größeren Strömungsflut (15) von der zweiten Abgasleitung (21) eine Abblaseleitung (40) abzweigt, in der für die größere Strömungsflut (15) vorgesehenes Abgas in einer Offenstellung eines in der Abblaseleitung (40) vorgesehenen, dritten Steuerelements (33) strömt und eine Umgehung der Abgase um die Turbine (3) herum ermöglicht wird. 5. A method for exhaust gas recirculation according to claim 2 or 3, characterized in that for the protection of the exhaust gas turbocharger (2) starting from the larger flow trough (15) from the second exhaust pipe (21) branches off a blow-off line (40), in the larger flow (15) provided exhaust gas in an open position provided in the blow-off line (40), third control element (33) flows and a bypass of the exhaust gases around the turbine (3) around is made possible.
6. Verfahren zur Abgasrückführung nach Anspruch 5, dadurch gekennzeichnet, dass die Steuerelemente (30; 32; 33} als den Durchfluss steuernde Ventile oder als einstellbare Drosselorgane bzw. Klappen ausgebildet sind.6. A method for exhaust gas recirculation according to claim 5, characterized in that the control elements (30; 32; 33} are designed as flow-controlling valves or as adjustable throttle bodies or flaps.
7. Verfahren zur Abgasrückführung nach Anspruch 1, dadurch gekennzeichnet, dass das in der Rückführleitung (35) verbaute Steuerelement (32) als Schaltventil ausgebildet ist. 7. A method for exhaust gas recirculation according to claim 1, characterized in that in the return line (35) built-in control element (32) is designed as a switching valve.
PCT/EP2006/004135 2005-05-06 2006-05-03 Method for exhaust gas recirculation for an internal combustion engine having an exhaust gas turbocharger WO2007093195A1 (en)

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DE10152804A1 (en) * 2001-10-25 2003-05-08 Daimler Chrysler Ag Internal combustion engine with exhaust gas turbocharger and exhaust feedback, has ratio of sizes of exhaust gas turbine flow channels defined depending on total stroke volume of engine

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US4179892A (en) * 1977-12-27 1979-12-25 Cummins Engine Company, Inc. Internal combustion engine with exhaust gas recirculation
DE19857234A1 (en) * 1998-12-11 2000-06-29 Daimler Chrysler Ag Exhaust gas re-circulation device for turbo charged IC engines with exhaust return pipe and regulator unit to regulate pressure of returned exhaust gas to keep is above charging air pressure when required
DE10132672A1 (en) * 2001-07-05 2003-01-16 Daimler Chrysler Ag Exhaust gas turbocharger for internal combustion engine enables different flow rates through exhaust gas openings to be set by altering valve body position
DE10152804A1 (en) * 2001-10-25 2003-05-08 Daimler Chrysler Ag Internal combustion engine with exhaust gas turbocharger and exhaust feedback, has ratio of sizes of exhaust gas turbine flow channels defined depending on total stroke volume of engine

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