EP2981690B1 - Internal combustion engine having an oil supply for a cam drive - Google Patents

Internal combustion engine having an oil supply for a cam drive Download PDF

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Publication number
EP2981690B1
EP2981690B1 EP14715217.7A EP14715217A EP2981690B1 EP 2981690 B1 EP2981690 B1 EP 2981690B1 EP 14715217 A EP14715217 A EP 14715217A EP 2981690 B1 EP2981690 B1 EP 2981690B1
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EP
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Prior art keywords
flat
oil supply
internal combustion
combustion engine
cylinder crankcase
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EP14715217.7A
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German (de)
French (fr)
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EP2981690A1 (en
Inventor
Werner Lemme
Marco Sliwa
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Deutz AG
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Deutz AG
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/102—Lubrication of valve gear or auxiliaries of camshaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
    • F01M9/00—Lubrication means having pertinent characteristics not provided for in, or of interest apart from, groups F01M1/00 - F01M7/00
    • F01M9/10—Lubrication of valve gear or auxiliaries
    • F01M9/104—Lubrication of valve gear or auxiliaries of tappets

Definitions

  • the invention relates to an internal combustion engine with an oil supply for a cam drive.
  • Such an oil supply to a cam drive is also shown in particular in Fig. 3 shown.
  • the object of the present invention is achieved by an internal combustion engine with a camshaft and at least two flat tappets that are driven by the camshaft and actuate the combustion valves, the flat tappets and / or the camshaft being guided and / or supported in the cylinder crankcase, the flat tappet being essentially in a Receiving bore is arranged in the cylinder crankcase and the flat tappets have at least one constriction and are designed to be lubricated by means of an oil supply.
  • the advantage here is that in the Area of the constriction oil is provided to lubricate the running surface of the cam.
  • a further advantageous embodiment provides that the flat tappet is movably arranged for guidance or mounting, in particular in the area of at least one shaft section.
  • Another advantageous embodiment provides that the shaft section is arranged above a constriction of the flat tappet.
  • An advantageous embodiment provides that one oil supply recess is arranged on the side on which the transverse force forms the smallest play and the other oil supply recess is arranged on the cam run-up side on which the transverse force forms the greatest play. There is almost no play on one side at the upper and lower end of the tappet - opposite each other - and the total play on the other side, so that the greatest possible amount of lubricating oil can be fed to the sliding point between the flat tappet and camshaft.
  • a cylinder crankcase of the internal combustion engine 1 is shown, in which a clockwise rotating camshaft 2 is mounted.
  • a substantially vertically displaceable flat tappet 3 is mounted on the running surface of the camshaft 2 in the cylinder crankcase of the internal combustion engine 1, in particular in a receiving bore in the cylinder crankcase 5.
  • the oil supply 4 from the flat tappet 3 in the cylinder crankcase of the internal combustion engine 1 and the sliding point between the flat tappet 3 and camshaft 2 is arranged in the area of the receiving bore in the cylinder crankcase 5 and the constriction of the flat tappet 10 moving up and down with the flat tappet 3.
  • the receiving bore in the cylinder crankcase 5, in which the movable flat tappet 3 is arranged, has an oil supply recess on the cam follower side (smaller) 6 and an oil supply recess on the cam follower side (larger) 7, by means of which oil reaches the sliding point between the flat tappet 3 and camshaft 2 .
  • the receiving bore in the cylinder crankcase 5 has, at its end inclined towards the camshaft, a shaft section of the cylinder crankcase on the cam follower side 8 and a shaft section of the cylinder crankcase on the cam follower side 9.
  • the shaft section of the cylinder crankcase on the cam follow-up side 8 and the shaft section of the cylinder crankcase on the cam run-up side 9 can be of the same length.
  • the shaft section of the cylinder crankcase on the cam outlet side 8 is smaller than the shaft section of the cylinder crankcase on the cam run-up side 9.
  • a larger amount of oil from the oil supply 4 reaches the area via the annular gap between the flat tappet 3 and the receiving bore in the cylinder crankcase 5 of the shaft section of the cylinder crankcase on the cam run-up side 9 than in the area of the shaft section of the cylinder crankcase on the cam run-out side 8, since the shorter shaft section 9 and the lower pressure loss mean that more oil gets into the larger oil supply recess on the cam run-up side 7.
  • the larger oil supply recess on the cam run-up side 7 can be designed as a groove or notch or as an eccentric hole, as shown in FIG Fig. 2 will be shown.
  • Fig. 2a shows a cylinder crankcase of the internal combustion engine 1 without a camshaft.
  • the flat tappet not shown, is mounted in a receiving bore in the cylinder crankcase 5.
  • the oil supply 4 from the flat tappet 3, not shown, in the cylinder crankcase of the internal combustion engine 1 and the sliding point, also not shown, between the flat tappet 3 and camshaft 2 is arranged in the area of the receiving bore in the cylinder crankcase 5 and the constriction of the flat tappet 10 moving up and down with the flat tappet 3.
  • the receiving bore in the cylinder crankcase 5, in which the movable flat tappet 3, not shown, is arranged, has an oil supply recess on the cam follower side (smaller) 6 and an oil supply recess on the cam run-up side (larger) 7, by means of which oil is applied to the sliding point between the flat tappet 3 and Camshaft 2 arrives.
  • the receiving bore in the cylinder crankcase 5 has on its side inclined towards the camshaft, not shown, oil supply recesses which are produced by means of a drill, the drilling path 11 of which is shown schematically.
  • the shaft section of the cylinder crankcase on the cam run-out side 8 is smaller than the shaft section of the cylinder crankcase on the cam run-up side 9 due to the inclined drilling of the drill bit 11 Receiving hole in the cylinder crankcase 5 in the area of the shaft section of the cylinder crankcase on the cam run-up side 9 than in the area of the shaft section of the cylinder crankcase on the cam run-out side 8, since more oil gets into the larger oil supply recess on the cam run-up side 7 due to the shorter shaft section 9 and the lower pressure loss.
  • the larger oil supply recess on the cam run-up side 7 can be designed as a groove or notch or as an eccentric bore.
  • Figure 2b shows an enlarged detail of Fig. 2a , whereby the drill path of the drill is not shown.
  • Fig. 3a shows a cylinder crankcase of the internal combustion engine 1 without a camshaft.
  • the flat tappet not shown, is mounted in a receiving bore in the cylinder crankcase 5.
  • the oil supply 4 from the flat tappet 3, not shown, in the cylinder crankcase of the internal combustion engine 1 and the sliding point, also not shown, between the flat tappet 3 and camshaft 2 is arranged in the area of the receiving bore in the cylinder crankcase 5 and the constriction of the flat tappet 10 moving up and down with the flat tappet 3.
  • the receiving bore in the cylinder crankcase 5, in which the movable flat tappet 3, not shown, is arranged, has an oil supply recess on the cam run-up side (larger) 7, by means of which oil reaches the sliding point between the flat tappet 3 and camshaft 2.
  • the receiving bore in the cylinder crankcase 5 has on its side inclined towards the camshaft, not shown, an oil supply recess 7 which is produced by means of a drill, the drilling path 11 of which is shown schematically.
  • the shaft section of the cylinder crankcase on the cam run-out side 8 is smaller than the shaft section of the cylinder crankcase on the cam run-up side 9 due to the inclined drilling of the drill bit 11 Receiving hole in the cylinder crankcase 5 in the area and shaft section of the cylinder crankcase on the cam run-up side 9 than in the region of the shaft section of the cylinder crankcase on the cam run-out side 8, since more oil gets into the larger oil supply recess on the cam run-up side 7 due to the shorter shaft section 9 and the lower pressure loss.
  • the larger oil supply recess on the cam run-up side 7 can be designed as a groove or notch or as an eccentric bore.
  • Figure 3b shows an enlarged detail of Fig. 3a , whereby the drill path of the drill is not shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Description

Die Erfindung betrifft eine Brennkraftmaschine mit einer Ölversorgung eines Nockentriebs.The invention relates to an internal combustion engine with an oil supply for a cam drive.

Derartige Brennkraftmaschinen sind bekannt aus der DE 42 14 800 A1 , dort wird eine Ölversorgung eines Nockentriebs insbesondere in Fig. 1 dargestellt. Daran ist nachteilig, dass die Gleitstelle zwischen Nocken und Stößel nicht zuverlässig mit Ol versorgt wird. Die JP S5820311 U beschreibt eine Brennkraftmaschine, gemäss dem Oberbegriff des Anspruchs 1.Such internal combustion engines are known from DE 42 14 800 A1 , there is an oil supply to a cam drive, especially in Fig. 1 shown. This has the disadvantage that the sliding point between the cam and the tappet is not reliably supplied with oil. The JP S5820311 U describes an internal combustion engine according to the preamble of claim 1.

Weiter wird eine derartige Ölversorgung eines Nockentriebs insbesondere in Fig. 3 dargestellt.Such an oil supply to a cam drive is also shown in particular in Fig. 3 shown.

Hier ist der große Aufwand von Nachteil, um einen Ölbehälter samt zugehörigem Ventil zu schaffen.The disadvantage here is the great effort required to create an oil container and associated valve.

Es ist die Aufgabe der vorliegenden Erfindung, eine Brennkraftmaschine mit einer Ölversorgung eines Nockentriebs zu schaffen, die einfach zu fertigen ist und die die Gleitstelle zuverlässig mit Schmiermittel versorgt.It is the object of the present invention to create an internal combustion engine with an oil supply for a cam drive which is easy to manufacture and which reliably supplies the sliding point with lubricant.

Die Aufgabe der vorliegenden Erfindung wird gelöst durch eine Brennkraftmaschine mit einer Nockenwelle und wenigstens zwei durch die Nockenwelle angetriebene, die Verbrennungsventile betätigende Flachstößel, wobei die Flachstößel und/oder die Nockenwelle im Zylinderkurbelgehäuse geführt und/oder gelagert sind, wobei der Flachstößel im Wesentlichen in einer Aufnahmebohrung im Zylinderkurbelgehäuse angeordnet ist und die Flachstößel wenigstens eine Einschnürung aufweisen und mittels einer Ölversorgung schmierbar ausgeführt sind. Hierbei ist von Vorteil, dass im Bereich der Einschnürung Öl zur Schmierung der Lauffläche des Nockens bereitgestellt wird.The object of the present invention is achieved by an internal combustion engine with a camshaft and at least two flat tappets that are driven by the camshaft and actuate the combustion valves, the flat tappets and / or the camshaft being guided and / or supported in the cylinder crankcase, the flat tappet being essentially in a Receiving bore is arranged in the cylinder crankcase and the flat tappets have at least one constriction and are designed to be lubricated by means of an oil supply. The advantage here is that in the Area of the constriction oil is provided to lubricate the running surface of the cam.

Eine weitere vorteilhafte Ausgestaltung sieht vor, dass der Flachstößel zur Führung bzw. Lagerung insbesondere im Bereich wenigstens eines Schaftabschnitts bewegbar angeordnet ist.A further advantageous embodiment provides that the flat tappet is movably arranged for guidance or mounting, in particular in the area of at least one shaft section.

Eine andere vorteilhafte Ausgestaltung sieht vor, dass der Schaftabschnitt oberhalb einer Einschnürung des Flachstößels angeordnet ist.Another advantageous embodiment provides that the shaft section is arranged above a constriction of the flat tappet.

Eine vorteilhafte Ausgestaltung sieht vor, dass die eine Ölversorgungsausnehmung auf der Seite angeordnet ist, auf der die Querkraft das kleinste Spiel bildet und die andere Ölversorgungsausnehmung auf der Nockenauflaufseite angeordnet ist, auf der die Querkraft das größte Spiel bildet. So ergibt sich am oberen und am unteren Ende des Stößels - jeweils gegenüberliegend - auf einer Seite nahezu kein Spiel, auf der anderen Seite ergibt sich das Gesamtspiel, so dass die größtmögliche Menge an Schmieröl der Gleitstelle zwischen Flachstößel und Nockenwelle zugeführt werden kann.An advantageous embodiment provides that one oil supply recess is arranged on the side on which the transverse force forms the smallest play and the other oil supply recess is arranged on the cam run-up side on which the transverse force forms the greatest play. There is almost no play on one side at the upper and lower end of the tappet - opposite each other - and the total play on the other side, so that the greatest possible amount of lubricating oil can be fed to the sliding point between the flat tappet and camshaft.

Weitere wichtige Merkmale und Vorteile ergeben sich aus den Unteransprüchen, aus den Zeichnungen und aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispiels anhand der Zeichnungen. Es zeigen:

Fig. 1
ein Zylinderkurbelgehäuse der Brennkraftmaschine
Fig. 2a
ein Zylinderkurbelgehäuse der Brennkraftmaschine mit Bohrweg
Fig. 2b
einZylinderkurbelgehäuse der Brennkraftmaschine ohne Bohrweg
Fig. 3a
ein Zylinderkurbelgehäuse der Brennkraftmaschine mit einseitigem Bohrweg
Fig. 3b
ein Zylinderkurbelgehäuse der Brennkraftmaschine ohne Bohrweg
Further important features and advantages emerge from the dependent claims, from the drawings and from the following description of a preferred exemplary embodiment with reference to the drawings. Show it:
Fig. 1
a cylinder crankcase of the internal combustion engine
Fig. 2a
a cylinder crankcase of the internal combustion engine with a drill path
Figure 2b
a cylinder crankcase of the internal combustion engine without drilling path
Fig. 3a
a cylinder crankcase of the internal combustion engine with a drilling path on one side
Figure 3b
a cylinder crankcase of the internal combustion engine without a drilling path

In Fig. 1 wird ein Zylinderkurbelgehäuse der Brennkraftmaschine 1 dargestellt, in dem eine im Uhrzeigersinn drehende Nockenwelle 2 gelagert ist.In Fig. 1 a cylinder crankcase of the internal combustion engine 1 is shown, in which a clockwise rotating camshaft 2 is mounted.

Auf der Lauffläche der Nockenwelle 2 ist ein im Wesentlichen vertikal verschiebbar angeordneter Flachstößel 3 im Zylinderkurbelgehäuse der Brennkraftmaschine 1 gelagert, insbesondere in einer Aufnahmebohrung im Zylinderkurbelgehäuse 5. Die Ölversorgung 4 von Flachstößel 3 im Zylinderkurbelgehäuse der Brennkraftmaschine 1 und der Gleitstelle zwischen Flachstößel 3 und Nockenwelle 2 ist im Bereich der Aufnahmebohrung im Zylinderkurbelgehäuse 5 und der sich mit dem Flachstößel 3 auf und ab bewegenden Einschnürung des Flachstößels 10 angeordnet. Die Aufnahmebohrung im Zylinderkurbelgehäuse 5, in der der bewegliche Flachstößel 3 angeordnet ist, weist eine Ölversorgungsausnehmung auf der Nockenablaufseite (kleiner) 6 und eine Ölversorgungsausnehmung auf der Nockenauflaufseite (größer) 7 auf, mittels der Öl auf die Gleitstelle zwischen Flachstößel 3 und Nockenwelle 2 gelangt. Die Aufnahmebohrung im Zylinderkurbelgehäuse 5 weist an ihrem der Nockenwelle zugeneigten Ende einen Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8 und einen Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9 auf. Der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8 und der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9 können gleich lang sein. In einer bevorzugten Ausgestaltung ist der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8 kleiner als der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9. Auf diese Weise gelangt eine größere Ölmenge aus der Ölversorgung 4 über den Ringspalt zwischen Flachstößel 3 und der Aufnahmebohrung im Zylinderkurbelgehäuse 5 in den Bereich des Schaftabschnittes des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9 als in den Bereich von Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8, da durch den kürzeren Schaftabschnitt 9 und den geringeren Druckverlust mehr Öl in die größere Ölversorgungsausnehmung auf der Nockenauflaufseite 7 gelangt. Die größere Ölversorgungsausnehmung auf der Nockenauflaufseite 7 kann als Nut oder als Kerbe ausgeführt sein oder als außermittige Bohrung, wie dies in Fig. 2 gezeigt wird.A substantially vertically displaceable flat tappet 3 is mounted on the running surface of the camshaft 2 in the cylinder crankcase of the internal combustion engine 1, in particular in a receiving bore in the cylinder crankcase 5. The oil supply 4 from the flat tappet 3 in the cylinder crankcase of the internal combustion engine 1 and the sliding point between the flat tappet 3 and camshaft 2 is arranged in the area of the receiving bore in the cylinder crankcase 5 and the constriction of the flat tappet 10 moving up and down with the flat tappet 3. The receiving bore in the cylinder crankcase 5, in which the movable flat tappet 3 is arranged, has an oil supply recess on the cam follower side (smaller) 6 and an oil supply recess on the cam follower side (larger) 7, by means of which oil reaches the sliding point between the flat tappet 3 and camshaft 2 . The receiving bore in the cylinder crankcase 5 has, at its end inclined towards the camshaft, a shaft section of the cylinder crankcase on the cam follower side 8 and a shaft section of the cylinder crankcase on the cam follower side 9. The shaft section of the cylinder crankcase on the cam follow-up side 8 and the shaft section of the cylinder crankcase on the cam run-up side 9 can be of the same length. In a preferred embodiment, the shaft section of the cylinder crankcase on the cam outlet side 8 is smaller than the shaft section of the cylinder crankcase on the cam run-up side 9. In this way, a larger amount of oil from the oil supply 4 reaches the area via the annular gap between the flat tappet 3 and the receiving bore in the cylinder crankcase 5 of the shaft section of the cylinder crankcase on the cam run-up side 9 than in the area of the shaft section of the cylinder crankcase on the cam run-out side 8, since the shorter shaft section 9 and the lower pressure loss mean that more oil gets into the larger oil supply recess on the cam run-up side 7. The larger oil supply recess on the cam run-up side 7 can be designed as a groove or notch or as an eccentric hole, as shown in FIG Fig. 2 will be shown.

Einschnürung des FlachstößelsConstriction of the flat ram

Fig. 2a zeigt ein Zylinderkurbelgehäuse der Brennkraftmaschine 1 ohne Nockenwelle. In einer Aufnahmebohrung im Zylinderkurbelgehäuse 5 wird der nicht dargestellte Flachstößel gelagert. Die Ölversorgung 4 vom nicht dargestellten Flachstößel 3 im Zylinderkurbelgehäuse der Brennkraftmaschine 1 und der ebenfalls nicht dargestellten Gleitstelle zwischen Flachstößel 3 und Nockenwelle 2 ist im Bereich der Aufnahmebohrung im Zylinderkurbelgehäuse 5 und der sich mit dem Flachstößel 3 auf und ab bewegenden Einschnürung des Flachstößels 10 angeordnet. Die Aufnahmebohrung im Zylinderkurbelgehäuse 5, in der der nicht dargestellte und bewegliche Flachstößel 3 angeordnet ist, weist eine Ölversorgungsausnehmung auf der Nockenablaufseite (kleiner) 6 und eine Ölversorgungsausnehmung auf der Nockenauflaufseite (größer) 7 auf, mittels der Öl auf die Gleitstelle zwischen Flachstößel 3 und Nockenwelle 2 gelangt. Die Aufnahmebohrung im Zylinderkurbelgehäuse 5 weist an ihrer der nicht dargestellten Nockenwelle zugeneigten Seite Ölversorgungsausnehmungen auf, die mittels eines Bohrers erzeugt werden, dessen Bohrweg 11 schematisch dargestellt wird. In einer bevorzugten Ausgestaltung ist der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8 durch das schräge Bohren des Bohrers 11 kleiner als der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9. Auf diese Weise gelangt eine größere Ölmenge aus der Ölversorgung 4 über den Ringspalt zwischen Flachstößel 3 und der Aufnahmebohrung im Zylinderkurbelgehäuse 5 in den Bereich des Schaftabschnittes des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9 als in den Bereich des Schaftabschnittes des Zylinderkurbelgehäuses auf der Nockenablaufseite 8, da durch den kürzeren Schaftabschnitt 9 und den geringeren Druckverlust mehr Öl in die größere Ölversorgungsausnehmung auf der Nockenauflaufseite 7 gelangt. Die größere Ölversorgungsausnehmung auf der Nockenauflaufseite 7 kann als Nut oder als Kerbe ausgeführt sein oder als außermittige Bohrung. Fig. 2a shows a cylinder crankcase of the internal combustion engine 1 without a camshaft. The flat tappet, not shown, is mounted in a receiving bore in the cylinder crankcase 5. The oil supply 4 from the flat tappet 3, not shown, in the cylinder crankcase of the internal combustion engine 1 and the sliding point, also not shown, between the flat tappet 3 and camshaft 2 is arranged in the area of the receiving bore in the cylinder crankcase 5 and the constriction of the flat tappet 10 moving up and down with the flat tappet 3. The receiving bore in the cylinder crankcase 5, in which the movable flat tappet 3, not shown, is arranged, has an oil supply recess on the cam follower side (smaller) 6 and an oil supply recess on the cam run-up side (larger) 7, by means of which oil is applied to the sliding point between the flat tappet 3 and Camshaft 2 arrives. The receiving bore in the cylinder crankcase 5 has on its side inclined towards the camshaft, not shown, oil supply recesses which are produced by means of a drill, the drilling path 11 of which is shown schematically. In a preferred embodiment, the shaft section of the cylinder crankcase on the cam run-out side 8 is smaller than the shaft section of the cylinder crankcase on the cam run-up side 9 due to the inclined drilling of the drill bit 11 Receiving hole in the cylinder crankcase 5 in the area of the shaft section of the cylinder crankcase on the cam run-up side 9 than in the area of the shaft section of the cylinder crankcase on the cam run-out side 8, since more oil gets into the larger oil supply recess on the cam run-up side 7 due to the shorter shaft section 9 and the lower pressure loss. The larger oil supply recess on the cam run-up side 7 can be designed as a groove or notch or as an eccentric bore.

Fig. 2b zeigt eine Detailvergrößerung von Fig. 2a, wobei der Bohrweg des Bohrers nicht dargestellt wird. Figure 2b shows an enlarged detail of Fig. 2a , whereby the drill path of the drill is not shown.

In Fig. 3a wird ein Zylinderkurbelgehäuse der Brennkraftmaschine 1 ohne Nockenwelle gezeigt. In einer Aufnahmebohrung im Zylinderkurbelgehäuse 5 wird der nicht dargestellte Flachstößel gelagert. Die Ölversorgung 4 vom nicht dargestellten Flachstößel 3 im Zylinderkurbelgehäuse der Brennkraftmaschine 1 und der ebenfalls nicht dargestellten Gleitstelle zwischen Flachstößel 3 und Nockenwelle 2 ist im Bereich der Aufnahmebohrung im Zylinderkurbelgehäuse 5 und der sich mit dem Flachstößel 3 auf und ab bewegenden Einschnürung des Flachstößels 10 angeordnet. Die Aufnahmebohrung im Zylinderkurbelgehäuse 5, in der der nicht dargestellte und bewegliche Flachstößel 3 angeordnet ist, weist eine Ölversorgungsausnehmung auf der Nockenauflaufseite (größer) 7 auf, mittels der Öl auf die Gleitstelle zwischen Flachstößel 3 und Nockenwelle 2 gelangt. Die Aufnahmebohrung im Zylinderkurbelgehäuse 5 weist an ihrer der nicht dargestellten Nockenwelle zugeneigten Seite eine Ölversorgungsausnehmung 7 auf, die mittels eines Bohrers erzeugt wird, dessen Bohrweg 11 schematisch dargestellt wird. In einer bevorzugten Ausgestaltung ist der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8 durch das schräge Bohren des Bohrers 11 kleiner als der Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9. Auf diese Weise gelangt eine größere Ölmenge aus der Ölversorgung 4 über den Ringspalt zwischen Flachstößel 3 und der Aufnahmebohrung im Zylinderkurbelgehäuse 5 in den Bereich und Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite 9 als in den Bereich von Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite 8, da durch den kürzeren Schaftabschnitt 9 und den geringeren Druckverlust mehr Öl in die größere Ölversorgungsausnehmung auf der Nockenauflaufseite 7 gelangt. Die größere Ölversorgungsausnehmung auf der Nockenauflaufseite 7 kann als Nut oder als Kerbe ausgeführt sein oder als außermittige Bohrung.In Fig. 3a shows a cylinder crankcase of the internal combustion engine 1 without a camshaft. The flat tappet, not shown, is mounted in a receiving bore in the cylinder crankcase 5. The oil supply 4 from the flat tappet 3, not shown, in the cylinder crankcase of the internal combustion engine 1 and the sliding point, also not shown, between the flat tappet 3 and camshaft 2 is arranged in the area of the receiving bore in the cylinder crankcase 5 and the constriction of the flat tappet 10 moving up and down with the flat tappet 3. The receiving bore in the cylinder crankcase 5, in which the movable flat tappet 3, not shown, is arranged, has an oil supply recess on the cam run-up side (larger) 7, by means of which oil reaches the sliding point between the flat tappet 3 and camshaft 2. The receiving bore in the cylinder crankcase 5 has on its side inclined towards the camshaft, not shown, an oil supply recess 7 which is produced by means of a drill, the drilling path 11 of which is shown schematically. In a preferred embodiment, the shaft section of the cylinder crankcase on the cam run-out side 8 is smaller than the shaft section of the cylinder crankcase on the cam run-up side 9 due to the inclined drilling of the drill bit 11 Receiving hole in the cylinder crankcase 5 in the area and shaft section of the cylinder crankcase on the cam run-up side 9 than in the region of the shaft section of the cylinder crankcase on the cam run-out side 8, since more oil gets into the larger oil supply recess on the cam run-up side 7 due to the shorter shaft section 9 and the lower pressure loss. The larger oil supply recess on the cam run-up side 7 can be designed as a groove or notch or as an eccentric bore.

Fig. 3b zeigt eine Detailvergrößerung von Fig. 3a, wobei der Bohrweg des Bohrers nicht dargestellt wird. Figure 3b shows an enlarged detail of Fig. 3a , whereby the drill path of the drill is not shown.

BezugszeichenReference number

  1. 1 Zylinderkurbelgehäuse der Brennkraftmaschine1 cylinder crankcase of the internal combustion engine
  2. 2 Nockenwelle2 camshaft
  3. 3 Flachstößel3 flat tappets
  4. 4 Ölversorgung4 oil supply
  5. 5 Aufnahmebohrung im Zylinderkurbelgehäuse5 Location hole in the cylinder crankcase
  6. 6 Ölversorgungsausnehmung auf der Nockenablaufseite (kleiner)6 Oil supply recess on the cam outlet side (smaller)
  7. 7 Ölversorgungsausnehmung auf der Nockenauflaufseite (größer)7 Oil supply recess on the cam run-up side (larger)
  8. 8 Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenablaufseite8 Shank section of the cylinder crankcase on the cam outlet side
  9. 9 Schaftabschnitt des Zylinderkurbelgehäuses auf der Nockenauflaufseite9 Shank section of the cylinder crankcase on the cam run-up side
  10. 10 Einschnürung des Flachstößels10 Constriction of the flat ram
  11. 11 Weg des Bohrers zur Erzeugung der Ölversorgungsausnehmungen11 Path of the drill to create the oil supply recesses
  12. 12 Nockenwellenlager im Zylinderkurbelgehäuse der Brennkraftmaschine12 camshaft bearings in the cylinder crankcase of the internal combustion engine
  13. 13 Kurbelwellenlager im Zylinderkurbelgehäuse der Brennkraftmaschine13 Crankshaft bearings in the cylinder crankcase of the internal combustion engine

Claims (5)

  1. Internal combustion engine, comprising at least one camshaft, at least two flat tappets which are driven by the camshaft and which actuate combustion valves, wherein the flat tappets and/or the camshaft are guided and/or mounted in the cylinder crankcase, wherein the flat tappet (3) is arranged substantially in a receiving bore (5) in the cylinder crankcase (1) and the flat tappets have at least one constriction (10) and an oil supply (4), which is arranged in particular in the region of said constriction for the purposes of lubricating flat tappets (3) and the running surface of said camshaft (2), and the oil supply recess (7) is arranged on the cam run-on side, on which the lateral force forms the greatest play, characterized in that the mounting of the flat tappet (3) in the region between oil supply (4) and camshaft (2) has a defined play of at least 0.03 mm and at most 0.073 mm in order to convey a defined droplet oil quantity into the region of cam running surface and flat tappet (3).
  2. Internal combustion engine according to Claim 1, characterized in that the flat tappet is, for guidance and/or mounting, arranged movably in particular in the region of at least one shank section (8, 9).
  3. Internal combustion engine according to Claim 2, characterized in that the shank section (8, 9) is arranged below a constriction (10) of the flat tappet (3) .
  4. Internal combustion engine according to one or more of the preceding claims,
    characterized in that the oil supply recess (6) is preferably arranged on the side on which the lateral force forms the smallest play.
  5. Method for operating an internal combustion engine, wherein a device according to one or more of the preceding claims is used in particular for lubricating the camshaft-flat tappet pairing.
EP14715217.7A 2013-04-06 2014-04-02 Internal combustion engine having an oil supply for a cam drive Active EP2981690B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013005959.3A DE102013005959B4 (en) 2013-04-06 2013-04-06 Internal combustion engine with an oil supply to a cam drive and method for operating such
PCT/EP2014/000879 WO2014161662A1 (en) 2013-04-06 2014-04-02 Internal combustion engine having an oil supply for a cam drive

Publications (2)

Publication Number Publication Date
EP2981690A1 EP2981690A1 (en) 2016-02-10
EP2981690B1 true EP2981690B1 (en) 2021-06-09

Family

ID=50439327

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14715217.7A Active EP2981690B1 (en) 2013-04-06 2014-04-02 Internal combustion engine having an oil supply for a cam drive

Country Status (4)

Country Link
EP (1) EP2981690B1 (en)
DE (1) DE102013005959B4 (en)
ES (1) ES2881234T3 (en)
WO (1) WO2014161662A1 (en)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE25154E (en) * 1962-04-10 Means for metering lubricating oil from an
US3299986A (en) * 1965-01-25 1967-01-24 Stephen F Briggs Valve operating lifter and valve train lubricator
US4329949A (en) * 1980-06-30 1982-05-18 Ford Motor Company Cylinder head for an internal-combustion engine
JPS57142112U (en) * 1981-03-03 1982-09-06
JPS5820311U (en) * 1981-07-31 1983-02-08 日産ディーゼル工業株式会社 Tappet scuffing prevention structure
JPS59177709U (en) * 1983-05-16 1984-11-28 日産ディーゼル工業株式会社 Cam tappet lubrication system
DE4214800C2 (en) * 1992-05-04 2000-07-20 Fev Motorentech Gmbh Four-stroke internal combustion engine
DE19529277A1 (en) * 1995-08-09 1997-02-13 Bayerische Motoren Werke Ag Method for operating a hydraulically controlled / regulated camshaft adjusting device for internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
WO2014161662A1 (en) 2014-10-09
DE102013005959B4 (en) 2020-03-26
EP2981690A1 (en) 2016-02-10
DE102013005959A1 (en) 2014-10-09
ES2881234T3 (en) 2021-11-29

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