DE19541176C2 - Internal combustion engine with inert gas direct charging - Google Patents

Internal combustion engine with inert gas direct charging

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Publication number
DE19541176C2
DE19541176C2 DE19541176A DE19541176A DE19541176C2 DE 19541176 C2 DE19541176 C2 DE 19541176C2 DE 19541176 A DE19541176 A DE 19541176A DE 19541176 A DE19541176 A DE 19541176A DE 19541176 C2 DE19541176 C2 DE 19541176C2
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DE
Germany
Prior art keywords
internal combustion
combustion engine
engine according
overflow channel
charge
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.)
Expired - Fee Related
Application number
DE19541176A
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German (de)
Other versions
DE19541176A1 (en
Inventor
Erhard Schmieder
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Individual
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Individual
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Priority to DE19541176A priority Critical patent/DE19541176C2/en
Publication of DE19541176A1 publication Critical patent/DE19541176A1/en
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Publication of DE19541176C2 publication Critical patent/DE19541176C2/en
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F02D21/00—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas
    • F02D21/06—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air
    • F02D21/08—Controlling engines characterised by their being supplied with non-airborne oxygen or other non-fuel gas peculiar to engines having other non-fuel gas added to combustion air the other gas being the exhaust gas of engine
    • 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
    • F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
    • 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
    • F02B47/00—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines
    • F02B47/04—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines the substances being other than water or steam only
    • F02B47/08—Methods of operating engines involving adding non-fuel substances or anti-knock agents to combustion air, fuel, or fuel-air mixtures of engines the substances being other than water or steam only the substances including exhaust gas
    • 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
    • F02M26/41—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories characterised by the arrangement of the recirculation passage in relation to the engine, e.g. to cylinder heads, liners, spark plugs or manifolds; characterised by the arrangement of the recirculation passage in relation to specially adapted combustion chambers
    • 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
    • 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
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/20—Feeding recirculated exhaust gases directly into the combustion chambers or into the intake runners
    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Description

Bei heute üblichen Verbrennungsmotoren mit geradzahliger Zylin­ derzahl befinden sich jeweils zwei Kolben im Gleichlauf, das heißt, sie erreichen ihren oberen beziehungsweise unteren Tot­ punkt zur gleichen Zeit. Diese Zylinder befinden sich aber je­ weils in entgegengesetzter Arbeitstaktfolge.In today's common internal combustion engines with an even numbered cylinder the number are two pistons in synchronism, the means they reach their upper or lower dead point at the same time. However, these cylinders are each because in the opposite work cycle sequence.

Wenn der Abwärtshub des einen Kolbens ein Expansionshub ist, dann ist der des anderen Kolbens ein Ansaughub und umgekehrt.If the downward stroke of one piston is an expansion stroke, then that of the other piston is an intake stroke and vice versa.

Diese beiden Zylinderräume werden am Ende des Abwärtshubes, also unmittelbar am unteren Totpunkt,durch einen Überströmkanal mit­ einander verbunden, welcher nur in unterer Totpunktlage von den beiden Kolben freigegeben wird.These two cylinder spaces are at the end of the downstroke, so directly at bottom dead center, through an overflow channel connected to each other, which is only in the bottom dead center position of the both pistons is released.

Durch Freigabe dieses Überströmkanals strömt Abgas höheren Druckes von einem Zylinder in den anderen Zylinder, welcher gerade das Ansaugen von Frischgas beendet hat.By opening this overflow channel, exhaust gas flows at a higher pressure from one cylinder to the other cylinder, which is straight has stopped sucking in fresh gas.

Dieser Überströmvorgang läuft also in jeder unteren Todpunktla­ ge der beiden Kolben zwischen den korrelierenden Zylindern je­ weils wechselweise entgegengesetzt ab.This overflow process therefore runs in every lower dead center ge of the two pistons between the correlating cylinders each because alternately opposite.

Dadurch entsteht im Zylinder eine ideale Schichtladung - oben befindet sich stets Frischgas, während sich im unteren Zylinder­ raum das an der Verbrennung nicht beteiligte Abgas konzentriert.This creates an ideal stratified charge in the cylinder - above there is always fresh gas, while in the lower cylinder the exhaust gas not involved in the combustion is concentrated.

Der Überströmkanal nach Fig. 1 verbindet die Zylinderräume un­ mittelbar miteinander.The overflow according to Fig. 1 connects the cylinder chambers un indirectly with each other.

Fig. 2 zeigt eine Reihe von Möglichkeiten auf, die Zylinderräu­ me mit mehr oder weniger langen Kanälen paarweise miteinander zu verbinden, was eine Kühlung des überströmenden Gases ermöglicht. Fig. 2 shows a number of ways to connect the Zylinderräu me with more or less long channels in pairs, which allows cooling of the overflowing gas.

Der Überströmkanal kann im Querschnitt sowohl konstant als auch variabel ausgelegt sein.The overflow channel can be both constant and in cross section be designed variably.

Durch Schrägstellen des Überströmkanals am Zylindereingang kann ein Drallwirbel um die Zylinderachse erzeugt werden.By tilting the overflow channel at the cylinder inlet a vortex around the cylinder axis are generated.

Die Überströmrate des Abgases läßt sich in Menge und Druck durch den Schließzeitpunkt des Einlaßventils, durch den Öffnungszeit­ punkt des Auslaßventils sowie durch den Querschnitt des Über­ strömkanals festlegen.The overflow rate of the exhaust gas can be measured in quantity and pressure the closing time of the intake valve, by the opening time point of the exhaust valve and through the cross section of the over set the flow channel.

Diesen Variationsmöglichkeiten entsprechend kann das überströ­ mende Abgas als Ausgleichladung bei gedrosselter Ansaugung, zum Beispiel bei Teillastdrosselung, als Verdrängungsladung für den Teillastbetrieb bei ungedrosselter Ansaugung sowie als Über­ druckladung wirken.Corresponding to these possible variations, this can overflow exhaust gas as compensation charge with throttled intake, for Example with partial load throttling, as a displacement charge for the Part load operation with unthrottled intake as well as over pressure charge act.

Dieses Verfahren einer Inertgasdirektaufladung ist vorgesehen für Verbrennungsmotoren mit Selbst- und Fremdzündung und führt zu Emissionsverminderung und Kraftstoffeinsparung, weil hierbei nicht nur erhebliche Ladungswechselarbeit eingespart wird, son­ dern es werden bei optimaler Schichtladung maximale Verdichtung sowie maximale Verbrennungsbedingungen erreicht. This method of direct inert gas charging is provided for internal combustion engines with spark and spark ignition and leads to reduce emissions and save fuel because of this not only is considerable charge-change work saved, son maximum compression with optimal stratified charge as well as maximum combustion conditions reached.  

Nach dem vorliegenden Stand der Technik ist eine strömungs­ technische Verbindung zweier oder mehrerer Zylinder im unteren Totpunktbereich nicht neu.According to the current state of the art, there is a flow technical connection of two or more cylinders in the lower one Dead center area not new.

Ein Vorschlag gemäß DE-AS 1 003 986 hat das Ziel, einen bereits geladenen Zylinder mit Frischgas nachzuladen unter Ausnutzung der im adiabatischen Auspuffstoß enthaltenen Energie.A proposal according to DE-AS 1 003 986 has the goal of one recharged cylinder with fresh gas using the energy contained in the adiabatic exhaust.

Der Nachteil dieses Vorschlages besteht darin, daß außer den Zylinderschlitzen ein Nachladerohr und zusätzliche Steueror­ gane erforderlich sind.The disadvantage of this proposal is that in addition to the Cylinder slots, a reloading tube and additional control unit gane are required.

Ein Vorschlag gemäß DE 30 17 190 A1 hat das Ziel, die Abgas­ wärme zum Vorwärmen und Verdichten des Frischgases vor Eintritt in den Zylinder zu nutzen.A proposal according to DE 30 17 190 A1 has the goal of exhaust gas heat to preheat and compress the fresh gas before entering to use in the cylinder.

Der Nachteil dieses Vorschlages besteht darin, daß außer den Zylinderschlitzen ein Erhitzer und Schubstangen benötigt wer­ den.The disadvantage of this proposal is that in addition to the Cylinder slots a heater and push rods are needed for anyone the.

Der vorliegende Verbrennungsmotor mit Inertgasdirektaufladung unterscheidet sich vom aufgezeigten Stand der Technik dadurch, daß hierbei die Energie des Abgases zur Nachladung beziehungs­ weise Aufladung von Abgas eines bereits mit Frischgas gelade­ nen Zylinders genutzt wird.The present internal combustion engine with direct inert gas charging differs from the prior art shown in that that here the energy of the exhaust gas for reloading wise charging of exhaust gas already loaded with fresh gas NEN cylinder is used.

Außerdem besteht der Vorteil gegenüber dem aufgezeigten Stand der Technik darin, daß hierfür lediglich ein Überströmschlitz oder -kanal erforderlich ist.There is also the advantage over the status shown the technology in that for this only an overflow slot or channel is required.

Claims (13)

1. Verbrennungsmotor mit Inertgasdirektaufladung mit Selbst- oder/und Fremdzündung, dadurch gekennzeichnet, daß jeweils zwei Zylinderräume mit gleichlaufenden Kol­ ben, aber entgegengesetzter Arbeitstaktfolge, im unteren Totpunktbereich durch einen Überströmkanal miteinander verbunden werden. 1. Internal combustion engine with inert gas direct charging with auto-ignition and / or spark ignition, characterized in that in each case two cylinder spaces with synchronous Kol ben, but opposite work cycle sequence, are connected to one another in the bottom dead center area by an overflow channel. 2. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß das überströmende Abgas in den korrelierenden Zylindern eine Überdruckladung in Form einer Schichtladung erzeugt.2. Internal combustion engine according to claim 1, characterized, that the overflowing exhaust gas in the correlating cylinders generates an overpressure charge in the form of a stratified charge. 3. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß das überströmende Abgas in den korrelierenden Zylindern eine Verdrängungsladung in Form einer Schichtladung erzeugt.3. Internal combustion engine according to claim 1, characterized, that the overflowing exhaust gas in the correlating cylinders generates a displacement charge in the form of a stratified charge. 4. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß das überströmende Abgas in den korrelierenden Zylindern eine Ausgleichladung in Form einer Schichtladung erzeugt.4. Internal combustion engine according to claim 1, characterized, that the overflowing exhaust gas in the correlating cylinders generates an equalizing charge in the form of a stratified charge. 5. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß der Überströmkanal in unterschiedlicher Länge und dadurch auch als Kühlkanal ausgelegt werden kann.5. Internal combustion engine according to claim 1, characterized, that the overflow channel in different lengths and thereby can also be designed as a cooling duct. 6. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß der Überströmkanal im Querschnitt sowohl konstant als auch variabel ausgelegt werden kann.6. Internal combustion engine according to claim 1, characterized, that the cross-section of the overflow channel is both constant and can also be designed variably. 7. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß durch Schrägstellen des Überströmkanals am Zylinderein­ gang ein Drallwirbel um die Zylinderachse oder in Richtung der Zylinderachse erzeugt werden kann.7. Internal combustion engine according to claim 1, characterized, that by inclining the overflow channel on the cylinder swirl around the cylinder axis or in the direction the cylinder axis can be generated. 8. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß durch Einbringen unterer Kolbenringe die Überdruckladung aus einem langen Überströmkanal während des Arbeitsspieles nicht entweichen kann, wobei der Kolbenbolzen gasdicht im Kolben sitzen muß. 8. Internal combustion engine according to claim 1, characterized, that by introducing lower piston rings the overpressure charge from a long overflow channel during the work cycle can not escape, the piston pin gas-tight in Piston must sit.   9. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß der Überströmkanal in der Zylinderwand als Durchbruch beliebiger Geometrie oder in ein oder mehreren Bohrungen ausgelegt werden kann.9. Internal combustion engine according to claim 1, characterized, that the overflow channel in the cylinder wall as an opening any geometry or in one or more holes can be interpreted. 10. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß der Kolbenboden unverändert oder im Bereich des Zylin­ derwanddurchbruches zum Überströmkanal hin abgeschrägt ist.10. Internal combustion engine according to claim 1, characterized, that the piston crown unchanged or in the area of the cylin the wall opening is chamfered towards the overflow channel. 11. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß aufgrund optimaler Schichtladung der Verbrennungsmotor mit Fremdzündung sowohl mit Benzin als auch mit Dieselkraft­ stoff betrieben werden kann.11. Internal combustion engine according to claim 1, characterized, that due to optimal stratified charge the internal combustion engine with spark ignition with both gasoline and diesel power can be operated. 12. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß aufgrund optimaler Schichtladung Benzin direkt oder in­ direkt eingespritzt werden kann.12. Internal combustion engine according to claim 1, characterized, that due to optimal stratified gasoline directly or in can be injected directly. 13. Verbrennungsmotor nach Patentanspruch 1, dadurch gekennzeichnet, daß sowohl flüssiger als auch gasförmiger Kraftstoff ein­ gesetzt werden kann.13. Internal combustion engine according to claim 1, characterized, that both liquid and gaseous fuel can be set.
DE19541176A 1995-11-04 1995-11-04 Internal combustion engine with inert gas direct charging Expired - Fee Related DE19541176C2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19541176A DE19541176C2 (en) 1995-11-04 1995-11-04 Internal combustion engine with inert gas direct charging

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19541176A DE19541176C2 (en) 1995-11-04 1995-11-04 Internal combustion engine with inert gas direct charging

Publications (2)

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DE19541176A1 DE19541176A1 (en) 1997-05-07
DE19541176C2 true DE19541176C2 (en) 1998-07-02

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DE19541176A Expired - Fee Related DE19541176C2 (en) 1995-11-04 1995-11-04 Internal combustion engine with inert gas direct charging

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19830300C2 (en) 1998-07-07 2000-05-18 Bosch Gmbh Robert Method for operating an internal combustion engine, in particular a motor vehicle
US6880500B2 (en) 2002-10-04 2005-04-19 Honeywell International, Inc. Internal combustion engine system
FR2864999B1 (en) * 2004-01-12 2006-03-03 Renault Sas THERMAL ENGINE AND METHOD FOR INJECTING BURNED GASES

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1003986B (en) * 1954-12-22 1957-03-07 Maschf Augsburg Nuernberg Ag Four-stroke internal combustion engine
DE3017190A1 (en) * 1980-05-05 1981-11-12 Heinrich 7915 Elchingen Bellan Combined heat and IC engine - has alternating cylinder pairs connected by exhaust gas heat exchanger

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1003986B (en) * 1954-12-22 1957-03-07 Maschf Augsburg Nuernberg Ag Four-stroke internal combustion engine
DE3017190A1 (en) * 1980-05-05 1981-11-12 Heinrich 7915 Elchingen Bellan Combined heat and IC engine - has alternating cylinder pairs connected by exhaust gas heat exchanger

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Publication number Publication date
DE19541176A1 (en) 1997-05-07

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