EP0745181B1 - Two-stroke engine - Google Patents

Two-stroke engine Download PDF

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Publication number
EP0745181B1
EP0745181B1 EP95909715A EP95909715A EP0745181B1 EP 0745181 B1 EP0745181 B1 EP 0745181B1 EP 95909715 A EP95909715 A EP 95909715A EP 95909715 A EP95909715 A EP 95909715A EP 0745181 B1 EP0745181 B1 EP 0745181B1
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EP
European Patent Office
Prior art keywords
piston
heat
piston rod
stroke engine
engine according
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Expired - Lifetime
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EP95909715A
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German (de)
French (fr)
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EP0745181A1 (en
Inventor
Lutz Hamann
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Ficht GmbH and Co KG
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Ficht GmbH and Co KG
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Publication of EP0745181A1 publication Critical patent/EP0745181A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F3/00—Pistons 
    • F02F3/16—Pistons  having cooling means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/22—Liquid cooling characterised by evaporation and condensation of coolant in closed cycles; characterised by the coolant reaching higher temperatures than normal atmospheric boiling-point
    • F01P2003/2278—Heat pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/08—Cooling of piston exterior only, e.g. by jets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P3/00—Liquid cooling
    • F01P3/06—Arrangements for cooling pistons
    • F01P3/10—Cooling by flow of coolant through pistons
    • 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
    • F02B2075/025—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle two

Definitions

  • Such an engine known for example from DE-OS 34 33 510, has at least two piston cylinder units lying opposite one another on an axis, the rigidly attached piston rods of which are coupled via a crank loop drive arranged between the piston cylinder units.
  • the inventive design of the piston rod as a heat dissipation tube creates a two-stroke engine, the piston of which is surprisingly well cooled despite the high power density of two-stroke engines and the exhaust gases flowing out during the working cycle and heating the piston edge of the piston crown. It is surprising that this principle of heat dissipation enables such rapid and effective heat dissipation, even with two-stroke engines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Means For Warming Up And Starting Carburetors (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a heat exchanger tube device, in which there is a combination of a heat exchanger tube and a shaker which causes the tube to reciprocate essentially along its longitudinal axis. A special embodiment of the heat exchanger tube device is used to cool reciprocating engine parts, e.g. pistons of internal combustion engines, especially two-stroke engines, in which use is made of an engine-specific device to remove heat from the engine part (4) to be cooled to a heat sink in the form of a hermetically sealed heat exchanger tube (6), one end of which is in heat transfer contact with the engine part (4) to be cooled, and which extends along the longitudinal axis in the direction of reciprocation of said engine part (4) as far as the heat sink and is filled with a given quantity of a known working liquid (16) for a heat exchanger tube which is evaporated by the heat to be dissipated.

Description

Die Erfindung betrifft einen Zweitaktmotor.The invention relates to a two-stroke engine.

Schwingungen ausführende Motorteile bedürfen regelmäßig der Kühlung. Beispielsweise müssen Kolben von Verbrennungsmotoren aufgrund des mit dem Brennverlauf verbundenen Wärmestroms aus dem Verbrennungsraum in die Kolben gekühlt werden, damit ihre Formstabilität erhalten bleibt. Bei Otto-Motoren werden die Kolben beispielsweise durch Anspritzen ihrer Unterseiten mit Motoröl aus dem Kurbelkasten gekühlt. Das dabei erwärmte Motoröl wird über Ölkühler rückgekühlt.Engine parts that carry out vibrations regularly require cooling. For example, pistons of internal combustion engines have to be cooled from the combustion chamber into the pistons due to the heat flow associated with the combustion process, so that their dimensional stability is maintained. In Otto engines, the pistons are cooled, for example, by spraying their undersides with engine oil from the crankcase. The heated engine oil is recooled using an oil cooler.

Die Anforderung an die Kühlung von Motorkolben wächst mit zunehmender Leistungsdichte des Motors. Besonders hohe Anforderungen werden an Zweitaktmotoren mit Kolbenkantensteuerung gestellt, was zum einen dadurch bedingt ist, daß Zweitaktmotoren im Vergleich zu Otto-Motoren eine doppelt so hohe Leistungsdichte aufweisen (beim Zweitaktmotor erfolgt ein Verbrennungsprozeß nach jeweils einem Kurbelwinkel von 360°, während beim Otto-Motor ein Verbrennungsprozeß nach jeweils einem Kurbelwinkel von 720° erfolgt) und zum anderen dadurch, daß das heiße Abgas die Kolbenkante des Kolbenbodens beim Arbeitstakt "Ausströmen" partiell stark erhitzt. Im Gegensatz zu Otto-Motoren ist bei kurbelkastengespülten Zweitaktmotoren eine Ölkühlung nicht möglich, da das beim Zweitaktmotor stark vernebelte Öl mit dem Gas in den Verbrennungsraum gerissen werden würde. Einen geringen, jedoch in der Praxis nicht ausreichenden Beitrag zur Kühlung kann der den Kolben kühlende Wärmestrom der Verdampfungswärme des Brennstoffs liefern, wenn er mit der Kolbenunterseite in Berührung gelangt. Dieser Beitrag zur Kolbenkühlung entfällt jedoch bei modernen Zweitaktmotoren, bei denen der Kraftstoff über Einspritzsysteme zugeführt wird. Für die Kolbenkühlung bei Zweitaktmotoren kommt ferner ein in Überschuß für die Kolbenschmierung zugeführtes Öl deshalb nicht in Betracht, weil der Kurbelraum vom Vorkompressionsraum abgeschottet ist.The requirement for cooling engine pistons increases with increasing engine power density. Particularly high demands are placed on two-stroke engines with piston edge control, which is partly due to the fact that two-stroke engines have twice the power density compared to Otto engines (with the two-stroke engine, a combustion process takes place after every crank angle of 360 °, while with the Otto engine a combustion process takes place after a crank angle of 720 °) and the other in that the hot exhaust gas Piston edge of the piston crown is partially strongly heated during the "outflow" cycle. In contrast to petrol engines, oil cooling is not possible with crankcase-flushed two-stroke engines, since the heavily atomized oil in the two-stroke engine would be torn into the combustion chamber with the gas. The heat flow of the heat of vaporization of the fuel, which cools the piston, can make a small but inadequate contribution to cooling when it comes into contact with the underside of the piston. However, this contribution to piston cooling does not apply to modern two-stroke engines in which the fuel is supplied via injection systems. For piston cooling in two-stroke engines, an oil supplied in excess for piston lubrication is also out of the question because the crankcase is sealed off from the pre-compression space.

Besonders problematisch ist die Kühlung der Kolben von Kurbelschlaufenmotoren. Ein derartiger, beispielsweise aus der DE-OS 34 33 510 bekannter Motor weist mindestens zwei auf einer Achse sich gegenüberliegende Kolbenzylindereinheiten auf, deren starr befestigte Kolbenstangen über einen zwischen den Kolbenzylindereinheiten angeordneten Kurbelschleifentrieb gekoppelt sind. Der Kurbelschleifentrieb, mit dem die hin- und hergehende Bewegung der Kolbenstangen in eine Rotationsbewegung umgewandelt wird, besteht in der Regel aus einem Kurbelschleifenrahmen, an dessen Stegen außenseitig die Kolbenstangen ebenfalls starr befestigt sind und in dessen Innenraum ein Gleitstein sitzt, der durch innenseitig an den Stegen angeordnete Gleitbahnen geführt wird und in dem drehbar ein Kurbelzapfen eines die Rotationsbewegung ausführenden Kurbeltriebes steckt, wobei sich die Achse des Kurbelzapfens quer zur Achse der Kolbenstangen erstreckt.Cooling the pistons of crank loop motors is particularly problematic. Such an engine, known for example from DE-OS 34 33 510, has at least two piston cylinder units lying opposite one another on an axis, the rigidly attached piston rods of which are coupled via a crank loop drive arranged between the piston cylinder units. The crank loop drive, with which the reciprocating movement of the piston rods is converted into a rotational movement, generally consists of a crank loop frame, on the webs of which the piston rods are also rigidly attached on the outside and in the interior of which a sliding block is seated, which is connected to the inside by the Web-arranged slideways is guided and in which a crank pin of a crank drive executing the rotational movement is rotatably inserted, the axis of the crank pin extending transversely to the axis of the piston rods.

Es ist intern versucht worden, die Kühlung der Kolben eines Kurbelschlaufenmotors über die Kolbenstangen -zu bewirken. Im Versuch scheitern diese Maßnahmen zur Kühlung der Kolben über die Kolbenstange durch Öl aus dem Kurbelraum an der Zuführung des Öls in die hohl ausgebildete Kolbenstange. Grundsätzlich kann Öl in die Kolbenstange ausschließlich an zwei Punkten eingeführt werden, nämlich einerseits am Umfang der Kolbenstange über das Trennwandlager im Bereich des oberen Totpunkts (OT) und zum anderen stirnseitig über die Gleitbahn zum Kulissenstein. Im zuerst genannten Fall wird die Kolbenstange an genau dem Punkt durch Ölzufuhröffnungen geschwächt, an dem sie im Betrieb die höchste Belastung erfährt. Im zweiten Fall steht durch das schnelle Überfahren des Gleitsteins nicht ausreichend Zeit zur Verfügung, die erforderliche Ölstrommenge in die Stange einzuleiten.Attempts have been made internally to cool the pistons of a crank loop motor via the piston rods. In the experiment, these measures for cooling the pistons via the piston rod fail due to oil from the crank chamber due to the supply of the oil into the hollow piston rod. Basically, oil can only be introduced into the piston rod at two points on the one hand on the circumference of the piston rod via the partition wall bearing in the area of top dead center (OT) and on the other hand on the end face via the slideway to the sliding block. In the former case, the piston rod is weakened by oil supply openings at exactly the point where it experiences the highest load during operation. In the second case, the quick overrun of the sliding block does not provide enough time to introduce the required amount of oil flow into the rod.

Als weiterer Nachteil dieser Art der Kolbenkühlung wurde erkannt, daß die sich translatorisch bewegende Masse der Kurbelschlaufe um den Masseanteil für die Ölleitungsführung und die Ölfüllung erhöht wird, wodurch zum Schwingungsausgleich zusätzliche oder größere Ausgleichsmassen vorgesehen werden müssen.As a further disadvantage of this type of piston cooling, it was recognized that the translationally moving mass of the crank loop is increased by the mass fraction for the oil line routing and the oil filling, as a result of which additional or larger compensating masses must be provided to compensate for vibrations.

Zum Stand der Technik gehören stationär angeordnete Wärmerohre, mit denen Wärmeenergie bei nahezu konstanter Temperatur von einer Wärmequelle zu einer Wärmesenke durch Verdampfung und Kondensation einer Arbeitsflüssigkeit in dem Wärmerohr bei gleicher Temperatur in einem geschlossenen Raum konstanten Drucks übertragen wird. Das Wärmerohr kann als sogenanntes Kapillar-Wärmerohr ausgebildet sein, dessen Innenseite durchgehend mit einer porösen Auskleidung versehen ist, deren Hohlräume allseitig miteinander verbunden sind, so daß Kapillarkräfte die Arbeitsflüssigkeit in jede Richtung transportieren können, sobald Ungleichgewichte in der Benetzung der Kapillaren auftreten. Der Wärmetransport erfolgt dabei ausschließlich durch Kapillarkräfte, unabhängig von der Ausrichtung des Wärmerohrs. Die Ausbildung der Kolbenstange eines vorstehend beschriebenen Zweitaktmotors als Kapillar-Wärmerohr ist unwirksam, weil die Wärmeableitung durch Kapillarkräfte viel zu langsam ist. Darüber hinaus gibt es Wärmerohre, bei denen der Transport der Arbeitsflüssigkeit ausschließlich durch Schwerkraft erfolgt. Auch ein derartiges Wärmerohr kann nicht die Kühlprobleme von Zweitaktmotoren lösen, weil die Kurbelstangen nicht schwerkraftgerecht angeordnet werden können.The prior art includes stationary heat pipes, with which heat energy is transferred from a heat source to a heat sink at an almost constant temperature by evaporation and condensation of a working fluid in the heat pipe at the same temperature in a closed space of constant pressure. The heat pipe can be designed as a so-called capillary heat pipe, the inside of which is continuously provided with a porous lining, the cavities of which are connected on all sides, so that capillary forces can transport the working fluid in any direction as soon as imbalances occur in the wetting of the capillaries. The heat is transported exclusively by capillary forces, regardless of the orientation of the heat pipe. The design of the piston rod of a two-stroke engine described above as a capillary heat pipe is ineffective because the heat dissipation by capillary forces is much too slow. There are also heat pipes in which the working fluid is transported solely by gravity. Even such a heat pipe cannot solve the cooling problems of two-stroke engines because the crank rods cannot be arranged in a way that suits gravity.

Aus der EP 0 131 382 A3 ist ein Kolben für eine Brennkraftmaschine bekannt, der ein U-förmig gebogenes auf den Kopf stehendes Wärmerohr aufweist, so daß die Basis des U-förmigen Wärmerohrs angrenzend an der den Brennraum begrenzenden Oberfläche angeordnet ist und die Schenkel des U-förmigen Wärmerohrs nahe an der Mantelfläche des Kolbens angeordnet sind, so daß ein stetiger Wärmeausgleich zwischen der den Brennraum begrenzenden Kolbenoberfläche und der Mantelfläche erfolgt. Hierdurch wird der gesamte Kolben in einem isothermischen Zustand gehalten, so daß keine Verformungen auf Grund von Wärmedifferenzen auftreten. Dieser verformungsfreie Kolben soll eine sichere Ölschmierung im Zylinder gewährleisten.From EP 0 131 382 A3 a piston for an internal combustion engine is known which has a U-shaped upside down heat pipe, so that the base of the U-shaped heat pipe is arranged adjacent to the surface delimiting the combustion chamber and the legs of the U-shaped heat pipes are arranged close to the outer surface of the piston, so that there is a constant heat balance between the piston surface delimiting the combustion chamber and the outer surface. As a result, the entire piston is kept in an isothermal state, so that no deformations occur due to heat differences. This deformation-free piston is intended to ensure safe oil lubrication in the cylinder.

In der EP 0 074 156 A2 ist ein Kolben für eine Brennkraftmaschine mit Flüssigkühlung beschrieben, wobei der Kolben einen abgeschlossenen Hohlraum aufweist, der mit einer Kühlflüssigkeit gefüllt ist, die vorzugsweise einen Siedepunkt von 200°C oder geringer bei atmosphärischem Druck hat. Im Kolben ist ein Wärmetauscher ausgebildet, der zur einen Seite an den Hohlraum angrenzt und zur anderen Seite mit kühlem Öl aus dem Motorraum beschickt wird, wobei das Öl über die Kolbenstange zugeführt wird. Solche Kolben mit Wärmetauscher können in großvolumigen Dieselmotoren verwendet werden, die entsprechend groß bemessene-Kolben aufweisen.EP 0 074 156 A2 describes a piston for an internal combustion engine with liquid cooling, the piston having a closed cavity which is filled with a cooling liquid which preferably has a boiling point of 200 ° C. or less at atmospheric pressure. A heat exchanger is formed in the piston, which adjoins the cavity on one side and is supplied with cool oil from the engine compartment on the other side, the oil being supplied via the piston rod. Such pistons with heat exchangers can be used in large-volume diesel engines which have correspondingly large pistons.

Aus der EP 0 619 419 A1 geht ein Stößel für ein Stößelventil hervor, das ultraleicht aus einem extrem dünnen Metallblech hohl ausgebildet ist. Dieser Stößel hat die Form eines langen dünnen Rohres, das einendig etwa pilzförmig zu einem Ventilsitz verbreitert ist. Im Stößel ist eine vorbestimmte Menge eines Kühlmittels, beispielsweise Natrium-Kalium gefüllt, wodurch der Stößel gekühlt werden soll.EP 0 619 419 A1 discloses a tappet for a tappet valve which is ultralightly hollow from an extremely thin metal sheet. This plunger is in the form of a long, thin tube, which is widened at approximately one end to form a valve seat. A predetermined amount of a coolant, for example sodium potassium, is filled in the plunger, as a result of which the plunger is to be cooled.

Der Erfindung liegt die Aufgabe zugrunde, einen Zweitaktmotor, insbesondere einen Kurbelschleifenmotor, zu schaffen, dessen Kolben ohne großen Aufwand effektiv gekühlt werden können.The invention has for its object to provide a two-stroke engine, in particular a cranked loop engine, the pistons can be cooled effectively with little effort.

Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst.This object is solved by the features of claim 1.

Durch die erfindungsgemäße Ausbildung der Kolbenstange als Wärmeabfuhrrohr wird ein Zweitaktmotor geschaffen, dessen Kolben trotz der hohen Leistungsdichte von Zweitaktmotoren und der beim Arbeitstakt ausströmenden, die Kolbenkante des Kolbenbodens erhitzenden Abgase überraschend gut gekühlt wird. Es ist überraschend, daß dieses Prinzip der Wärmeableitung eine derart schnelle und effektive Wärmeabfuhr, selbst bei Zweitaktmotoren, ermöglicht.The inventive design of the piston rod as a heat dissipation tube creates a two-stroke engine, the piston of which is surprisingly well cooled despite the high power density of two-stroke engines and the exhaust gases flowing out during the working cycle and heating the piston edge of the piston crown. It is surprising that this principle of heat dissipation enables such rapid and effective heat dissipation, even with two-stroke engines.

Vorteilhafte Weiterbildungen der Erfindung sind in den Unteransprüchen gekennzeichnet.Advantageous developments of the invention are characterized in the subclaims.

Nachfolgend wird die Erfindung anhand der Zeichnung beispielhaft näher erläutert; es zeigen:

Fig. 1
eine teilweise aufgeschnittene Stirnansicht eines Kurbelschlaufenmotors mit erfindungsgemäßer Kühleinrichtung in einer Kolbenstange;
Fig. 2
in einer Einzelheit eine erweiterte Ausbildung der erfindungsgemäßen Kühleinrichtung in einer Kolbenstange.
The invention is explained in more detail below using the drawing as an example; show it:
Fig. 1
a partially cut end view of a crank loop motor with a cooling device according to the invention in a piston rod;
Fig. 2
in a detail, an expanded design of the cooling device according to the invention in a piston rod.

Der Zweitaktmotor gemäß Fig. 1 hat zwei achsgleich gegenüberliegende Arbeitszylinder 1 und 2, die mit gegenüberliegenden Seiten eines Kurbelgehäuses 3 fest verbunden sind. In den Arbeitszylindern 1 und 2 laufen Arbeitskolben 4 und -5, an denen Kolbenstangen 6 und 7 starr befestigt sind. Die Kolbenstangen 6 und 7 sind mit einem Kurbelschlaufenrahmen 8 fest verbunden, der eine geradlinige Kulisse 9 einschließt, deren Längsachse 10 in einem Winkel von 90° quer zur Längsachse 11 der beiden Arbeitszylinder 1 und 2 gerichtet ist. In der Kulisse 9 bewegt sich ein Gleitstein 12, der auf einem Kurbelzapfen 13 eines Kurbelabtriebs drehbar gelagert ist.1 has two axially opposite working cylinders 1 and 2, which are fixedly connected to opposite sides of a crankcase 3. In the working cylinders 1 and 2, working pistons 4 and -5 run, on which piston rods 6 and 7 are rigidly attached. The piston rods 6 and 7 are firmly connected to a crank loop frame 8, which includes a rectilinear link 9, the longitudinal axis 10 of which is directed at an angle of 90 ° transversely to the longitudinal axis 11 of the two working cylinders 1 and 2. A sliding block 12, which is rotatably mounted on a crank pin 13 of a crank output, moves in the backdrop 9.

Nimmt man die Drehrichtung R des Motors im Uhrzeigersinn an, so bewegen sich die beiden Arbeitskolben 4 und 5 gleichzeitig gleichgerichtet. Diese Bewegung wird über die Kurbelschleife 8 auf den Kurbelzapfen 13 übertragen, der dadurch dem Kurbelabtrieb eine Drehbewegung aufzwingt.Assuming the direction of rotation R of the motor clockwise, the two working pistons 4 and 5 move simultaneously in the same direction. This movement is transmitted via the crank loop 8 to the crank pin 13, which thereby forces the crank output to perform a rotary movement.

Da die beiden Zylinderkolbenanordnungen 1, 4 sowie 2, 5 und die zugehörigen Kolbenstangen 6, 7 identisch aufgebaut sind, werden konstruktive Einzelheiten nachfolgend anhand der Kolbenzylinderanordnung 1, 4 näher beschrieben.Since the two cylinder piston arrangements 1, 4 and 2, 5 and the associated piston rods 6, 7 are constructed identically, structural details are described in more detail below with reference to the piston cylinder arrangement 1, 4.

Die Kolbenstange 6 ist in einem sogenannten Trennwandlager 15 geführt, das in der Wand des Kurbelgehäuses 3 eingesetzt ist, an die der Zylinder 1 angeschlossen ist.The piston rod 6 is guided in a so-called partition wall bearing 15, which is inserted in the wall of the crankcase 3, to which the cylinder 1 is connected.

Die Kolbenstange 6 ist hohl und erfindungsgemäß mit einer bestimmten Menge einer Arbeitsflüssigkeit 16 gefüllt und wird nach Art eines Wärmerohres verwendet. Es ist einendig z. B. einstückig mit der Kurbelschlaufe 8 ausgebildet und anderendig über eine Kolbenbefestigungsschraube 17 starr mit dem Kolben 4 verbunden. Durch den im Verbrennungsraum 18 des Zylinders 1 erfolgenden Verbrennungsprozeß fließt ein Wärmestrom 19 in den Kopf des Kolbens 4 und in den Kolbenbefestigungsbereich. Von dort fließt ein Teil des Wärmestroms in die Kolbenstange 6, deren Wandung kolbenkopfseitig dadurch stark erhitzt wird. Die Wärme wird an die im Innenraum der Kolbenstange 6 befindliche Arbeitsflüssigkeit 16 übertragen, die dadurch verdampft. Die vom Dampf aufgenommene Wärmemenge wird wegen des guten Wärmeübergangswertes von Dampf zur Metallwandung der hohlen Kolbenstange 6 sehr schnell an den kühleren, kurbelschlaufenseitigen Bereich der Kolbenstange 6 abgegeben, wo Dampf zumindest teilmengenweise zur Arbeitsflüssigkeit kondensiert. Die Arbeitsflüssigkeit verdampft somit während des Motorbetriebs am heißen, kolbenkopfseitigen Endbereich der Kolbenstange 6, und die im Arbeitsmitteldampf aufgenommene Wärmemenge wird an den kühleren kurbelschlaufenseitigen Endbereich der Kolbenstange 6 abgegeben. Dabei wird die Enthalpie des Dampfes um denjenigen Anteil vermindert, der durch die Abkühlung des Dampfs am kalten Ende der Kolbenstange 6 abgeleitet wird. Durch diese abgeleitete Wärmemenge wird eine bestimmte Wärmemenge festgelegt, die am heißen Ende der Kolbenstange 6 in diese einfließt. Der Dampftransport zum kühleren Endbereich der Kolbenstange 6 sowie der Flüssigkeitstransport zum wärmeren Endbereich der Kolbenstange wird neuartig durch die hin- und hergehende Bewegung der Kolbenstange 6 sehr schnell bewirkt. Aufgrund dieser Schüttelbewegung gelangt der kondensierte Anteil des Dampfes sehr schnell wieder zum heißen Ende der Kolbenstange 6, wo die Arbeitsflüssigkeit durch Wärmeaufnahme vom Kolbenkopf erneut verdampft wird und sehr schnell wieder in Kontakt mit dem kälteren Ende der Kolbenstange 6 kommt. Es ist überraschend, daß dieses Schüttelprinzip eine derart schnelle und effektive Wärmeabfuhr ermöglicht.The piston rod 6 is hollow and according to the invention filled with a certain amount of a working fluid 16 and is used in the manner of a heat pipe. It is zendig z. B. integrally formed with the crank loop 8 and at the other end rigidly connected to the piston 4 via a piston fastening screw 17. Due to the combustion process taking place in the combustion chamber 18 of the cylinder 1, a heat flow 19 flows into the head of the piston 4 and into the piston attachment area. From there, part of the heat flow flows into the piston rod 6, the wall of which on the piston head side is thereby greatly heated. The heat is transferred to the working fluid 16 located in the interior of the piston rod 6, which thereby evaporates. The amount of heat absorbed by the steam is very quickly due to the good heat transfer value of steam to the metal wall of the hollow piston rod 6 to the cooler area of the crank loop Delivered piston rod 6, where steam condenses at least in part to the working fluid. The working fluid thus evaporates during engine operation at the hot end region of the piston rod 6 on the piston head side, and the amount of heat absorbed in the working fluid vapor is released to the cooler end region of the piston rod 6 on the crank loop side. The enthalpy of the steam is reduced by the proportion which is derived by the cooling of the steam at the cold end of the piston rod 6. A certain amount of heat is determined by this derived amount of heat, which flows into the piston rod 6 at the hot end thereof. The steam transport to the cooler end region of the piston rod 6 and the liquid transport to the warmer end region of the piston rod is brought about very quickly by the reciprocating movement of the piston rod 6. As a result of this shaking movement, the condensed portion of the steam quickly returns to the hot end of the piston rod 6, where the working fluid is evaporated again by absorbing heat from the piston head and comes very quickly back into contact with the colder end of the piston rod 6. It is surprising that this shaking principle enables such rapid and effective heat dissipation.

Die Arbeitsflüssigkeit ist bevorzugt Wasser, Diphyl, Perchlorethylen, Trichlorethylen oder ein halogenierter Kohlenwasserstoff. Die Arbeitsflüssigkeit wird in die Kolbenstange 6 gefüllt und die Kolbenstange 6 wird daraufhin verschlossen. Bevorzugt ist der nicht von der Arbeitsflüssigkeit ausgefüllte Teil der hohlen Kolbenstange 6 evakuiert, um den Wirkungsgrad des Kühlsystems zu erhöhen.The working fluid is preferably water, diphyl, perchlorethylene, trichlorethylene or a halogenated hydrocarbon. The working fluid is filled into the piston rod 6 and the piston rod 6 is then closed. The part of the hollow piston rod 6 which is not filled with the working fluid is preferably evacuated in order to increase the efficiency of the cooling system.

Ein Teil des am heißen Ende in die Kolbenstange 6 einfließenden Wärmestroms wird nach der Erfindung vom schlaufenseitigen Endbereich teilweise auch an das für die Schmierung des Trennwandlagers 15 verwendete Öl abgegeben und mit diesem in den Ölsumpf 20 des Kurbelgehäuses 3 geleitet (siehe Pfeile 22). Ein weiterer Teil des von der Kolbenstange 6 abgehenden Wärmestroms wird von dem für die Schmierung des Kulissensteins 12 verwendeten Öl 21 aufgenommen und ebenfalls in den Ölsumpf 20 geleitet.A portion of the heat flow flowing into the piston rod 6 at the hot end is, according to the invention, also partially released from the loop-side end region to the oil used for the lubrication of the partition wall bearing 15 and conducted with it into the oil sump 20 of the crankcase 3 (see arrows 22). Another part of the heat flow coming from the piston rod 6 is used for the lubrication of the sliding block 12 Oil 21 added and also passed into the oil sump 20.

Das kalte Ende der Kolbenstange 6 kann zusätzlich durch einen Ölstrahl 23 gekühlt werden, der gegen den in den Kurbelraum 3 eintretenden Bereich der Kurbelstange 6 gerichtet wird und dessen Öl ebenfalls in den Ölsumpf 20 gelangt.The cold end of the piston rod 6 can additionally be cooled by an oil jet 23 which is directed against the area of the crank rod 6 entering the crank chamber 3 and the oil of which also reaches the oil sump 20.

Der mit Arbeitsflüssigkeit 16 gefüllte Hohlraum der Kolbenstange 6 kann zudem in Übertragungsverbindung mit einem ringförmigen Hohlraum 25 stehen, der im Kolbenkopf, an den Kolbenboden angrenzend ausgebildet ist (siehe Fig. 2). Durch diese Maßnahme kommt die Arbeitsflüssigkeit 16 in unmittelbaren Kontakt mit dem heißen Kolbenboden, so daß Wärme vom Kolbenboden unmittelbar in die Arbeitsflüssigkeit 16 eingeleitet wird. Dabei kann die Befestigungseinrichtung des Kolbens 4 mit der Schraube 17 so ausgebildet sein, daß das Gewindeloch für die Schraube 17 einen Zugang zum Hohlraumm der Kolbenstange 6 hat und als Befüllöffnung für die Arbeitsflüssigkeit verwendet werden kann.The cavity of the piston rod 6 filled with working fluid 16 can also be in communication with an annular cavity 25 which is formed in the piston head, adjacent to the piston crown (see FIG. 2). As a result of this measure, the working fluid 16 comes into direct contact with the hot piston crown, so that heat is introduced directly into the working fluid 16 from the piston crown. The fastening device of the piston 4 with the screw 17 can be designed such that the threaded hole for the screw 17 has access to the cavity of the piston rod 6 and can be used as a filling opening for the working fluid.

Claims (9)

  1. Two-stroke engine, in particular a crank slide drive frame engine, with a piston reciprocating back and forth in each cylinder, in which the piston rod (6) is designed as a heat dissipator tube which cools the piston (4), such that the heat dissipator tube moves in rapid reciprocation essentially along the direction of its longitudinal axis and is at one end in heat-transferring contact with the piston (4), and such that the piston rod (6) essentially forms a hermetically sealed hollow along its entire length, extends into the crankcase area serving as a heat sink, and is filled with a given quantity of a heat tube working liquid (16), which may be one known in itself, and which vaporizes under the action of the heat to be dissipated.
  2. Two-stroke engine according to Claim 1,
    characterized in that
    the heat tube comprises a porous lining in a way known in itself.
  3. Two-stroke engine according to Claims 1 and/or 2,
    characterized in that
    the vapour-pressure curve of the working liquid (16) is such that at a pressure of approximately 30 bar, the temperature is in the range between approximately 50° and 300°C.
  4. Two-stroke engine according to Claim 3,
    characterized in that
    the working liquid is water, diphenyl, perchloroethylene, trichloroethylene, or a halogenated hydrocarbon.
  5. Two-stroke engine according to one or more of Claims 3 and 4,
    characterized in that
    the portion of the heat dissipator tube not filled with the working liquid (16) is evacuated.
  6. Two-stroke engine according to one or more of Claims 1 to 5,
    characterized in that
    in the piston (4), adjacent to its bottom, there is a hollow space (25) which communicates with the hollow space of the piston rod (6).
  7. Two-stroke engine according to Claim 6,
    characterized in that
    the hollow space (25) in the piston (4) extends essentially over the entire area of the piston bottom.
  8. Two-stroke engine according to one or more of Claims 1 to 7, with a partition wall bearing arranged in the partition wall between the cylinder and the crankcase, through which the piston rod passes, such that the partition wall bearing (15) is lubricated with oil from the crankcase (3),
    characterized in that
    the cold end of the piston rod (6) is cooled by an oil jet (23) directed against the portion of the piston rod (5) that projects into the crankcase (3), the oil then running down into the oil sump (20).
  9. Two-stroke engine according to one or more of Claims 1 to 8, in which the piston head is bolted to the piston rod with a screw-bolt (17),
    characterized in that
    the threaded hole for the screw-bolt (17) in the piston rod opens into the hollow space of the piston rod (6).
EP95909715A 1994-02-17 1995-02-13 Two-stroke engine Expired - Lifetime EP0745181B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4405091 1994-02-17
DE4405091A DE4405091A1 (en) 1994-02-17 1994-02-17 Heat pipe device, in particular device for cooling vibrating engine parts
PCT/EP1995/000526 WO1995022686A1 (en) 1994-02-17 1995-02-13 Heat exchanger tube device, especially a device for cooling reciprocating engine parts

Publications (2)

Publication Number Publication Date
EP0745181A1 EP0745181A1 (en) 1996-12-04
EP0745181B1 true EP0745181B1 (en) 1997-09-03

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EP95909715A Expired - Lifetime EP0745181B1 (en) 1994-02-17 1995-02-13 Two-stroke engine

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EP (1) EP0745181B1 (en)
AT (1) ATE157740T1 (en)
DE (2) DE4405091A1 (en)
WO (1) WO1995022686A1 (en)

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DE102007000652B4 (en) 2007-11-07 2016-08-18 Technische Universität Dresden Piston cooling device for reciprocating engines with oscillating and translational movement of the piston and the piston rod
DE102008055939B3 (en) * 2008-11-05 2009-11-05 Rajat Gupta Internal-combustion engine i.e. reciprocating piston engine, for use in motor vehicle, has piston with elliptically formed opening, which is aligned right-angled to motion direction in cylinder, and output shaft clamping down opening
USD749715S1 (en) 2012-08-06 2016-02-16 Iff Gmbh Electric heating apparatus
DE102013100830A1 (en) 2013-01-28 2014-07-31 Bertwin R. Geist Immobilien + Erneuerbare Energien E.K. Method for producing heat pipe for piston rod of slider crank engine, involves placing medium together with receiving device, which contains or retains medium in solid or semi-solid state, and subsequently carrying out material-fit joining
WO2014076305A1 (en) * 2012-11-19 2014-05-22 Bertwin R. Geist Immobilien + Erneuerbare Energien E.K. Method for producing a hollow body which is pressure-tight to a predetermined medium
DE102012111136A1 (en) 2012-11-19 2014-05-22 Bertwin R. Geist Immobilien + Erneuerbare Energien E.K. Producing pressure-tight hollow body to predetermined medium, comprises joining two body parts, which when assembled, form hollow body containing medium in gaseous and/or liquid form, or by sealing single body which forms hollow body
DE102014201473A1 (en) 2014-01-28 2015-07-30 Neuman & Esser Gmbh & Co. Kg PISTON ROD FOR PISTON COMPRESSORS AND PISTON COMPRESSOR
US11761369B1 (en) * 2021-11-01 2023-09-19 United States Of America As Represented By The Secretary Of The Air Force Heat pipes integrated into a 3-D printed part

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EP0074156A2 (en) * 1981-09-05 1983-03-16 Mitsubishi Jukogyo Kabushiki Kaisha Piston in an internal combustion engine
EP0619419A1 (en) * 1993-04-01 1994-10-12 Eaton Corporation Ultra light engine valve

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004038945A1 (en) * 2004-08-11 2006-02-23 Mahle International Gmbh Light metal piston with heat pipes

Also Published As

Publication number Publication date
WO1995022686A1 (en) 1995-08-24
EP0745181A1 (en) 1996-12-04
DE4405091A1 (en) 1995-08-24
ATE157740T1 (en) 1997-09-15
DE59500610D1 (en) 1997-10-09

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