DE3715750A1 - Internal-Combustion Engine - Google Patents

Internal-Combustion Engine

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Publication number
DE3715750A1
DE3715750A1 DE19873715750 DE3715750A DE3715750A1 DE 3715750 A1 DE3715750 A1 DE 3715750A1 DE 19873715750 DE19873715750 DE 19873715750 DE 3715750 A DE3715750 A DE 3715750A DE 3715750 A1 DE3715750 A1 DE 3715750A1
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Germany
Prior art keywords
combustion engine
piston
internal combustion
engine according
combustion chamber
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.)
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Application number
DE19873715750
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German (de)
Inventor
Joern Martens
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MARTENS, JOERN, 27711 OSTERHOLZ-SCHARMBECK, DE
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Individual
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Priority to DE19873715750 priority Critical patent/DE3715750A1/en
Publication of DE3715750A1 publication Critical patent/DE3715750A1/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
    • F02B73/00—Combinations of two or more engines, not otherwise provided for
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/02—Engines with reciprocating-piston pumps; Engines with crankcase pumps
    • F02B33/06—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps
    • F02B33/10—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder
    • F02B33/14—Engines with reciprocating-piston pumps; Engines with crankcase pumps with reciprocating-piston pumps other than simple crankcase pumps with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder working and pumping pistons forming stepped piston
    • 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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • 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
    • F02B75/00—Other engines
    • F02B75/28—Engines with two or more pistons reciprocating within same cylinder or within essentially coaxial 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
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Abstract

Internal-combustion engine, having an annular combustion space (1) and inlet (4) and outlet (5) channels opening tangentially into the latter, the fresh air flowing into the cylinder (3) being set into rotation about the connecting rod (7) located centrally in the combustion space (1). These unilaterally directed gas dynamics are also continued during the following strokes. A second piston (11) which is connected firmly to the smaller piston (2) via a rod (10), can take over both the supercharging and the afterexpansion of the combustion gases from the cylinder (3); an interspace (15), located between the two pistons (2,11) acts as a pumping space for cooling and lubricating fluid. In a version of the engine as a fuel-injection diesel engine, the injection takes place directly through the inlet valve (6), at the tip of which the injection valve (21) is arranged. <IMAGE>

Description

Verbrennungskraftmaschinen, die durch die Verbren­ nung eines Energieträgers in einem Brennraum (1) mechanische Energie direkt erzeugen, indem der Verbren­ nungsdruck einen Kolben (2), der den Brennraum (1) ein­ seitig begrenzt, verschiebt, und so den Zylinderraum vergrößert, wobei der Kolben (2), meist über eine Pleuelstange (7) und eine Kurbelwelle, die mecha­ nische Energie überträgt, sind aus Fachliteratur und Patenschriften in mannigfacher Ausführung be­ kannt.Internal combustion engines that generate mechanical energy directly by the combustion of an energy source in a combustion chamber ( 1 ) by the combustion pressure displacing a piston ( 2 ) which limits the combustion chamber ( 1 ) on one side, and thus enlarges the cylinder chamber, the Pistons ( 2 ), usually via a connecting rod ( 7 ) and a crankshaft that transmits mechanical energy, are known from specialist literature and patent documents in a variety of designs.

Wirkungsgrad, Leistungsgewicht, Lebensdauer, Abgas- und Leistungsverhalten und die Geräuschemis­ sion sind vielfach verbessert worden und, so die Forderung, noch weiter zu verbessern. Speziell dem Strömungsverhalten der Gase im Brennraum (1), der Aufladung und der möglichen Nutzung der Restenergie der Abgase wurde bei der Suche nach einem akzepta­ blem Kompromiß viel Aufmerksamkeit geschenkt. So auch bei der erfindungsgemäßen Konstruktion, bei der hauptsächlich in der Ausführung an einen selbstzün­ denden Verbrennungsmotor nach dem bekannten 4-Takt Diesel-Prinzip gedacht wurde, "Viertaktdieselmotor nach dem Ringkammerverfahren" von mir genannt.Efficiency, power-to-weight ratio, service life, exhaust gas and performance behavior and noise emission have been improved many times and, according to the demand, should be improved even further. Much attention has been paid in particular to the flow behavior of the gases in the combustion chamber ( 1 ), the charging and the possible use of the residual energy of the exhaust gases in the search for an acceptable compromise. So also in the construction according to the invention, in which the design of a self-igniting internal combustion engine based on the well-known 4-stroke diesel principle was thought of, "four-stroke diesel engine according to the ring chamber method" by me.

Bei der erfindungsgemäßen Konstruktion (Fig. 1-6) wird die Frischluft durch den Einlaßkanal (4) über das Ventil (6) in den Brennraum (1) geleitet (Fig. 1). Dabei wird die Frischluft bei geöffnetem Ventil (14) durch den Kolben (2) vorkomprimiert (Fig. 1-2).In the construction according to the invention ( Fig. 1-6), the fresh air is passed through the inlet duct ( 4 ) via the valve ( 6 ) into the combustion chamber ( 1 ) ( Fig. 1). The fresh air is pre-compressed by the piston ( 2 ) when the valve ( 14 ) is open ( Fig. 1-2).

Der Frischlufteintritt in den Brennraum (1) erfolgt dabei so, daß im Brennraum (1) eine möglichst gleich­ gerichtete Luftströmung um die Pleuelstange (7) herum entsteht (Fig. 1, 6). Diese Rotation der Frischluft im Zylinderraum (1) bleibt auch in der folgenden Kom­ pressionsphase weitgehend erhalten. Der durch das er­ findungsgemäße Einspritzventil (20′) eingespritzte Kraftstoff wird zentral in der Strömungsrichtung der Frischluft eingebracht. Die schädliche Kondensation des Kraftstoffs an den Zylinderwänden wird so redu­ ziert, die bereits vorhandene Gasdynamik im Zylinder (3′) induziert einen entsprechend gerichteten Verbren­ nungsablauf im Brennraum (1′), die Verbrennung des ein­ gespritzten Kraftstoffs erfolgt gleichmäßiger und "weicher" in der Arbeitsphase (Fig. 3). Danach wird, bei geöffnetem Auslaßventil (6′) das Abgas über die Verbindungsleitung und das Einlaßventil (13) in den Raum (12) eingebracht und hier nachexpandiert, die Energie der Abgase also noch teilweise genutzt und in mechanische Energie umgesetzt, bevor das Abgas über ein Auslaßventil (14) und evtl. z. B. eine An­ lage zur katalytischen Nachverbrennung der Abgase (22) an dieAtmosphäre abgegeben wird. In den an­ deren Zylinder (2′) wird gleichzeitig über ein Ein­ laßventil (13′) Frischluft eingebracht.The fresh air inlet into the combustion chamber (1) is effected such that in the combustion chamber (1) a possible rectified air flow around the connecting rod (7) is formed around (Fig. 1, 6). This rotation of the fresh air in the cylinder space ( 1 ) remains largely intact in the following compression phase. The fuel injected by the inventive injection valve ( 20 ' ) is introduced centrally in the flow direction of the fresh air. The harmful condensation of the fuel on the cylinder walls is thus reduced, the already existing gas dynamics in the cylinder ( 3 ' ) induces a correspondingly directed combustion process in the combustion chamber ( 1' ), the combustion of the injected fuel takes place more evenly and "softer" in the Working phase ( Fig. 3). Then, with the exhaust valve ( 6 ' ) open, the exhaust gas is introduced into the space ( 12 ) via the connecting line and the intake valve ( 13 ) and expanded again here, so the energy of the exhaust gases is still partially used and converted into mechanical energy before the exhaust gas is exhausted an outlet valve ( 14 ) and possibly z. B. A system for catalytic afterburning of the exhaust gases ( 22 ) is released into the atmosphere. In the other at the cylinder ( 2 ' ) fresh air is introduced simultaneously via a inlet valve ( 13' ).

Bei der Bewegung vom oberen Totpunt (O.T) in den unteren Totpunkt (U.T) vergrößert sich das Vo­ lumen der Zwischenkammern (15′-15′′) zwischen den Rückseiten der beiden Kolben (2′, 11′) (2′′, 11′′), in die so, aus den Zwischenkammern (15′′′, 15′′′′) einer vorhandenen zweiten "Twin-Einheit" deren Kolben eine gegenläufige Bewegungsrichtung aufweisen, Kühlmittel durch einen Wärmetauscher (19) über eine Verbindungs­ leitung (17) strömen kann. Das Kühlmittel kann dabei noch für die Kühlung des Zylinderdeckels (8) usw. herangezogen werden, eine spezielle Kühlmittelpumpe erübrigt sich. Rückschlagventile (24, 25) sorgen für eine einheitliche, gleichbleibende Strömungsrichtung in den Verbindungsrohren (16, 17). Durch Verzicht auf die Wasserpumpe und mit dem integrierten Lader gelang es bei der erfindungsgemäßen Konstruktion die Anzahl der beweglichen Teile und notwendigen An- und Ab­ triebe im Vergleich zu herkömmlichen, vergleichbaren Verbrennungsmotoren mit Ladern zu senken. Die erfin­ dungsgemäße Konstruktion von Zylinder, Kolben und Ven­ tilen verbessert Wirkungsgrad, Geräusch- und Abgasver­ halten und das Leistungsgewicht. Die Ausführung mit Wasser als Kühl- und Schmiermittel in der Zwischen­ kammer (z. B. 15) erfordert natürlich eine spezielle Materialwahl bei Kolben (2, 11) und Zylinder (3, 23). Keramisches Material bietet sich hier an. Das an den Zylinderwänden verdampfende Wasser wirkt sich vergleich­ mäßigend auf die Verbrennung und auch wirkungsgrad­ steigernd aus, die Schadstoffemission wird, speziell bezüglich ihres Ruß-Anteils, positiv beeinflußt.When moving from top dead center (OT) to bottom dead center (UT) , the volume of the intermediate chambers ( 15'-15 '' ) between the rear sides of the two pistons ( 2 ', 11' ) ( 2 '', 11 '' ), In which, from the intermediate chambers ( 15 ''',15'''' ) of an existing second "twin unit" whose pistons have an opposite direction of movement, coolant through a heat exchanger ( 19 ) via a connecting line ( 17 ) can flow. The coolant can also be used for cooling the cylinder cover ( 8 ) etc., a special coolant pump is not necessary. Check valves ( 24, 25 ) ensure a uniform, constant flow direction in the connecting pipes ( 16, 17 ). By dispensing with the water pump and with the integrated loader, the number of moving parts and necessary drives and drives in the construction according to the invention was able to be reduced compared to conventional, comparable internal combustion engines with loaders. The design of the cylinder, piston and valves according to the invention improves efficiency, noise and exhaust gas behavior and the power / weight ratio. The version with water as a coolant and lubricant in the intermediate chamber (e.g. 15 ) naturally requires a special choice of material for pistons ( 2, 11 ) and cylinders ( 3, 23 ). Ceramic material lends itself here. The water evaporating on the cylinder walls has a moderating effect on the combustion and also increases efficiency, the pollutant emission, especially with regard to its soot content, is positively influenced.

Claims (13)

1. Verbrennungskraftmaschine mit mindestens einem Brenn­ raum (1), dessen Volumen durch mindestens einen, in einem Zylinder (3) befindlichen Kolben (2) bestimmt wird, dadurch gekennzeichnet, daß der Brennraum (1) ringförmig mit annähernd kreisförmigem Querschnitt gestaltet ist, und, daß die imaginären Längsachsen des Einlaßkanals (4) und des Auslaßkanals (5) in etwa tangential zur imaginären Kurve angeordnet sind, die durch die imaginären Querschnittsmittel­ punkte der, in gedachten, parallel zur Bewegungs­ richtung des Kolbens ausgeführten Schnitten, entstehenden imaginären Segmente des Brennraumes (1) verläuft, und die imaginären Längsachsen des Einlaßkanals (4) und des Auslaßkanals (5) und der Ventile (6) in etwa parallel zueinander ver­ laufen.1. Internal combustion engine with at least one combustion chamber ( 1 ), the volume of which is determined by at least one piston ( 2 ) located in a cylinder ( 3 ), characterized in that the combustion chamber ( 1 ) is annular in shape with an approximately circular cross section, and That the imaginary longitudinal axes of the inlet channel ( 4 ) and the outlet channel ( 5 ) are arranged approximately tangentially to the imaginary curve, which points through the imaginary cross-sectional centers of the imaginary segments made parallel to the direction of movement of the piston, resulting imaginary segments of the combustion chamber ( 1 ), and the imaginary longitudinal axes of the inlet channel ( 4 ) and the outlet channel ( 5 ) and the valves ( 6 ) run approximately parallel to each other ver. 2. Verbrennungskraftmaschine nach Anspruch 1, dadurch gekennzeichnet, daß die Pleuelstange (7) zwischen Kolben (2) und Kurbelwelle (23) zentral die innere Begrenzung des Brennraumes (1) darstellt, die druck­ dicht durch den Zylinderdeckel (8) mittels Dichtringen (9), die vorzugsweise am Zylinderdeckel (8) befestigt sind, geführt ist.2. Internal combustion engine according to claim 1, characterized in that the connecting rod ( 7 ) between the piston ( 2 ) and crankshaft ( 23 ) represents the inner boundary of the combustion chamber ( 1 ), the pressure tight through the cylinder cover ( 8 ) by means of sealing rings ( 9 ), which are preferably attached to the cylinder cover ( 8 ). 3. Verbrennungskraftmaschine nach Anspruch 1-2, dadurch gekennzeichnet, daß der Kolben (2), der den Brenn­ raum (1) begrenzt, auf der, dem Brennraum (1) abge­ wandten Seite, über eine Stange (10) mit einem zweiten Kolben (11) verbunden ist, der einen Raum (12) begrenzt, der mindestens ein Einlaßventil (13) und ein Auslaßventil (14) besitzt.3. Internal combustion engine according to claims 1-2, characterized in that the piston (2) which space the focal limited (1) which eclip on, the combustion chamber (1) facing side, via a rod (10) with a second piston ( 11 ) is connected, which delimits a space ( 12 ) which has at least one inlet valve ( 13 ) and one outlet valve ( 14 ). 4. Verbrennungskraftmaschine nach Anspruch 1-3, dadurch gekennzeichnet, daß die, vom Brennraum (1) abgewandte Seite des Kolbens (2) der den Brennraum (1) begrenzt und die, diesem Kolben (2) zugewandte Seite des Kolbens (11), der den anderen Raum (12) begrenzt, mit der Innen­ wand des Zylinders (3) eine Zwischenkammer (15) bilden die mit einer Flüssigkeit gefüllt ist.4. Internal combustion engine according to claims 1-3, characterized in that the side facing away from the combustion chamber ( 1 ) of the piston ( 2 ) delimits the combustion chamber ( 1 ) and the side of the piston ( 11 ) facing this piston ( 2 ), which limits the other space ( 12 ), with the inner wall of the cylinder ( 3 ) form an intermediate chamber ( 15 ) which is filled with a liquid. 5. Verbrennungskraftmaschine nach Anspruch 1-4, dadurch gekennzeichnet, daß die Flüssigkeit in der Zwischen­ kammer (15) als Kühl- und Schmiermittel mindestens für Kolben (2, 11) und Zylinder wirkt.5. Internal combustion engine according to claims 1-4, characterized in that the liquid in the intermediate chamber ( 15 ) acts as a coolant and lubricant at least for pistons ( 2, 11 ) and cylinders. 6. Verbrennungskraftmaschine nach Anspruch 1-5, dadurch gekennzeichnet, daß die den Brennraum (1) begrenzende Fläche des Kolbens (2) weitaus kleiner als die den anderen Raum (12) begrenzende Fläche des zweiten Kol­ bens (11) ist, und das Volumen der Zwischenkammer (15), abhängig vom Kolbenweg, in dem, der Brennkammer (1) zugewandten "oberen Totpunkt" sein Minimum erreicht und im anderen, "unteren Totpunkt", sein Maximum erreicht, und die Zwischenkammer mindestens eine Ver­ bindungsleitung (16, 17) aufweist.6. Internal combustion engine according to claims 1-5, characterized in that the combustion chamber ( 1 ) delimiting surface of the piston ( 2 ) is much smaller than the other space ( 12 ) delimiting surface of the second piston ( 11 ), and the volume the intermediate chamber ( 15 ), depending on the piston travel, in which the combustion chamber ( 1 ) facing "top dead center" reaches its minimum and in the other, "bottom dead center", reaches its maximum, and the intermediate chamber at least one Ver connecting line ( 16, 17th ) having. 7. Verbrennungskraftmaschine nach Anspruch 1-6, dadurch gekennzeichnet, daß jeweils zwei Zylinder (3′) (3′′) zu einer "Twin-Einheit" (18) zusammengefaßt sind, wobei jeweils ein Raum (z. B. 12′′), einerseits über zumindest ein Einlaßventil (i. B. 14′′) mit der Atmos­ phäre und andererseits über zumindest ein Auslaß­ ventil (i. B. 13′′) mit den Einlaßkanälen (i. B. 4′, 4′′) der Brennräume (1′, 1′′) verbunden ist und jeweils der andere Raum (i. B. 12′) einerseits über zumindest ein Einlaßventil (i. B. 13′) mit den Auslaßkanälen (5′, 5′′) der entsprechenden Brennräume (1′, 1′′) und andererseits über mindestens ein Auslaßventil (i. B. 14′) mit der Atmosphäre verbunden ist.7. Internal combustion engine according to claims 1-6, characterized in that in each case two cylinders ( 3 ' ) ( 3'' ) are combined to form a "twin unit" ( 18 ), each having a space (for example 12'' ), on the one hand via at least one inlet valve (e.g. 14 '' ) with the atmosphere and on the other hand via at least one outlet valve (e.g. 13 '' ) with the inlet channels (e.g. 4 ', 4'' ) of the combustion chambers ( 1 ′, 1 ′ ′ ) and the other chamber (i. B. 12 ′ ) on the one hand via at least one inlet valve (i. B. 13 ′ ) with the outlet channels ( 5 ′, 5 ′ ′ ) the corresponding combustion chambers ( 1 ', 1'' ) and on the other hand is connected to the atmosphere via at least one exhaust valve (i. B. 14' ). 8. Verbrennungskraftmaschine nach Anspruch 1-7, dadurch gekennzeichnet, daß die Verbindungsleitungen (16, 17) der Zwischenkammern (15′, 15′′) paarweise so ausgeführt sind, daß die Störung durch sie hindurch jeweils nur in einer Richtung pro Rohr erfolgt.8. Internal combustion engine according to claims 1-7, characterized in that the connecting lines ( 16, 17 ) of the intermediate chambers ( 15 ', 15'' ) are carried out in pairs so that the fault occurs through them only in one direction per tube. 9. Verbrennungskraftmaschine nach Anspruch 1-8, dadurch gekennzeichnet, daß eine "Twin-Einheit" (18) mit einer zweiten "Twin-Einheit" (18′) kombiniert wird, deren Kolben (2′′′, 11′′′) (2′′′′, 11′′′′) sich in gegen­ läufiger Richtung zu denen der erstgenannten (18) bewegen, wobei die Zwischenkammern (15′, 15′′) der einen "Twin-Einheit" (18) mit denen der anderen über Verbin­ dungsleitungen (16, 17) miteinander verbunden sind, die, zwischengeschaltet, einen Wärmetauscher aufweisen.9. Internal combustion engine according to claims 1-8, characterized in that a "twin unit" ( 18 ) is combined with a second "twin unit" ( 18 ' ), the pistons ( 2''', 11 ''' ) ( 2 '''', 11 '''' ) move in the opposite direction to those of the former ( 18 ), the intermediate chambers ( 15 ', 15'' ) of a "twin unit" ( 18 ) with those the other are connected to one another via connecting lines ( 16, 17 ) which, connected in between, have a heat exchanger. 10. Verbrennungskraftmaschine nach Anspruch 1-9, dadurch gekennzeichnet, daß die Einspritzventile (20) für den Kraftstoff integriertes Bestandteil der Einlaßventile (6) sind, und die Ventile in ihrer äußeren Form in etwa einen Stromlinienkörper darstellen, dessen imagi­ näre Längsachse zugleich der Ventilbewegungsrichtung entspricht, und an deren, dem Brennraum (1) zugewandten Spitze sich zentral die Austrittsdüse (22) für den Kraftstoff befindet.10. Internal combustion engine according to claims 1-9, characterized in that the injection valves ( 20 ) for the fuel are an integral part of the inlet valves ( 6 ), and the valves in their outer shape represent approximately a streamlined body, the imaginary longitudinal axis of which is also the valve movement direction corresponds, and at the tip facing the combustion chamber ( 1 ) there is a central outlet nozzle ( 22 ) for the fuel. 11. Verbrennungskraftmaschine nach Anspruch 1-10, dadurch gekennzeichnet, daß die Anlage (22) zur katalytischen Nachverbrennung und Entrußung der Abgase mit im Raum (i B. 12′) angeordnet ist.11. Internal combustion engine according to claims 1-10, characterized in that the system ( 22 ) for catalytic afterburning and emission control of the exhaust gases is arranged in the room (i B. 12 ' ). 12. Verbrennungskraftmaschine nach Anspruch 1-11, dadurch gekennzeichnet, daß die Pleuelstange (7) und die Stan­ ge (10) innen hohl sind und mindestens eine der Ver­ bindungsleitungen (16, 17) durch sie hindurch geführt ist.12. Internal combustion engine according to claim 1-11, characterized in that the connecting rod ( 7 ) and the Stan ge ( 10 ) are hollow inside and at least one of the Ver connecting lines ( 16, 17 ) is passed through them. 13. Verbrennungskraftmaschine nach Anspruch 1-12, dadurch gekennzeichnet, daß die Verbindungsleitungen (16, 17) koaxial durch die Pleuelstange (7) und die Stange (10) geführt sind.13. Internal combustion engine according to claim 1-12, characterized in that the connecting lines ( 16, 17 ) are guided coaxially through the connecting rod ( 7 ) and the rod ( 10 ).
DE19873715750 1987-05-12 1987-05-12 Internal-Combustion Engine Withdrawn DE3715750A1 (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3826600A1 (en) * 1988-08-05 1990-02-08 Joern Martens Exhaust turbocharger with exhaust emission control device
DE4007466A1 (en) * 1990-03-09 1991-02-14 Franz Josef Knott Reduced emissions two=stroke IC engine - has separately lubricated piston which operates without oil being mixed with fuel
US5694891A (en) * 1993-11-04 1997-12-09 Liebich; Max Internal combustion engine
IT201800005066A1 (en) * 2018-05-04 2019-11-04 Two-stroke engine with integral pistons

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GB248737A (en) * 1925-03-05 1926-05-06 Sulzer Ag Improvements in or relating to apparatus for supplying air to two-stroke cycle internal combustion engines
DE488477C (en) * 1929-12-28 Johann Wolf Double-acting two-stroke internal combustion engine with compressor
JPS59226231A (en) * 1983-06-07 1984-12-19 「湧」井　貞美 Small and light internal-combustion engine in which plurality of combustion chambers are disposed in series and connected dynamically with each other
US5167208A (en) * 1992-03-09 1992-12-01 Rasiah Randolph R Internal combustion engine

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE294946C (en) *
DE268147C (en) *
DE488477C (en) * 1929-12-28 Johann Wolf Double-acting two-stroke internal combustion engine with compressor
US1170966A (en) * 1909-06-18 1916-02-08 George W Donning Engine.
GB248737A (en) * 1925-03-05 1926-05-06 Sulzer Ag Improvements in or relating to apparatus for supplying air to two-stroke cycle internal combustion engines
JPS59226231A (en) * 1983-06-07 1984-12-19 「湧」井　貞美 Small and light internal-combustion engine in which plurality of combustion chambers are disposed in series and connected dynamically with each other
US5167208A (en) * 1992-03-09 1992-12-01 Rasiah Randolph R Internal combustion engine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3826600A1 (en) * 1988-08-05 1990-02-08 Joern Martens Exhaust turbocharger with exhaust emission control device
DE3826600C2 (en) * 1988-08-05 1998-03-19 Joern Martens Exhaust gas turbocharger with exhaust gas cleaning device
DE4007466A1 (en) * 1990-03-09 1991-02-14 Franz Josef Knott Reduced emissions two=stroke IC engine - has separately lubricated piston which operates without oil being mixed with fuel
US5694891A (en) * 1993-11-04 1997-12-09 Liebich; Max Internal combustion engine
IT201800005066A1 (en) * 2018-05-04 2019-11-04 Two-stroke engine with integral pistons
WO2019211371A1 (en) * 2018-05-04 2019-11-07 Saleri Remo Felice Engine with cooperating pistons based on a two-stroke cycle

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