EP0292603B1 - Prime mover, particularly an internal combustion engine - Google Patents

Prime mover, particularly an internal combustion engine Download PDF

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Publication number
EP0292603B1
EP0292603B1 EP87111871A EP87111871A EP0292603B1 EP 0292603 B1 EP0292603 B1 EP 0292603B1 EP 87111871 A EP87111871 A EP 87111871A EP 87111871 A EP87111871 A EP 87111871A EP 0292603 B1 EP0292603 B1 EP 0292603B1
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EP
European Patent Office
Prior art keywords
rod portion
connecting rod
piston
production machine
rod
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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EP87111871A
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German (de)
French (fr)
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EP0292603A1 (en
Inventor
Gerhard Mederer
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Individual
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Individual
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Priority to AT87111871T priority Critical patent/ATE60881T1/en
Priority to JP63504861A priority patent/JP2693197B2/en
Priority to PCT/EP1988/000367 priority patent/WO1988008922A1/en
Publication of EP0292603A1 publication Critical patent/EP0292603A1/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
    • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
    • F02B41/02—Engines with prolonged expansion
    • F02B41/04—Engines with prolonged expansion in main cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
    • F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
    • 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
    • F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
    • F02B75/048—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of a variable crank stroke length
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2142—Pitmans and connecting rods
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2173—Cranks and wrist pins

Definitions

  • Engine or machine in particular internal combustion engine
  • the invention relates to an engine or working machine, in particular an internal combustion engine with at least one cylinder and a piston which is axially displaceable therein and which is connected to the crankshaft via an upper connecting rod section and a lower connecting rod section connected by a joint to the crankshaft, and in which both connecting rod sections are connected by one articulated common pivot lever are supported on an axis fixed to the motor housing.
  • an internal combustion engine (DE-PS 30 30 615) it is known to connect the piston and the crankshaft to one another by means of two articulated connecting rod sections.
  • this internal combustion engine uses a pivot lever that engages a common joint for the two connecting rod sections and is supported at its other end on a variably adjustable eccentric.
  • an improved torque curve is achieved by achieving an extended residence time of the piston in the top dead center.
  • this object is achieved in that the upper connecting rod section at the end facing away from the piston has an axial extension which extends beyond the common joint, and in that the pivoting lever articulates with the end facing the connecting rod section on the extension.
  • the support axis for the swivel lever in the engine block is expediently designed to be eccentrically adjustable, the support axis being adjustable radially to the longitudinal central axis of the cylinder and axially transverse to the longitudinal central axis of the cylinder.
  • connecting rod sections and swivel levers allow the most effective torque to be shifted to the most effective crankshaft positions, which leads to low fuel consumption, shorter ignition delay and, accordingly, smooth combustion with quiet operation of the internal combustion engine. In addition, there is also a reduction in the piston side pressure and thus a reduced warming up of the engine and a reduced wear. It goes without saying that the inventive design of connecting rod sections and swivel levers equally in gasoline and diesel engines or in any power machines that are operated with a piston, e.g. Compressors or pumps, can be used.
  • An advantageous embodiment of the internal combustion engine can be achieved if the length of the lower connecting rod section is approximately 1.3 times the length of the upper connecting rod section, the total length of both connecting rods Sections about 3% larger than the distance between the connecting rod bearing of the upper connecting rod portion and the circle described by the connecting rod bearing of the lower connecting rod portion in the top dead center of the piston and that the length of the pivot lever is carried out approximately 1.2 times the length of the upper connecting rod portion is, the radial distance of the pivot point of the pivot lever from the cylinder axis is approximately 1.0 times the length of the upper connecting rod section and the base point of the projection of the pivot point on the cylinder axis from the crankshaft axis is a distance that is approximately 1/3 of the distance from the piston rod bearing of the upper connecting rod section from the crankshaft axis at the top dead center of the piston.
  • the upper connecting rod section is fork-shaped and carries a bearing washer fixedly against rotation, to which the lower connecting rod section is articulated and the pivoting lever is eccentrically articulated with the ends facing away from the crankshaft or the support axis.
  • the fork ends of the upper connecting rod section preferably have steps which are protruded by the bearing plate, the peripheral surface of the bearing plate supporting the lower connecting rod section and the part of the bearing plate extending in the area of the steps being articulated to the pivot lever.
  • the required axial extension at the upper connecting rod section and, moreover, a narrow construction for the connecting rod formed by the connecting rod sections is achieved, as a result of which the connecting rod sections and the pivoting lever can also be accommodated in a space-saving manner in multi-cylinder machines.
  • the support axis is advantageously formed in the motor housing. It is also possible to arrange the support axis outside the engine block. In the latter embodiment, the pivot lever for connection to the support axis extends through a recess in the motor housing wall.
  • 1 is a cylinder, e.g. referred to an internal combustion engine that slidably receives a piston 2.
  • the cylinder 1 is closed at the upper end by a plate-shaped cylinder head 3.
  • the devices for the supply of fuel and air or fuel mixture and the removal of combustion gases are not shown for reasons of clarity.
  • the piston 2 receives a piston pin 4, on which an upper connecting rod section 5 engages with its upper bearing 6 such that it can pivot.
  • the connecting rod section 5 is preferably fork-shaped and the legs 7 of the connecting rod section 5 hold in the area of the free ends by means of bolts 8 a bearing disc 9 (FIG. 2, 3) to which the upper end of a lower connecting rod section 10 is articulated, the lower end of which Bearing 18 engages a crankshaft 11.
  • the legs 7 have shoulders 12 which are surmounted by the bearing disk 9.
  • a pivot lever 14 with one end 14 ′′ acts in an articulated manner by means of a bolt 13, which is pivotally supported with its other end 14 ′ in a bearing 16 arranged eccentrically on a support axis 15.
  • the articulation point for the pivot lever 14 on the upper connecting rod section 5 is extended by the extension 27 beyond the common articulation point of both connecting rod sections 5 and 10.
  • the piston 2 is at top dead center.
  • the connecting rod bearing 6 on the piston side moves along the cylinder axis 22 and the bearing disc 9 moves on a movement path Form of a circular arc 17.
  • the bolt 13 moves on a further circular path 21.
  • the crankshaft 11 and with it the crankshaft-side bearing 18 rotate in the direction of the arrow 19.
  • the changes in position of the connecting rod sections 5, 10 and the pivot lever 14 at the bottom dead center of the piston 2 correspond to the dashed lines.
  • the corresponding position of the crankshaft bearing 18 is designated by the letters UT.
  • the 360 of a crankshaft revolution is plotted on the abscissa and the torque value determined for constant piston pressure force is plotted on the ordinate.
  • the dashed line 24 shows the torque curve in a conventional comparison motor. It can be seen that the maximum torque can be achieved with line 23 at approximately 45 crankshaft revolutions. 3, which shows the piston travel over the crankshaft revolution, the solid line 25 leaving the internal combustion engine according to the invention and the dashed line 26 for a conventional comparison engine (line 26) leaving its top dead center earlier and later Reached again, that is to say it remains much shorter in the region of its top dead center position than the piston 2 of the embodiment according to the invention (line 25).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Transmission Devices (AREA)
  • Harvester Elements (AREA)

Abstract

In a prime mover, particularly an internal combustion engine with a minimum of one cylinder and a piston axially displaceable in the latter, which piston is connected to the crankshaft via an upper connecting rod section and a lower connecting rod section connected to the latter by an articulated joint and in which both connecting rod sections are supported by a pivoted common rocking lever on an adjustable shaft fixed to the engine housing, in order to promote increases in performance and for adaptation to different types of fuel,the upper connecting rod section (5) has, at the end remote from the piston (2), an axial extension (27) extended beyond the common articulated joint (9) of the two connecting rod sections (5, 10) and the rocking lever (14) engages in an articulated manner on the extension (27) by the end (14'') facing the connecting rod sections (5, 10). <IMAGE>

Description

Kraft- oder Arbeitsmaschine, insbesondere VerbrennungskraftmaschineEngine or machine, in particular internal combustion engine

Die Erfindung betrifft eine Kraft- oder Arbeitsmaschine, insbesondere Verbrennungskraftmaschine mit mindestens einem Zylinder und einem in diesem axial verschieblichen Kolben, der über einen oberen Pleuelabschnitt und einem durch ein Gelenk mit diesem verbundenen unteren Pleuelabschnitt mit der Kurbelwelle verbunden ist und bei der beide Pleuelabschnitte durch einen angelenkten gemeinsamen Schwenkhebel an einer motorgehäusefest einstellbaren Achse abgestützt sind.The invention relates to an engine or working machine, in particular an internal combustion engine with at least one cylinder and a piston which is axially displaceable therein and which is connected to the crankshaft via an upper connecting rod section and a lower connecting rod section connected by a joint to the crankshaft, and in which both connecting rod sections are connected by one articulated common pivot lever are supported on an axis fixed to the motor housing.

Bei einer Verbrennungskraftmaschine (DE-PS 30 30 615) ist es bekannt, den Kolben und die Kurbelwelle durch zwei gelenkig verbundene Pleuelabschnitte miteinander zu verbinden. Außerdem findet bei dieser Verbrennungskraftmaschine ein an einem gemeinsamen Gelenk für die beiden Pleuelabschnitte angreifender Schwenkhebel Anwendung, der mit seinem anderen Ende an einem veränderlich einstellbaren Exzenter abgestützt ist. Bei dieser Verbrennungskraftmaschine ist durch Erreichung einer verlängerten Verweilzeit des Kolbens im oberen Totpunkt ein verbesserter Drehmomentverlauf erzielt.In an internal combustion engine (DE-PS 30 30 615) it is known to connect the piston and the crankshaft to one another by means of two articulated connecting rod sections. In addition, this internal combustion engine uses a pivot lever that engages a common joint for the two connecting rod sections and is supported at its other end on a variably adjustable eccentric. In this internal combustion engine, an improved torque curve is achieved by achieving an extended residence time of the piston in the top dead center.

Es ist Aufgabe der Erfindung, Maßnahmen zu Lei stungssteigerungen und zur Anpassung an unterschiedliche Kraftstoffe bei Verbrennungskraftmaschinen der vorgenannten Art zu schaffen.It is an object of the invention to provide measures to increase performance and to adapt to different fuels in internal combustion engines of the aforementioned type.

Erfindungsgemäß ist diese Aufgabe dadurch gelöst, daß der obere Pleuelabschnitt an dem den Kolben abgewandten Ende eine über das gemeinsame Gelenk hinausgeführte axiale Verlängerung aufweist und daß der Schwenkhebel mit dem den Pleuelabschnitt zugewandten Ende an der Verlängerung gelenkig angreift. Zweckmäßig ist die Stützachse für den Schwenkhebel im Motorblock exzentrisch einstellbar ausgebildet wobei die Stützachse zur Längsmittelachse des Zylinders radial und quer zur Längsmittelachse des Zylinders axial einstellbar ist. Auf diese Weise liegen das gemeinsame Gelenk beider Pleuelabschnitte und das Gelenk von oberem Pleuelabschnitt und Schwenkhebel auf zwei getrennten Bewegungsbahnen, was zu einer verringerten Kolbenbeschleunigung bei gleichem Kolbenweg und durch die Ausbildung größerer Hebelarme zu einer Erhöhung des Drehmoments führt. Die gewählte Kinematik von Pleuelabschnitten und Schwenkhebel erlaubt die Verlagerung des jeweils wirksamsten Drehmoments auf die wirksamsten Kurbelwellenstellungen, was zu einem geringem Kraftstoffverbrauch, zu einem kürzerem Zündverzug und demgemäß zu einer weichen Verbrennung mit einem ruhigen Betrieb der Verbrennungskraftmaschine führt. Darüberhinaus stellt sich auch eine Verringerung des Kolbenseitendrucks und damit eine verringerte Erwärmung des Motors und ein verminderter Verschleiß ein. Es versteht sich, daß die erfindungsmäßige Ausbildung von Pleuelabschnitten und Schwenkhebel gleichermaßen bei Otto- und Dieselmotoren bzw. bei beliebigen Arbeitskraftmaschinen, die mit einem Kolben betrieben werden, z.B. Kompressoren oder Pumpen, Anwendung finden kann.According to the invention, this object is achieved in that the upper connecting rod section at the end facing away from the piston has an axial extension which extends beyond the common joint, and in that the pivoting lever articulates with the end facing the connecting rod section on the extension. The support axis for the swivel lever in the engine block is expediently designed to be eccentrically adjustable, the support axis being adjustable radially to the longitudinal central axis of the cylinder and axially transverse to the longitudinal central axis of the cylinder. In this way, the joint of the two connecting rod sections and the joint of the upper connecting rod section and the pivot lever lie on two separate movement paths, which leads to reduced piston acceleration with the same piston travel and, due to the formation of larger lever arms, an increase in the torque. The selected kinematics of connecting rod sections and swivel levers allow the most effective torque to be shifted to the most effective crankshaft positions, which leads to low fuel consumption, shorter ignition delay and, accordingly, smooth combustion with quiet operation of the internal combustion engine. In addition, there is also a reduction in the piston side pressure and thus a reduced warming up of the engine and a reduced wear. It goes without saying that the inventive design of connecting rod sections and swivel levers equally in gasoline and diesel engines or in any power machines that are operated with a piston, e.g. Compressors or pumps, can be used.

Eine vorteilhafte Ausgestaltung der Verbrennungskraftmaschine ist dann erzielbar, wenn die Länge des unteren Pleuelabschnitts etwa das 1,3fache der Länge des oberen Pleuelabschnitts beträgt, die Gesamtlänge beider Pleuel abschnitte etwa 3 % größer als der Abstand zwischen dem kolbenseitigen Pleuellager des oberen Pleuelabschnitts und dem von dem kurbelwellenseitigen Pleuellager des unteren Pleuelabschnitts beschriebenen Kreis im oberen Totpunkt des Kolbens ist und daß weiter die Länge des Schwenkhebels etwa mit der 1,2fachen Länge des oberen Pleuelabschnitts ausgeführt ist, der radiale Abstand der Anlenkstelle des Schwenkhebels von der Zylinderachse etwa das 1,0fache der Länge des oberen Pleuelabschnitts beträgt und der Fußpunkt der Projektion der Anlenkstelle auf die Zylinderachse von der Kurbelwellenachse einen Abstand besitzt, der etwa 1/3 des Abstands des kolbenseitigen Pleuellagers des oberen Pleuelabschnitts von der Kurbelwellenachse im oberen Totpunkt des Kolbens beträgt. Die dadurch gewährleistete relativ lange Verweilzeit des Kolbens in seinem oberen Totpunkt erlaubt die Verbrennung des Kraftstoffs und die Kolbenbewegung optimal aufeinander abzustimmen, wobei die Verbrennung im oberen Totpunkt beginnt. Eine solche Verschiebung des Einspritzungsintervalls in Richtung auf einen späteren Zeitpunkt hin ist deswegen möglich, weil der Kolben länger im Bereich seiner oberen Totpunktstellung verweilt. Dies bringt auch einen verringerten Zündverzug mit verringerten Temperaturen und Druckbelastungen für den Motor. Versuche haben außerdem gezeigt, daß eine erhebliche Kraftstoffeinsparung unter Beibehaltung gleicher Leistungen erzielbar ist. Schließlich ist auch die Verwendung unterschiedlicher Kraftstoffe möglich, da die Kolbengeschwindigkeit veränderbar und den jeweiligen Kraftstoffen anpaßbar ist. Versuche haben bewiesen, daß Dieselmotore mit der beschriebnen Kinematik ohne Umstellungsmaßnahmen und ohne Leistungsabfall auch mit Benzin betrieben werden können. Außerdem besteht die Möglichkeit, wegen der geringeren Kolbenbelastung Kolben schwächerer Ausbildung oder mit geringerem Gewicht zu verwenden.An advantageous embodiment of the internal combustion engine can be achieved if the length of the lower connecting rod section is approximately 1.3 times the length of the upper connecting rod section, the total length of both connecting rods Sections about 3% larger than the distance between the connecting rod bearing of the upper connecting rod portion and the circle described by the connecting rod bearing of the lower connecting rod portion in the top dead center of the piston and that the length of the pivot lever is carried out approximately 1.2 times the length of the upper connecting rod portion is, the radial distance of the pivot point of the pivot lever from the cylinder axis is approximately 1.0 times the length of the upper connecting rod section and the base point of the projection of the pivot point on the cylinder axis from the crankshaft axis is a distance that is approximately 1/3 of the distance from the piston rod bearing of the upper connecting rod section from the crankshaft axis at the top dead center of the piston. The relatively long residence time of the piston in its top dead center that is guaranteed thereby allows the combustion of the fuel and the piston movement to be optimally coordinated with one another, the combustion starting at the top dead center. Such a shift of the injection interval towards a later point in time is possible because the piston remains longer in the area of its top dead center position. This also results in reduced ignition delay with reduced temperatures and pressure loads for the engine. Tests have also shown that considerable fuel savings can be achieved while maintaining the same performance. Finally, the use of different fuels is also possible, since the piston speed can be changed and adapted to the respective fuels. Experiments have shown that diesel engines with the described kinematics can also be operated with petrol without conversion measures and without a drop in performance. There is also the possibility of using pistons of weaker design or with a lower weight because of the lower piston load.

In Ausgestaltung der Verbrennungskraftmaschine ist noch vorgesehen, daß der obere Pleuelabschnitt gabelförmig ausgebildet ist und eine Lagerscheibe verdrehungsfrei fest trägt, an die der untere Pleuelabschnitt zentrisch und der Schwenkhebel exzentrisch mit den der Kurbelwelle bzw. der Stützachse abgewandten Enden angelenkt sind. Bevorzugt weisen die Gabelenden des oberen Pleuelabschnitts Absetzungen auf, die durch die Lagerscheibe überragt sind, wobei die Umfangsfläche der Lagerscheibe den unteren Pleuelabschnitt stützt und der im Bereich der Absetzungen sich erstreckende Teil der Lagerscheibe mit dem Schwenkhebel gelenkig verbunden ist. Hierdurch ist auf einfache Weise die geforderte axiale Verlängerung am oberen Pleuelabschnitt und darüberhinaus ein schmaler Aufbau für das durch die Pleuelabschnitte gebildete Pleuel erzielt, wodurch die Pleuelabschnitte und der Schwenkhebel auch in Mehrzylindermaschinen platzsparend untergebracht werden können. Ferner ist noch vorgesehen, die Stützachse vorteilhaft im Motorgehäuse auszubilden. Auch ist es möglich die Stützachse außerhalb des Motorblocks anzuordnen. Bei der letztgenannten Ausführung durchgreift der Schwenkhebel zur Verbindung mit der Stützachse eine Ausnehmung in der Motorgehäusewandung.In an embodiment of the internal combustion engine, it is also provided that the upper connecting rod section is fork-shaped and carries a bearing washer fixedly against rotation, to which the lower connecting rod section is articulated and the pivoting lever is eccentrically articulated with the ends facing away from the crankshaft or the support axis. The fork ends of the upper connecting rod section preferably have steps which are protruded by the bearing plate, the peripheral surface of the bearing plate supporting the lower connecting rod section and the part of the bearing plate extending in the area of the steps being articulated to the pivot lever. As a result, the required axial extension at the upper connecting rod section and, moreover, a narrow construction for the connecting rod formed by the connecting rod sections is achieved, as a result of which the connecting rod sections and the pivoting lever can also be accommodated in a space-saving manner in multi-cylinder machines. It is also provided that the support axis is advantageously formed in the motor housing. It is also possible to arrange the support axis outside the engine block. In the latter embodiment, the pivot lever for connection to the support axis extends through a recess in the motor housing wall.

Die Erfindung ist anhand eines Ausführungsbeispiels in der Zeichnung verdeutlicht. Hierin zeigen:

Fig. 1
eine Kraft- oder Arbeitsmaschine schematisch im Schnitt,
Fig. 2
eine Kraft- oder Arbeitsmaschine im Schnitt,
Fig. 3
Teilstücke von Pleuelabschnitten und Schwenkhebel in Seitenansicht,
Fig. 4 und 5
verschiedene graphische Darstellungen
The invention is illustrated using an exemplary embodiment in the drawing. Show here:
Fig. 1
a motor or work machine schematically in section,
Fig. 2
a machine or machine on average,
Fig. 3
Parts of connecting rod sections and swivel levers in side view,
4 and 5
various graphical representations

In den Fig. ist mit 1 ein Zylinder, z.B. einer Verbrennungskraftmaschine bezeichnet, der einen Kolben 2 verschieblich aufnimmt. Der Zylinder 1 ist beim Ausführungsbeispiel am oberen Ende durch einen plattenförmigen Zylinderkopf 3 verschlossen. Die Einrichtungen für die Zuführung von Brennstoff und Luft bzw. Brennstoffgemisch und der Abführung von Verbrennungsgasen sind aus Gründen der Übersicht nicht dargestellt.In the figures, 1 is a cylinder, e.g. referred to an internal combustion engine that slidably receives a piston 2. In the exemplary embodiment, the cylinder 1 is closed at the upper end by a plate-shaped cylinder head 3. The devices for the supply of fuel and air or fuel mixture and the removal of combustion gases are not shown for reasons of clarity.

Der Kolben 2 nimmt einen Kolbenbolzen 4 auf, an dem ein oberer Pleuelabschnitt 5 mit seinem oberen Lager 6 schwenkbeweglich angreift. Der Pleuelabschnitt 5 ist vorzugsweise gabelförmig ausgeführt und die Schenkel 7 des Pleuelabschnitts 5 halten im Bereich der freien Enden mittels Bolzen 8 eine Lagerscheibe 9 (Fig. 2,3), an die das obere Ende eines unteren Pleuelabschnitts 10 angelenkt ist, der mit seinem unteren Lager 18 an einer Kurbelwelle 11 angreift. Die Schenkel 7 weisen Absetzungen 12 auf, die durch die Lagerscheibe 9 überragt sind. An der Lagerscheibe 9 greift mittels eines Bolzen 13 ein Schwenkhebel 14 mit einem Ende 14'' gelenkig an, der mit seinem anderen Ende 14' in einem an einer Stützachse 15 exzentrisch angeordneten Lager 16 schwenkbar gestützt ist. Wie insbesondere die Fig. 1 und 3 zeigen, ist die Anlenkstelle für den Schwenkhebel 14 am oberen Pleuelabschnitt 5 um die Verlängerung 27 über die gemeinsame Anlenkstelle beider Pleuelabschnitte 5 und 10 hinausgeführt. Durch Verdrehen der Stützachse 15 sind die Stellungen des Lagers 16 und damit die wirksame Länge des Schwenkhebels 14 veränderbar.The piston 2 receives a piston pin 4, on which an upper connecting rod section 5 engages with its upper bearing 6 such that it can pivot. The connecting rod section 5 is preferably fork-shaped and the legs 7 of the connecting rod section 5 hold in the area of the free ends by means of bolts 8 a bearing disc 9 (FIG. 2, 3) to which the upper end of a lower connecting rod section 10 is articulated, the lower end of which Bearing 18 engages a crankshaft 11. The legs 7 have shoulders 12 which are surmounted by the bearing disk 9. On the bearing disc 9, a pivot lever 14 with one end 14 ″ acts in an articulated manner by means of a bolt 13, which is pivotally supported with its other end 14 ′ in a bearing 16 arranged eccentrically on a support axis 15. 1 and 3 in particular, the articulation point for the pivot lever 14 on the upper connecting rod section 5 is extended by the extension 27 beyond the common articulation point of both connecting rod sections 5 and 10. By turning the support axis 15, the positions of the bearing 16 and thus the effective length of the pivot lever 14 can be changed.

In Fig. 1 befindet sich der Kolben 2 im oberen Totpunkt. Bei Abwärtsbewegungen des Kolbens 2 bewegt sich das kolbenseitige Pleuellager 6 längs der Zylinderachse 22 und die Lagerscheibe 9 auf einer Bewegungsbahn in Form eines Kreisbogens 17. Der Bolzen 13 bewegt sich auf einer weiteren Kreisbahn 21. Gleichzeitig dreht die Kurbelwelle 11 und mit ihr das kurbelwellenseitige Lager 18 in Richtung des Pfeils 19. Die Lageänderungen der Pleuelabschnitte 5,10 und des Schwenkhebels 14 im unteren Totpunkt des Kolbens 2 entsprechen den gestrichelten Linien. Die entsprechende Stellung des kurbelwellenseitigen Lagers 18 ist durch die Buchstaben UT bezeichnet. Es zeigt sich, daß bei Abwärtsbewegungen des Kolbens 2 aus dem oberen Totpunkt sich die Bewegungsbahn 17 für die Lagerscheibe 9 der Zylinderachse 22 annähert und diese im weiteren Verlauf der Abwärtsbewegungen des Kolbens 2 schneidet. Hierdurch ist erreicht, daß der Kolben 2 bei seinen Bewegungen aus dem oberen Totpunkt zunächst nur langsam vom Totpunkt entfernt wird, während das kurbelwellenseitige Pleuellager 18 bereits einen relativ großen Kurbelwellenwinkel durchläuft und der untere Pleuelabschnitt 10 eine Stellung erreicht, in der er in der Lage ist, ein großes Drehmoment zu übertragen. Dieser Zusammenhang läßt sich aus den in den Fig. 3 und 4 dargestellten Kurven entnehmen. Die Fig. 4 zeigt dabei mit der ausgezogenen Linie 23 einen Momentverlauf bei einer Verbrennungskraftmaschine erfindungsgemäßer Ausbildung. Auf der Abszisse sind die 360 einer Kurbelwellenumdrehung und auf der Ordinate der für konstante Kolbenaufdruckkraft ermittelte Momentenwert aufgetragen. Die gestrichelte Linie 24 gibt den Momentenverlauf bei einem herkömmlichen Vergleichsmotor wieder. Es zeigt sich, daß das maximale Drehmoment mit der Linie 23 bei etwa 45 Kurbelwellenumdrehung erreichbar ist. Geht man mit diesen Werten in die Fig. 3, welche den Kolbenweg über der Kurbelwellenumdrehung zeigt, wobei die ausgezogene Linie 25 die erfindungsgemäße Verbrennungskraftmaschine und die gestrichelte Linie 26 für einen herkömmlichen Vergleichsmotor (Linie 26) seinen oberen Totpunkt früher verläßt und später wieder erreicht, also insgesamt sehr viel kürzer im Bereich seiner oberen Totpunktstellung verweilt als der Kolben 2 der erfindungsgemäßen Ausführung (Linie 25).In Fig. 1, the piston 2 is at top dead center. When the piston 2 moves downward, the connecting rod bearing 6 on the piston side moves along the cylinder axis 22 and the bearing disc 9 moves on a movement path Form of a circular arc 17. The bolt 13 moves on a further circular path 21. At the same time, the crankshaft 11 and with it the crankshaft-side bearing 18 rotate in the direction of the arrow 19. The changes in position of the connecting rod sections 5, 10 and the pivot lever 14 at the bottom dead center of the piston 2 correspond to the dashed lines. The corresponding position of the crankshaft bearing 18 is designated by the letters UT. It can be seen that when the piston 2 moves downward from the top dead center, the movement path 17 for the bearing disk 9 approaches the cylinder axis 22 and cuts it in the further course of the downward movements of the piston 2. It is thereby achieved that the piston 2 is initially only slowly removed from the dead center during its movements from the top dead center, while the connecting rod bearing 18 on the crankshaft side already runs through a relatively large crankshaft angle and the lower connecting rod section 10 reaches a position in which it is able to transmit a large torque. This relationship can be seen from the curves shown in FIGS. 3 and 4. 4 shows with the solid line 23 a torque curve in an internal combustion engine according to the invention. The 360 of a crankshaft revolution is plotted on the abscissa and the torque value determined for constant piston pressure force is plotted on the ordinate. The dashed line 24 shows the torque curve in a conventional comparison motor. It can be seen that the maximum torque can be achieved with line 23 at approximately 45 crankshaft revolutions. 3, which shows the piston travel over the crankshaft revolution, the solid line 25 leaving the internal combustion engine according to the invention and the dashed line 26 for a conventional comparison engine (line 26) leaving its top dead center earlier and later Reached again, that is to say it remains much shorter in the region of its top dead center position than the piston 2 of the embodiment according to the invention (line 25).

Messungen beim Betrieb des Motors mit der beanspruchten Kinematik von Pleuelabschnitten und Schwenkhebel haben gezeigt, daß ein um 40 % geringerer Kraftstoffverbrauch bzw. eine entsprechende höhere Leistung erreichbar ist. Darüberhinaus enthalten die Abgase weniger Schadstoffe. Bei den Abgasen geht der Anteil an Stickoxyd um ca. 55%, der Anteil an Rußteilchen um ca. 75 % zurück. Wie gesagt, entstehen auch geringere Spitzendrucke und man erhält durch den kürzeren Zündverzug eine weiche Verbrennung, das heißt, annähernd eine Gleichraumverbrennung. Der Lauf der Brennkraftmaschine wird dadurch ruhiger. Der Betrieb der Verbrennungskraftmaschine kann mit Dieselkraftstoff, Benzin oder anderweitigen, auch geringwertigen Kraftstoffen erfolgen.Measurements during the operation of the engine with the claimed kinematics of connecting rod sections and swivel levers have shown that a 40% lower fuel consumption or a correspondingly higher output can be achieved. In addition, the exhaust gases contain fewer pollutants. The proportion of nitrogen oxide in exhaust gases decreases by approx. 55% and the proportion of soot particles by approx. 75%. As I said, lower peak pressures also occur and the shorter ignition delay results in a soft combustion, that is to say, approximately uniform combustion. This makes the engine run more smoothly. The internal combustion engine can be operated with diesel fuel, gasoline or other fuels, including low-quality fuels.

Claims (9)

  1. A power engine or production machine, more especially an internal combustion engine, including at least one cylinder and one piston, which is axially displaceable in said cylinder and is connected to the crankshaft via the intermediary of an upper connecting-rod portion and a lower connecting-rod portion, which is connected to the upper connecting-rod portion by means of a common pivot joint, and wherein both connecting-rod portions are supported on an adjustable axle, which is secured to the engine housing, by means of a pivotally mounted common pivotal lever, characterised in that the upper connecting-rod portion (5) includes an axial extension (27), which extends beyond the common pivot joint (9), at the end remote from the pistons (2), and in that the pivotal lever (14) engages pivotally with the extension (27) by the end (14'') facing the connecting-rod portions (5, 10).
  2. Power engine or production machine according to claim 1, characterised in that the supporting axle (15) for the pivotal lever (14) is eccentrically adjustable.
  3. Power engine or production machine according to claim 2, characterised in that the supporting axle (15) is adjustable radially relative to the central longitudinal axis (22) of the cylinder (1).
  4. Power engine or production machine according to claim 2, characterised in that the supporting axle (15) is axially adjustable transversely relative to the central longitudinal axis (22) of the cylinder (1).
  5. Power engine or production machine according to claim 1, characterised in that the upper connecting-rod portion (5) is bifurcated and fixedly carries a bearing disc (9) in a torsion-free manner, the lower connecting-rod portion (10) being pivotally mounted centrally on said bearing disc, and the pivotal lever (14) being pivotally mounted eccentrically on said bearing disc by the ends remote from the crankshaft (11) or supporting axle (15).
  6. Power engine or production machine according to claim 5, characterised in that the bifurcated ends of the connecting-rod portion (5) have shoulder portions (12), which protrude through the bearing disc (9), and in that the bearing disc (9) supports the lower connecting-rod portion (10) with its circumferential surface and is pivotally connected to the pivotal lever (14) in the region of the shoulder portions (12).
  7. Power engine or production machine according to claim 2, characterised in that the supporting axle (15) is disposed in the engine housing.
  8. Power engine or production machine according to claim 2, characterised in that the supporting axle (15) is disposed externally of the engine housing.
  9. Power engine or production machine according to claim 1, characterised in that the length of the lower connecting-rod portion (10) amounts to substantially 1.3 times the length of the upper connecting-rod portion (5), the total length of both connecting-rod portions (5, 10) is substantially 3 % greater than the spacing between the connecting-rod bearing (6) at the piston end of the upper connecting-rod portion (5) and the circle described by the connecting-rod bearing (18) at the crankshaft end of the lower connecting-rod portion (10) in the upper dead centre of the piston (2), and in that the length of the pivotal lever (14) is substantially 1.2 times the length of the upper connecting-rod portion (5), the radial spacing between the pivotal mounting position of the pivotal lever (14) and the axis (22) of the cylinder is substantially 1.0 times the length of the upper connecting-rod portion (5), and the base of the projection of the bearing (16) onto the axis of the cylinder from the axis of the crankshaft has a spacing which is substantially 1/3 of the spacing between the connecting-rod bearing (6) at the piston end of the upper connecting-rod portion (5) and the axis of the crankshaft in the upper dead centre of the piston (2).
EP87111871A 1987-05-08 1987-08-17 Prime mover, particularly an internal combustion engine Expired - Lifetime EP0292603B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
AT87111871T ATE60881T1 (en) 1987-05-08 1987-08-17 ENGINE OR WORK MACHINE, ESPECIALLY AN INTERNAL COMBUSTION ENGINE.
JP63504861A JP2693197B2 (en) 1987-05-08 1988-05-03 Power or work machines, especially internal combustion engines
PCT/EP1988/000367 WO1988008922A1 (en) 1987-05-08 1988-05-03 Driving or working engine, in particular an internal combustion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873715391 DE3715391A1 (en) 1987-05-08 1987-05-08 INTERNAL COMBUSTION ENGINE OR OTHER DRIVE
DE3715391 1987-05-08

Publications (2)

Publication Number Publication Date
EP0292603A1 EP0292603A1 (en) 1988-11-30
EP0292603B1 true EP0292603B1 (en) 1991-02-13

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EP87111871A Expired - Lifetime EP0292603B1 (en) 1987-05-08 1987-08-17 Prime mover, particularly an internal combustion engine

Country Status (6)

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US (1) US4957069A (en)
EP (1) EP0292603B1 (en)
JP (1) JP2693197B2 (en)
AT (1) ATE60881T1 (en)
DE (3) DE3715391A1 (en)
WO (1) WO1988008922A1 (en)

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DE102004040841A1 (en) * 2004-08-23 2006-03-02 Helmut Obieglo Stroke transmission for internal combustion engine has lower piston rod and extension that are angled relative to each other
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Also Published As

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JP2693197B2 (en) 1997-12-24
EP0292603A1 (en) 1988-11-30
WO1988008922A1 (en) 1988-11-17
ATE60881T1 (en) 1991-02-15
US4957069A (en) 1990-09-18
DE8711149U1 (en) 1988-06-09
DE3768029D1 (en) 1991-03-21
JPH02500379A (en) 1990-02-08
DE3715391A1 (en) 1988-12-01
DE3715391C2 (en) 1991-11-14

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