EP0314773B1 - Driving or working engine, in particular an internal combustion engine - Google Patents

Driving or working engine, in particular an internal combustion engine Download PDF

Info

Publication number
EP0314773B1
EP0314773B1 EP88905184A EP88905184A EP0314773B1 EP 0314773 B1 EP0314773 B1 EP 0314773B1 EP 88905184 A EP88905184 A EP 88905184A EP 88905184 A EP88905184 A EP 88905184A EP 0314773 B1 EP0314773 B1 EP 0314773B1
Authority
EP
European Patent Office
Prior art keywords
engine
cylindrical portion
rod portion
piston
connecting 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.)
Expired - Lifetime
Application number
EP88905184A
Other languages
German (de)
French (fr)
Other versions
EP0314773A1 (en
Inventor
Gerhard Mederer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE19873715391 external-priority patent/DE3715391A1/en
Application filed by Individual filed Critical Individual
Priority to AT88905184T priority Critical patent/ATE66721T1/en
Publication of EP0314773A1 publication Critical patent/EP0314773A1/en
Application granted granted Critical
Publication of EP0314773B1 publication Critical patent/EP0314773B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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

Definitions

  • the invention relates to an engine or working machine, in particular an internal combustion engine with an upper connecting rod section and a lower connecting rod section between the piston and the crankshaft, which are connected to one another by a common joint and in which the two connecting rod sections are supported by an articulated pivot lever on an axle fixed to the motor housing.
  • the upper connecting rod section has a strip-shaped web symmetrically in the longitudinal center plane with a cylinder section arranged at the end facing away from the piston, the partial sections of which project beyond the web on both sides and support ring parts of the lower connecting rod section and in that in the upper cylinder section the web plane and recesses are provided in the lower connecting rod section between the ring parts, which are penetrated transversely by a bolt which is eccentrically mounted in the cylinder section at a distance from the cylinder section axis and on which the pivot lever engages with one end.
  • the web allows bending stresses to be absorbed and compensated for within limits. Furthermore, a narrow construction of the connecting rod is achieved, so that the counterweights of the crankshaft are kept low and can be designed to save space.
  • the lower connecting rod section is formed by halves connected to one another over a partial length by clamping members, for example screws, which each have one of the ring parts on the piston-side ends, the common width of both connecting rod section halves is equal to or less than the axial length of the cylinder section.
  • the division of the lower connecting rod section provides the prerequisites for simple assembly of the connecting rod sections and the swivel lever.
  • the two ring parts of the lower connecting rod section are supported on the partial sections of the upper connecting rod section instead of known slide bearings by needle bearings.
  • the bolt is press-fit by the pivot lever and is held in the cylinder section without displacement by means of the pivot lever.
  • 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, as in particular FIGS. 2 to 6 show a piston pin 32 on which the upper connecting rod section 30 is mounted with its upper bearing 31. Furthermore, the connecting rod section 30 has a cylinder section 33 at the end facing away from the piston 2.
  • the bearing 31 and the cylinder portion 33 are connected to each other by a web 34 'extending symmetrically to the longitudinal central axis of the upper connecting rod portion 30'.
  • ring parts 36 and 36' of a connecting rod 35 connected to its bearing 34 with the crankshaft 11 are supported.
  • the bearing 31, the sections 33 'and 33 ⁇ and the bearing 34 take needle bearings 43.
  • a pivot lever 39 extends, which comprises a pin 40 rotatably guided in the sections 33 'and 33 ⁇ with a press fit and with its other end 39th 'Is supported on a support fixed to the motor housing, for example a pin 41 arranged eccentrically on a rotatably adjustable disk 44.
  • the bolt 40 with its central axis, as shown in the figures, is offset from the central axis of the cylinder section 33 by an extension 27.
  • the design of the connecting rod sections 30 and 35 provides a particularly narrow connecting rod with reduced weight, whereby a favorable mass balance and an advantageous guidance of the crankshaft 11 to the connecting rod can take place.
  • the web 34 'of the upper connecting rod section 30 provides free spaces 45 on both sides, through which crankshaft parts, for example mass balancing weights, can be passed.
  • the pivot lever 39 acts on the connecting rod sections 30 and 35 in the region of the longitudinal center plane, as a result of which tilting moments on the pivot lever 39 and connecting rod sections 30, 35 are avoided.
  • a rotating shaft can also be used as a support member for the pivot lever 39.
  • the lower connecting rod section 35 is formed in the exemplary embodiment by halves 35 ', 35 ⁇ , which are formed by clamping members, e.g. Screws 44 are held together. To avoid protruding ends, depressions 46 are provided for receiving the screw heads 47 and nuts 48 of the clamping members.
  • the piston 2 is at top dead center.
  • the piston pin 32 moves along the cylinder axis 22 and the ring parts 36, 36 'on a movement path in the form of a circular arc 17.
  • the bolt 40 moves on a further circular path 21.
  • the crankshaft 11 rotates and with it the crankshaft-side bearing 34 in the direction of arrow 19.
  • the changes in position of the connecting rod sections 30, 35 and the pivot lever 39 at the bottom dead center of the piston 2 correspond to the dashed lines.
  • the corresponding position of the bearing 34 on the crankshaft side is designated by the letters UT.
  • FIG. 7 shows with the solid line 23 a torque curve in an internal combustion engine of the design 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 rotation and with the dashed line at approximately 65 ° crankshaft rotation. If one goes with these values in FIG.

Landscapes

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

Abstract

The engine has one or more pistons working in cylinders and coupled via top and bottom connecting rod sections to the crankshaft. The two sections are supported from an adjustable shaft in the engine housing by a lever, coupled to the joint between then. The top section (5) has at the end away from the piston (2) an axial extension (27) beyond the joint (9) to the bottom section (10). The lever (14) is hinged at this end (14") on the extension.

Description

Die Erfindung betrifft eine Kraft- oder Arbeitsmaschine, insbesondere Verbrennungskraftmaschine mit einem oberen Pleuelabschnitt und einem unteren Pleuelabschnitt zwischen Kolben und Kurbelwelle, die durch ein gemeinsames Gelenk miteinander verbunden sind und bei der die beiden Pleuelabschnitte durch einen angelenkten Schwenkhebel an einer motorgehäusefesten Achse abgestützt sind.The invention relates to an engine or working machine, in particular an internal combustion engine with an upper connecting rod section and a lower connecting rod section between the piston and the crankshaft, which are connected to one another by a common joint and in which the two connecting rod sections are supported by an articulated pivot lever on an axle fixed to the motor housing.

Bei der Verbrennungskraftmaschine (DE-PS 3030615) sind der Kolben und die Kurbelwelle durch zwei gelenkig verbundene Pleuelabschnitte miteinander verbunden. Außerdem findet bei dieser Verbrennungskraftmaschine ein an dem gemeinsamen Gelenk für die beiden Pleuelabschnitte angreifender Schwenkhebel Anwendung, der mit seinem anderen Ende an einem veränderlich einstellbaren Exzenter abgestützt ist. Obwohl bei dieser Verbrennungskraftmaschine die Kinematik der beiden Pleuelabschnitte mit dem Schwenkhebel bereits zu einer verlängerten Verweilzeit des Kolbens in seinem oberen Totpunkt und damit zu einem verbesserten Drehmomentenverlauf führt, ist zu einer weiteren Verbesserung des Drehmomentenverlaufs bei einer Verbennungskraftmaschine dieser Art (EP-A-0292603) vorgeschlagen, den oberen Pleuelabschnitt mit einer über das gemeinsame Gelenk hinausgeführten Verlängerung zu versehen und den Schwenkhebel an der Verlängerung angreifen zu lassen.In the internal combustion engine (DE-PS 3030615), the piston and the crankshaft are connected to one another by two articulated connecting rod sections. In addition, this internal combustion engine uses a pivot lever which engages the common joint for the two connecting rod sections and which is supported at its other end on a variably adjustable eccentric. Although in this internal combustion engine the kinematics of the two connecting rod sections with the pivot lever already leads to an extended dwell time of the piston in its top dead center and thus to an improved torque curve, there is a further improvement in the torque curve in an internal combustion engine of this type (EP-A-0292603) proposed to provide the upper connecting rod section with an extension extending beyond the common joint and to allow the pivot lever to engage the extension.

Es ist Aufgabe der Erfindung, bei Verbrennungskraftmaschinen der vorliegenden Gattung, Maßnahmen zu Leistungssteigerungen bei verringertem Gewicht und zum Verbessern des Massenausgleichs sowie zum Betrieb mit unterschiedlichen Kraftstoffen zu schaffen.It is an object of the invention to provide measures for performance increases with reduced weight and for improving the mass balance and for operation with different fuels in internal combustion engines of the present type.

Erfindungsgemäß ist diese Aufgabe gelöst dadurch, daß der obere Pleuelabschnitt symmetrisch in der Längsmittelebene einen streifenförmigen Steg mit einem an dem dem Kolben abgewandten Ende angeordneten Zylinderabschnitt fest aufweist, dessen den Steg zu beiden Seiten überragende Teilabschnitte Ringteile des unteren Pleuelabschnitts lagern und daß im oberen Zylinderabschnitt in der Stegebene und im unteren Pleuelabschnitt zwischen den Ringteilen Ausnehmungen vorgesehen sind, die quer durch einen im Zylinderabschnitt im Abstand der Zylinderabschnittsachse exzentrisch gelagerten Bolzen durchgriffen sind, an dem der Schwenkhebel mit einem Ende angreift. Abgesehen der auf diese Weise erreichten Gewichtseinsparung, insbesondere beim oberen Pleuelabschnitt, Bolzen und Schwenkhebel von etwa einem Drittel gegenüber dem Gewicht der bekannten Verbrennungskraftmaschinen, erlaubt der Steg Biegebeanspruchungen in Grenzen aufzunehmen und auszugleichen. Ferner wird ein schmaler Aufbau des Pleuels erzielt, so daß die Gegengewichte der Kurbelwelle gering gehalten und platzsparend ausbildbar sind.According to the invention, this object is achieved in that the upper connecting rod section has a strip-shaped web symmetrically in the longitudinal center plane with a cylinder section arranged at the end facing away from the piston, the partial sections of which project beyond the web on both sides and support ring parts of the lower connecting rod section and in that in the upper cylinder section the web plane and recesses are provided in the lower connecting rod section between the ring parts, which are penetrated transversely by a bolt which is eccentrically mounted in the cylinder section at a distance from the cylinder section axis and on which the pivot lever engages with one end. In addition to the weight saving achieved in this way, in particular in the case of the upper connecting rod section, bolts and pivot levers of approximately one third compared to the weight of the known internal combustion engines, the web allows bending stresses to be absorbed and compensated for within limits. Furthermore, a narrow construction of the connecting rod is achieved, so that the counterweights of the crankshaft are kept low and can be designed to save space.

In Ausgestaltung der Verbrennungskraftmaschine ist vorgesehen, den unteren Pleuelabschnitt durch über eine Teillänge durch Klemmglieder, z.B. Schrauben miteinander verbundene Hälften zu bilden, die an den kolbenseitigen Enden je einen der Ringteile aufweisen, wobei die gegemeinsame Breite beider Pleuelabschnittshälften gleich oder kleiner als die axiale Länge des Zylinderabschnitts ist. Die Teilung des unteren Pleuelabschnitts gibt die Voraussetzung für eine einfache Montage der Pleuelabschnitte und des Schwenkhebels.In an embodiment of the internal combustion engine, it is provided that the lower connecting rod section is formed by halves connected to one another over a partial length by clamping members, for example screws, which each have one of the ring parts on the piston-side ends, the common width of both connecting rod section halves is equal to or less than the axial length of the cylinder section. The division of the lower connecting rod section provides the prerequisites for simple assembly of the connecting rod sections and the swivel lever.

Von besonderem Vorteil hat sich jedoch erwiesen, wenn die beiden Ringteile des unteren Pleuelabschnitts anstelle bekannter Gleitlager durch Nadellager auf die Teilabschnitte des oberen Pleuelabschnitts abgestützt sind. Zur Vermeidung von zusätzlichen Haltegliedern zur Verhütung unerwünschter axialer Bewegungen des Bolzens ist vorgesehen, daß der Bolzen mit Preßsitz durch den Schwenkhebel umfaßt ist und mittels des Schwenkhebels verschiebungsfrei im Zylinderabschnitt gehalten ist.However, it has proven to be particularly advantageous if the two ring parts of the lower connecting rod section are supported on the partial sections of the upper connecting rod section instead of known slide bearings by needle bearings. To avoid additional holding members to prevent undesirable axial movements of the bolt, it is provided that the bolt is press-fit by the pivot lever and is held in the cylinder section without displacement by means of the pivot lever.

Letztlich besteht noch die Möglichkeit, die wirksame Länge des Schwenkhebels dadurch veränderlich zu gestalten, daß der Schwenkhebel mit dem dem Zylinderabschnitt abgewandten Ende an einem auf einer drehbeweglichen Scheibe exzentrisch ausgebildeten Achse oder Welle gelagert ist.Ultimately, there is still the possibility of making the effective length of the pivoting lever variable in that the pivoting lever with the end facing away from the cylinder section is mounted on an axis or shaft which is eccentrically formed on a rotating disc.

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

Fig. 1
eine Kraft- oder Arbeitsmaschine schematisch im Schnitt,
Fig. 2
Pleuelabschnitte und Schwenkhebel gemäß einer Ausführung im Schnitt,
Fig. 3
Pleuelabschnitte und Schwenkhebel gemäß Fig. 2 in Seitenansicht,
Fig. 4
einen oberen Pleuelabschnitt im Schnitt,
Fig. 5
einen unteren Pleuelabschnitt in Vorderansicht
Fig. 6
einen Schwenkhebel in Vorderansicht und
Fig. 7 und 8
verschiedene grafische 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
Connecting rod sections and swivel levers according to one embodiment in section,
Fig. 3
Connecting rod sections and pivot lever according to FIG. 2 in side view,
Fig. 4
an upper connecting rod section in section,
Fig. 5
a lower connecting rod section in front view
Fig. 6
a swivel lever in front view and
7 and 8
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, wie insbesondere die Fig. 2 bis 6 zeigen einen Kolbenbolzen 32 auf, an dem der obere Pleuelabschnitt 30 mit seinem oberen Lager 31 gelagert ist. Weiter weist der Pleuelabschnitt 30 an dem dem Kolben 2 abgewandten Ende einen Zylinderabschnitt 33 auf. Das Lager 31 und der Zylinderabschnitt 33 sind durch einen symmetrisch zur Längsmittelachse des oberen Pleuelabschnitts 30 sich erstreckenden Steg 34′ miteinander verbunden. An den Teilabschnitten 33′ und 33˝ des Zylinderabschnitts 33 sind Ringteile 36 und 36′ eines mit seinem Lager 34 mit der Kurbelwelle 11 verbundenen unteren Pleuelabschnitts 35 gelagert. Das Lager 31, die Teilabschnitte 33′ und 33˝ sowie das Lager 34 nehmen Nadellager 43 auf. Im Zylinderabschnitt 33 und zwischen den Teilabschnitten 33′ und 33˝ sind Ausnehmungen 38 und 38′ vorgesehen, durch die ein Schwenkhebel 39 hindurchgreift, der einen in den Teilabschnitten 33′ und 33˝ drehbar geführten Bolzen 40 mit Preßsitz umfaßt und mit seinem anderen Ende 39′ an einer motorgehäusefesten Abstützung, z.B. einem auf einer drehbar einstellbaren Scheibe 44 exzentrisch angeordneten Zapfen 41 abgestützt ist. Der Bolzen 40 ist mit seiner Mittelachse, wie in den Fig. verdeutlicht, zur Mittelachse des Zylinderabschnitts 33 um eine Verlängerung 27 versetzt. Die Ausgestaltung der Pleuelabschnitte 30 und 35 erbringt ein besonders schmales Pleuel mit verringertem Gewicht, wodurch ein günstiger Massenausgleich und eine vorteilhafte Führung der Kurbelwelle 11 zum Pleuel erfolgen kann. Schließlich erbringt der Steg 34′ des oberen Pleuelabschnitts 30 zu beiden Seiten Freiräume 45, durch die Kurbelwellenteile, etwa Massenausgleichsgewichte hindurchführbar sind. Außerdem greift der Schwenkhebel 39 im Bereich der Längsmittelebene an den Pleuelabschnitten 30 und 35 an, wodurch Kippmomente an Schwenkhebel 39 und Pleuelabschnitten 30, 35 vemieden sind. Es versteht sich, daß anstelle des den Schwenkhebel 39 stützenden Zapfens 41 auch eine umlaufende Welle als Stützglied für den Schwenkhebel 39 Anwendung finden kann.The piston 2 receives, as in particular FIGS. 2 to 6 show a piston pin 32 on which the upper connecting rod section 30 is mounted with its upper bearing 31. Furthermore, the connecting rod section 30 has a cylinder section 33 at the end facing away from the piston 2. The bearing 31 and the cylinder portion 33 are connected to each other by a web 34 'extending symmetrically to the longitudinal central axis of the upper connecting rod portion 30'. At the subsections 33 'and 33˝ of the cylinder section 33, ring parts 36 and 36' of a connecting rod 35 connected to its bearing 34 with the crankshaft 11 are supported. The bearing 31, the sections 33 'and 33˝ and the bearing 34 take needle bearings 43. In the cylinder section 33 and between the sections 33 'and 33˝ recesses 38 and 38' are provided through which a pivot lever 39 extends, which comprises a pin 40 rotatably guided in the sections 33 'and 33˝ with a press fit and with its other end 39th 'Is supported on a support fixed to the motor housing, for example a pin 41 arranged eccentrically on a rotatably adjustable disk 44. The bolt 40, with its central axis, as shown in the figures, is offset from the central axis of the cylinder section 33 by an extension 27. The design of the connecting rod sections 30 and 35 provides a particularly narrow connecting rod with reduced weight, whereby a favorable mass balance and an advantageous guidance of the crankshaft 11 to the connecting rod can take place. Finally, the web 34 'of the upper connecting rod section 30 provides free spaces 45 on both sides, through which crankshaft parts, for example mass balancing weights, can be passed. In addition, the pivot lever 39 acts on the connecting rod sections 30 and 35 in the region of the longitudinal center plane, as a result of which tilting moments on the pivot lever 39 and connecting rod sections 30, 35 are avoided. It goes without saying that, instead of the pivot 41 supporting the pivot lever 39, a rotating shaft can also be used as a support member for the pivot lever 39.

Der untere Pleuelabschnitt 35 ist beim Ausführungsbeispiel durch Hälften 35′, 35˝ gebildet, die durch Klemmglieder, z.B. Schrauben 44 aneinander gehalten sind. Zur Vermeidung überstehender Enden sind Einsenkungen 46 für die Aufnahme der Schraubenköpfe 47 und Muttern 48 der Klemmglieder vorgesehen.The lower connecting rod section 35 is formed in the exemplary embodiment by halves 35 ', 35˝, which are formed by clamping members, e.g. Screws 44 are held together. To avoid protruding ends, depressions 46 are provided for receiving the screw heads 47 and nuts 48 of the clamping members.

In Fig. 1 befindet sich der Kolben 2 im oberen Totpunkt. Bei Abwärtsbewegungen des Kolbens 2 bewegt sich der Kolbenbolzen 32 längs der Zylindersachse 22 und die Ringteile 36, 36′ auf einer Bewegungsbahn in Form eines Kreisbogens 17. Der Bolzen 40 bewegt sich auf einer weiteren Kreisbahn 21. Gleichzeitig dreht die Kurbelwelle 11 und mit ihr das kurbelwellenseitige Lager 34 in Richtung des Pfeils 19. Die Lageänderungen der Pleuelabschnitte 30, 35 und des Schwenkhebels 39 im unteren Totpunkt des Kolbens 2 entsprechen den gestrichelten Linien. Die entsprechende Stellung des kurbelwellenseitigen Lagers 34 ist durch die Buchstaben UT bezeichnet. Es zeigt sich, daß bei Abwärtsbewegungen des Kolbens 2 aus dem oberen Totpunkt sich die Bewegungsbahn 17 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 34 bereits einen relativ grossen Kurbelwellenwinkel durchläuft und der untere Pleuelabschnitt 35 eine Stellung erreicht, in der er in der Lage ist, ein großes Drehmoment zu übertragen.In Fig. 1, the piston 2 is at top dead center. When the piston 2 moves downward, the piston pin 32 moves along the cylinder axis 22 and the ring parts 36, 36 'on a movement path in the form of a circular arc 17. The bolt 40 moves on a further circular path 21. At the same time, the crankshaft 11 rotates and with it the crankshaft-side bearing 34 in the direction of arrow 19. The changes in position of the connecting rod sections 30, 35 and the pivot lever 39 at the bottom dead center of the piston 2 correspond to the dashed lines. The corresponding position of the bearing 34 on the crankshaft side is designated by the letters UT. It can be seen that when the piston 2 moves downward from the top dead center, the path of motion 17 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 34 on the crankshaft side already runs through a relatively large crankshaft angle and the lower connecting rod section 35 reaches a position in which it is able to transmit a large torque.

Die Fig. 7 zeigt mit der ausgezogenen Linie 23 einen Momentenverlauf 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 und bei der gestrichelten Linie bei etwa 65° Kurbelwellenumdrehung erreichbar ist. Geht man mit diesen Werten in die Fig. 8 welche den Kolbenweg über der Kurbelwellenumdrehung zeigt, wobei die ausgezogene Linie 25 die erfindungsgemäße Verbrennungskraftmaschine und die gestrichelte Linie 26 für einen herkömmlichen Vergleichsmotor gelten, so erkennt man, daß der Kolben 2 beim Vergleichsmotor (Linie 26) seinen oberen Totpunkt früher verläßt und später wieder erreicht, also insgesamt sehr viel kürzer im Bereich seiner oberen Totpunkstellung verweilt als der Kolben 2 der erfindungsgemäßen Ausführung (Linie 25).7 shows with the solid line 23 a torque curve in an internal combustion engine of the design 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 rotation and with the dashed line at approximately 65 ° crankshaft rotation. If one goes with these values in FIG. 8, which shows the piston travel over the crankshaft revolution, with the solid line 25 the internal combustion engine according to the invention and the dashed line 26 for a conventional comparison engine, it can be seen that the piston 2 in the comparison engine (line 26 ) leaves its top dead center earlier and reaches it again later, that is to say it stays in the area of its top dead center position much shorter than the piston 2 of the embodiment according to the invention (line 25).

Messungen beim Betrieb des Motors mit der beanspruchten Kinematik von Pleuel und Schwenkhebel haben gezeigt, daß ein um 40% geringerer Kraftstoffverbrauch bzw. eine entsprechend 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, z.B. Pflanzenölen erfolgen. Außerdem bleibt der Motor insgesamt kühler, wodurch ein verkleinertes Kühlsystem Anwendung finden kann. Versuche haben gezeigt, daß der Motor ggf. sogar ohne Wasserkühlung gefahren werden kann. Eine vergrößerte Motorölmenge mit einem notfalls zugordneten Ölkühler dürfte zur Abführung der verringerten Wärmemenge ausreichen. Hierdurch sind auch Vorteile hinsichtlich des Gefrierschutzes bei Winterbetrieb gegeben.Measurements when operating the engine with the stressed connecting rod and swivel arm kinematics 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 arise 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, petrol or other fuels, including low-quality fuels, e.g. Vegetable oils are made. In addition, the engine remains cooler overall, which means that a smaller cooling system can be used. Tests have shown that the engine can even be operated without water cooling. An increased amount of engine oil with an assigned oil cooler should be sufficient to dissipate the reduced amount of heat. This also gives advantages with regard to freeze protection in winter operation.

Claims (5)

1. An engine or production machine, more especially an internal combustion engine, having an upper connecting-rod portion and a lower connecting-rod portion between the piston and crankshaft, said portions being interconnected by means of a common pivot joint, and wherein the two connecting-rod portions are supported by a pivotally mounted pivotal lever on an axle integral with the motor housing, the upper connecting-rod portion (30) being provided symmetrically in the central longitudinal plane with a strip-like web (34) having a cylindrical portion (33) disposed on the end remote from the piston, the partial sections (33′) and (33˝) of which cylindrical portion protrude beyond the web (34) on both sides and support annular portions (36, 36′) of the lower connecting-rod portion (35), and recesses (38, 38′) are provided in the cylindrical portion (33) in the web plane and in the lower connecting-rod portion (35) between the annular portions (36, 36′) and have a bolt/pin (40) extending therethrough, which pin is eccentrically mounted in the cylindrical portion (33) at a distance from the axis of the cylindrical portion, one end of the pivotal lever (39) engaging with said pin.
2. Engine or production machine according to claim 1, characterised in that, over part of its length, the lower connecting-rod portion (35) is formed by halves (35′, 35˝), which are interconnected by means of clamping members (44) and which each have an annular portion (36, 36′) on the ends adjacent to the piston, and in that the joint width of both connecting-rod portion halves (35′, 35˝) is identical to or smaller than the axial length of the cylindrical portion (33).
3. Engine or production machine according to claims 1 and 2, characterised in that the two annular portions (36, 36′) of the lower connecting-rod portion (35) are supported by means of needle bearings (43) on the partial sections (33′, 33˝) of the upper connecting-rod portion (30).
4 Engine or production machine according to claim 1, characterised in that the pin (40) is surrounded by the pivotal lever (39) with a press fit and is retained in the cylindrical portion (33) in a non-displaceable manner by means of the pivotal lever (39).
5. Engine or production machine according to claims 1 and 4, characterised in that the pivotal lever (39) is mounted with the end remote from the cylindrical portion (33) on an axle (41) or shaft, which is provided eccentrically on a rotatable disc (44).
EP88905184A 1987-05-08 1988-05-03 Driving or working engine, in particular an internal combustion engine Expired - Lifetime EP0314773B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88905184T ATE66721T1 (en) 1987-05-08 1988-05-03 ENGINE OR WORK MACHINE, ESPECIALLY AN INTERNAL COMBUSTION ENGINE.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3715391 1987-05-08
DE19873715391 DE3715391A1 (en) 1987-05-08 1987-05-08 INTERNAL COMBUSTION ENGINE OR OTHER DRIVE
DE8711187U 1987-08-17
DE8711187 1987-08-17

Publications (2)

Publication Number Publication Date
EP0314773A1 EP0314773A1 (en) 1989-05-10
EP0314773B1 true EP0314773B1 (en) 1991-08-28

Family

ID=25855359

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88905184A Expired - Lifetime EP0314773B1 (en) 1987-05-08 1988-05-03 Driving or working engine, in particular an internal combustion engine

Country Status (3)

Country Link
EP (1) EP0314773B1 (en)
AT (1) ATE66721T1 (en)
DE (1) DE3864491D1 (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0292603A1 (en) * 1987-05-08 1988-11-30 Gerhard Mederer Prime mover, particularly an internal combustion engine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0292603A1 (en) * 1987-05-08 1988-11-30 Gerhard Mederer Prime mover, particularly an internal combustion engine

Also Published As

Publication number Publication date
ATE66721T1 (en) 1991-09-15
DE3864491D1 (en) 1991-10-02
EP0314773A1 (en) 1989-05-10

Similar Documents

Publication Publication Date Title
EP0292603B1 (en) Prime mover, particularly an internal combustion engine
DE3030615C2 (en) Internal combustion engine
DE7005077U (en) VALVE CONTROL DEVICE FOR COMBUSTION MACHINERY.
DE2539047C2 (en) Reciprocating internal combustion engine
DE19814870A1 (en) Stroke piston internal combustion engine
DE2042632A1 (en) Piston engine
DE10026634C2 (en) Device for changing the compression of a cylinder of a reciprocating piston internal combustion engine
DE2746203A1 (en) Opposing paired cylinders of iC engine - are connected by common piston rod, with independent connecting rods providing swivel connection to crankshaft
EP0314773B1 (en) Driving or working engine, in particular an internal combustion engine
WO2018033276A1 (en) Connection rod for an internal combustion engine with a variable compression
DE69100805T2 (en) SYSTEM FOR REACHING A 4-STROKE CYCLE WITH A REVOLUTION OF THE CRANKSHAFT IN AN INTERNAL COMBUSTION ENGINE.
WO2011107130A1 (en) Method for operating a reciprocating piston engine
DE3114459A1 (en) Crank gear for a reciprocating piston engine
DE3129630A1 (en) Piston drive mechanism for reciprocating piston internal combustion engine
EP0451466B1 (en) Internal combustion piston engine
DE10019959A1 (en) Control method for IC engine uses variation in engine compression and alteration of crankshaft synchronization to change their relative positions
EP0081205B1 (en) Internal combustion wobble plate engine
DE102011017212A1 (en) Crankshaft drive for a reciprocating engine having at least one variably adjustable compression ratio
DE4239074C2 (en) Rotating oscillating piston engine
EP3364010A1 (en) Connecting rod for a combustion engine with variable compression
AT524321B1 (en) internal combustion engine
DE2345225C2 (en)
DE2422394C2 (en)
DE475448C (en) Gearbox for internal combustion engines with opposing pistons
DE19533696A1 (en) Piston=type IC engine

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH DE FR GB IT LI NL SE

17P Request for examination filed

Effective date: 19890512

17Q First examination report despatched

Effective date: 19890821

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Effective date: 19910828

REF Corresponds to:

Ref document number: 66721

Country of ref document: AT

Date of ref document: 19910915

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3864491

Country of ref document: DE

Date of ref document: 19911002

ITF It: translation for a ep patent filed

Owner name: SOCIETA' ITALIANA BREVETTI S.P.A.

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: CH

Ref legal event code: AEN

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19940428

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19940510

Year of fee payment: 7

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19940513

Year of fee payment: 7

EAL Se: european patent in force in sweden

Ref document number: 88905184.3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19950503

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19950504

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19950531

Ref country code: CH

Effective date: 19950531

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19950503

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

EUG Se: european patent has lapsed

Ref document number: 88905184.3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19960531

Year of fee payment: 9

Ref country code: AT

Payment date: 19960531

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Effective date: 19970503

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19971201

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 19971201

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20000524

Year of fee payment: 13

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020131

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20020225

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021203

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050503