EP0023250A1 - Actuating mechanism for inlet or exhaust valves of internal-combustion engines - Google Patents

Actuating mechanism for inlet or exhaust valves of internal-combustion engines Download PDF

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Publication number
EP0023250A1
EP0023250A1 EP80103049A EP80103049A EP0023250A1 EP 0023250 A1 EP0023250 A1 EP 0023250A1 EP 80103049 A EP80103049 A EP 80103049A EP 80103049 A EP80103049 A EP 80103049A EP 0023250 A1 EP0023250 A1 EP 0023250A1
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EP
European Patent Office
Prior art keywords
bearing
control lever
oil
bore
oil distribution
Prior art date
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Granted
Application number
EP80103049A
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German (de)
French (fr)
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EP0023250B1 (en
Inventor
Hubert Hitziger
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MAN AG
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MAN Maschinenfabrik Augsburg Nuernberg AG
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Publication of EP0023250A1 publication Critical patent/EP0023250A1/en
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Publication of EP0023250B1 publication Critical patent/EP0023250B1/en
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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
    • F01M9/107—Lubrication of valve gear or auxiliaries of rocker shaft bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • F01M9/101—Lubrication of valve gear or auxiliaries of cam surfaces
    • 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
    • F01M11/00—Component parts, details or accessories, not provided for in, or of interest apart from, groups F01M1/00 - F01M9/00
    • F01M11/02—Arrangements of lubricant conduits

Definitions

  • the invention relates to a valve control mechanism for intake and exhaust valves of internal combustion engines with features according to the preamble of claim 1.
  • Such a valve control mechanism is known from US Pat. No. 3,021,826.
  • the bearings on the control lever are supplied with the same lubricating oil only in a certain position.
  • the lubricating oil supplied can emerge from the bearing gaps at the bearing points more or less throttled during the lubrication phase, so that greater oil losses occur at the location of the lubrication and also a relatively large amount of contamination in the cylinder head cover.
  • maintenance and adjustment measures while the engine is running are practically impossible or can only be carried out with this circumstance due to the escaping and uncontrolled lubricating oil.
  • valve control mechanism in which the lubricating points located on the interacting surfaces of the lubricating points which transmit the force and movement to and from the control lever can be supplied intermittently as a function of the control lever movement with precisely metered amounts of lubricating oil.
  • the inventive division of the annular oil distributor channel into an upper oil distributor chamber and a lower oil distributor chamber and coupling of the oil distributor bores leading to the individual lubrication points to the upper oil distributor chamber ensures that the latter is connected to the lubricating oil supply only in one position of the control lever when the valves are open and can be filled with lubricating oil are. In this position of the control lever, however, the lubricating oil fed into the oil distribution bores cannot escape at the lubrication points, since the interacting surfaces of the bearing elements transmitting the force and movement to and from the control lever while closing the lubricating oil outlet openings due to the counterpressure of the opened valves and the cam-actuated push rod and under a we press well above the lubricating oil pressure.
  • the amount of lubricating oil in the oil distributor bores can only emerge from the now open oil distributor bores when the control lever is in the position, namely when the valves are closed and the push rod is not actuated, at the bearing gaps of the bearing elements that are no longer under pressure in this case.
  • the small, precisely metered amounts of lubricating oil at the individual lubrication points largely prevent uncontrolled leakage of lubricating oil, so that maintenance and adjustment measures can be carried out at any time even with the engine running.
  • the valve control mechanism shown in the figures is used to actuate two exhaust valves 1 and 2 an internal combustion engine.
  • the two intake valves, not shown, of the internal combustion engine can be actuated by a valve control mechanism which is of the same or a similar design.
  • the valve control mechanism shown consists of two control levers 3 and 4, each of which has a bearing bore 5 with a fixed bearing bush 6 and is pivotably arranged on a bearing axis 7 by means of this.
  • the two bearing axles 7 are each fixed in place on a cylinder head of the internal combustion engine and there on bearing blocks, not shown.
  • the first control lever 3 has a bearing pin 8 with a curved bearing surface 9, spaced apart from the bearing axis 7 and with a curved bearing surface 9, on the outer shape of which a bearing shell 10 is adapted, which is arranged on the end of a push rod 11.
  • the latter cooperates with a camshaft, not shown, and can be deflected axially by a cam for pivoting the control lever 3.
  • a further bearing journal 12 is arranged on the first control lever 3, which is also fastened in a receiving bore spatially from the bearing axis 7, but at a distance from the bearing journal 8.
  • This journal 12 has a spherical bearing surface 13, on the outer shape of which a bearing shell of a spherical cap 14 cooperating is adapted, which cooperates with an end face 15 opposite the bearing shell with an end face on the valve lifter 16 of the exhaust valve 1 for actuating the same.
  • a third bearing pin 17 firmly inserted in a bore.
  • This third bearing pin 17 also has a spherical bearing surface 18 to which a bearing shell cooperating with it is adapted to a spherical cap 19. The latter is with one the bearing surface opposite sliding surface 20, mounted transversely on an associated sliding surface on the second control lever 4.
  • the bearing pin 17 and the spherical cap 19 are used to transmit motion from the first control lever 3 when the same is pivoted through the push rod 11 ′ to the second control lever 4, and consequently to pivot it synchronously about its bearing axis 7.
  • a bearing pin 21 is fastened in a bore in the second control lever 4 , which is substantially the same as the second bearing pin 12 on the first control lever 3 and has a spherical bearing surface 22, on the outer shape of which a bearing shell of a spherical cap 23 is adapted. The latter is pivotable about the ball pin and acts with an end face 24 opposite the bearing shell on an end face on the valve tappet 25 of the second exhaust valve 2 to actuate it.
  • the bearing elements on the respective control lever 3 or 4 and the surfaces of the bearing elements which transmit the force and movement to and from the respective control lever can be supplied with lubricating oil by the lubricating device according to the invention described below.
  • Each of the two bearing axles has a central inlet bore 26, which is connected on the input side to a lubricating oil supply (not shown), and an inlet duct 27 which branches off therefrom and leads radially to its circumferential surface.
  • the two oil distributor chambers 28, 29 are formed by a radial groove in the bearing bush 6, which is interrupted at two circumferential locations by webs 30 and 31, and on the outside in each case by the wall of the associated bearing bore 5 limited in the control lever 3 or 4.
  • At least one lubrication bore 32 leads from each upper oil distributor chamber 28 and at least one lubrication bore 33 leads from each lower oil distributor chamber 29 through the bearing bush 6 to the respective bearing axis 7; in addition, a passage bore 34 leads from the respective upper oil distributor chamber 28 and a passage bore 35 from the respective lower oil distributor chamber 29 through the bearing bush 6 to the respective bearing axis 7.
  • the two through bores 34 and 35 to the upper and lower oil distribution chambers 28 and 29 are now arranged in relation to the inlet channel 27 in the bearing axis 7 in such a way that the lower oil distribution chamber 29 and thus its lubricating holes 33 leading away in each position of the control lever 3 and 4 is connected via the through bore 35 to the inlet channel 27 in the respective bearing axis 7 and thus to the lubricating oil supply, while the upper oil distributor chamber 28 with the lubricating bores 32 and ⁇ lver leading away from it divider bores 36 only in that position of the control levers 3 and 4 with open valves 1 and 2 - corresponding to FIG.
  • the resulting output force of the penetrating lubricating oil is superimposed on the weight of the respective control lever 3 or 4, if, as in the present case, the output force of the incoming lubricating oil is approximately ten times the weight, this force is capable of a pumping movement of the control lever.
  • the lower oil distribution chamber 29 thus represents an oil source for supplying oil to the bearing between the bearing shaft and the bearing bush.
  • the oil source becomes an oil sink, since this is between the bearing shaft and the bearing bush located oil can only be pushed through the lubrication holes 33 into the lower oil distribution chamber 29.
  • divider chamber increases logarithmically and quickly reaches very high values, which means that a non-return valve is provided. This ensures a secure load-bearing capacity of the bearing for the respective control lever.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

1. Valve control mechanism for inlet- or exhaust valves (1, 2) of internal combustion engines with at least one control lever (3, 4) which has a bearing bore (5) with a fixedly inserted bearing bushing (6) and is disposed pivotably over this on a bearing axis (7), which has an inlet bore (26) connected to a lubricating oil supply and at least one inlet duct (27) branching off from this, which duct is connected via throughflow apertures (34, 35) of the bearing bushing (6) and an annular oil distribution duct consisting of two separate chambers to several oil distribution bores (36) branching from this and leading to different lubricating positions and opening into the latter with outlet apertures, which lubricating positions are located on mutually co-operating surfaces (9, 10, 13, 18, 20, 22) of the bearing elements (8, 11, 12, 14, 17, 19, 21, 23) transmitting the force and the movement to and from the control lever (3, 4), characterised in that the annular oil distribution duct is divided into an upper oil distribution chamber (28), from which branch the oil distribution bores (36) leading to the lubricating positions, and a lower oil distribution chamber (29) spatially separated from this, from which at least one lubricating bore (32, 33), and a throughflow aperture (34, 35), passes respectively through the bearing bushing (6) to the bearing axis (7), in such a way that the upper oil distribution chamber (28) is connected to the lubricating oil supply only in the position of the control lever (3, 4) when the valves (1, 2) are open, and consequently with closed outlet apertures at the lubricating positions, and the lower oil distribution chamber (29) on the other hand is always connected via the supply duct (27) of the bearing axis (7) to the lubricating oil supply.

Description

Die Erfindung betrifft einen Ventilsteuermechanismus für Ein- bzw. Auslaßventile von Brennkraftmaschinen mit Merkmalen entsprechend dem Oberbegriff des Anspruchs 1.The invention relates to a valve control mechanism for intake and exhaust valves of internal combustion engines with features according to the preamble of claim 1.

Ein derartiger Ventilsteuermechanismus ist durch die US-PS 3 021 826 bekannt. Bei dieser bekannten Lösung wird den Lagerstellen am Steuerhebel zwar auch nur in einer bestimmten Stellung desselben Schmieröl zugeführt. Das zugeführte Schmieröl kann während der Schmierphase an den Lagerstellen jedoch mehr oder minder stark gedrosselt aus den Lagerspalten austreten, so daß größere ölverluste am Ort der Schmierung und außerdem eine relativ große Verschmutzung im Zylinderkopfdeckel auftritt. Darüber hinaus sind Wartungs- und Einstellmaßnahmen bei laufendem Motor infolge des austretenden und unkontrolliert umherspritzenden Schmieröles praktisch nicht bzw. nur unter Inkaufnahme dieses Umstandes durchführbar. Darüber hinaus ist bei dieser bekannten Lösung auch keine befriedigende Schmierung am Ort der Betätigung der Ventilstößel erzielbar, da für die Schmierung dieser Betätigungsflächen praktisch nur das am Lager des Ventilbetätigungselementes austretende und außen am Betätigungskörper in unkontrollierter Weise ablaufende Lecköl verwendet wird. Es ist zu bezweifeln, ob diese Zufallschmierung den Anforderungen hinsichtlich Langlebigkeit eines derartigen Ventilsteuermechanismus gerecht wird.Such a valve control mechanism is known from US Pat. No. 3,021,826. In this known solution, the bearings on the control lever are supplied with the same lubricating oil only in a certain position. The lubricating oil supplied can emerge from the bearing gaps at the bearing points more or less throttled during the lubrication phase, so that greater oil losses occur at the location of the lubrication and also a relatively large amount of contamination in the cylinder head cover. In addition, maintenance and adjustment measures while the engine is running are practically impossible or can only be carried out with this circumstance due to the escaping and uncontrolled lubricating oil. In addition, no satisfactory lubrication can be achieved at the location of the actuation of the valve tappet in this known solution, since for the lubrication of these actuating surfaces practically only that on the bearing of the Valve actuating element leaking and leakage oil is used outside of the actuating body in an uncontrolled manner. It is doubtful whether this random lubrication will meet the durability requirements of such a valve timing mechanism.

Es ist demgegenüber Aufgabe der Erfindung, einen Ventilsteuermechanismus zu schaffen, bei dem die sich an den miteinander zusammenwirkenden Flächen der die Kraft und Bewegung zum und vom Steuerhebel übertragenden Lagerelemente befindlichen Schmierstellen taktweise in Abhängigkeit von der Steuerhebelbewegung mit exakt dosierten Schmierölmengen versorgbar sind. Diese Aufgabe ist erfindungsgemäß durch einen Ventilsteuermechanismus entsprechend den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Ausgestaltungen desselben sind in den Unteransprüchen gekennzeichnet.In contrast, it is an object of the invention to provide a valve control mechanism in which the lubricating points located on the interacting surfaces of the lubricating points which transmit the force and movement to and from the control lever can be supplied intermittently as a function of the control lever movement with precisely metered amounts of lubricating oil. This object is achieved according to the invention by a valve control mechanism according to the features of claim 1. Advantageous refinements of the same are characterized in the subclaims.

Durch die erfindungsgemäße Aufteilung des ringförmigen ölverteilerkanales in eine obere Ölverteilerkammer und eine untere Ölverteilerkammer sowie Ankoppelung der zu den einzelnen Schmierstellen führenden ölverteilerbohrungen an die obere ölverteilerkammer ist gewährleistet, daß letztere nur in einer Stellung des Steuerhebels bei geöffneten Ventilen an die Schmierölversorgung angeschlossen und mit Schmieröl auffüllbar sind. In dieser Stellung des Steuerhebels kann'das in die ölverteilerbohrungen eingespeiste Schmieröl jedoch nicht an den Schmierstellen austreten, da die miteinander zusammenwirkenden Flächen der die Kraft und Bewegung zum und vom Steuerhebel übertragenden Lagerelemente unter Verschließung der Schmierölaustrittsöffnungen infolge des Gegendruckes der geöffneten Ventile sowie der nockenbetätigten Schubstange und unter einer wesentlich über dem Schmieröldruck liegenden Pressung satt aneinander anliegen. Die in den ölverteilerbohrungen befindliche Schmierölmenge kann erst in der Stellung des Steuerhebels, nämlich bei geschlossenen Ventilen und nicht betätigter Schubstange an den Lagerspalten der in diesem Falle nicht mehr druckbelasteten Lagerelemente aus den nun offenen ölverteilerbohrungen austreten. Hierdurch ist gewährleistet, daß jeder Schmierstelle nur eine exakt dosierte Schmierölmenge zuführbar und daher gegenüber bekannten Ventilsteuermechanismen eine erhebliche Schmierölverbrauchsreduzierung erzielbar ist. Außerdem ist durch die geringen, exakt dosierten Schmierölmengen an den einzelnen Schmierstellen ein unkontrolliertes Austreten von Schmieröl weitgehend verhindert, so daß Wartungs- und Einstellmaßnahmen jederzeit auch bei laufendem Motor durchführbar sind.The inventive division of the annular oil distributor channel into an upper oil distributor chamber and a lower oil distributor chamber and coupling of the oil distributor bores leading to the individual lubrication points to the upper oil distributor chamber ensures that the latter is connected to the lubricating oil supply only in one position of the control lever when the valves are open and can be filled with lubricating oil are. In this position of the control lever, however, the lubricating oil fed into the oil distribution bores cannot escape at the lubrication points, since the interacting surfaces of the bearing elements transmitting the force and movement to and from the control lever while closing the lubricating oil outlet openings due to the counterpressure of the opened valves and the cam-actuated push rod and under a we press well above the lubricating oil pressure. The amount of lubricating oil in the oil distributor bores can only emerge from the now open oil distributor bores when the control lever is in the position, namely when the valves are closed and the push rod is not actuated, at the bearing gaps of the bearing elements that are no longer under pressure in this case. This ensures that only a precisely metered amount of lubricating oil can be supplied to each lubrication point and therefore a significant reduction in lubricating oil consumption can be achieved compared to known valve control mechanisms. In addition, the small, precisely metered amounts of lubricating oil at the individual lubrication points largely prevent uncontrolled leakage of lubricating oil, so that maintenance and adjustment measures can be carried out at any time even with the engine running.

Nachstehend ist die Erfindung anhand eines in der Zeichnung dargestellten Ausführungsbeispiels näher beschrieben'. Es zeigen

  • Fig. 1 einen Querschnitt durch Teile eines Ventilsteuermechanismus bei geschlos-- senen Ventilen,
  • Fig. 2 die Teile des in Fig. 1 gezeigten Ventilsteuermechanismus in einer Stellung bei offenen Ventilen.
The invention is described in more detail below on the basis of an exemplary embodiment shown in the drawing. Show it
  • 1 shows a cross section through parts of a valve control mechanism with closed valves,
  • Fig. 2 shows the parts of the valve control mechanism shown in Fig. 1 in a position with the valves open.

Gleiche oder einander ähnliche Bauteile oder Teile hiervon sind in der Zeichnung mit gleichen Bezugszeichen versehen.The same or similar components or parts thereof are provided with the same reference numerals in the drawing.

Der in den Figuren gezeigte Ventilsteuermechanismus dient zu Betätigung von zwei Auslaßventilen 1 und 2 einer Brennkraftmaschine. Die beiden nicht dargestellten Einlaßventile der Brennkraftmaschine sind durch einen mit diesem baugleichen oder ähnlich ausgebildeten Ventilsteuermechanismus betätigbar. Der dargestellte Ventilsteuermechanismus besteht aus zwei Steuerhebeln 3 und 4, von denen jeder eine Lagerbohrung 5 mit fest eingesetzter Lagerbuchse 6 aufweist und mittels dieser schwenkbar auf einer Lagerachse 7 angeordnet ist. Die beiden Lagerachsen 7 sind jeweils ortsfest an einem Zylinderkopf der Brennkraftmaschine und dort an nicht dargestellten Lagerböcken befestigt. Der erste Steuerhebel 3 besitzt räumlich beabstandet von der Lagerachse 7 einen fest in einer Bohrung eingesetzten Lagerzapfen 8 mit gewölbter Lagerfläche 9, an deren Außenform eine Lagerschale 10 angepaßt ist, die stirnseitig an einer Schubstange 11 angeordnet ist. Letztere wirkt mit einer nicht dargestellten Nockenwelle zusammen und ist durch einen Nocken derselben axial zur Verschwenkung des Steuerhebels 3 auslenkbar. Darüber hinaus ist am ersten Steuerhebel--3 ein weiterer Lagerzapfen 12 angeordnet, der ebenfalls räumlich von der Lagerachse 7, dem Lagerzapfen 8 jedoch gegenüberliegend beabstandet,'in einer Aufnahmebohrung befestigt ist. Dieser Lagerzapfen 12 besitzt eine kugelförmige Lagerfläche 13, an deren Außenform eine mit dieser zusammenwirkende Lagerschale einer Kalotte 14 angepaßt ist, die mit einer der Lagerschale gegenüberliegenden Stirnfläche 15 mit einer Stirnfläche am Ventilstößel 16 des Auslaßventiles 1 zur Betätigung desselben zusammenwirkt. Neben dem zweiten Kugelzapfen . 12 ist in größerem Abstand von der Lagerachse 7 am Steuerhebel 3 noch ein dritter Lagerzapfen 17 in einer Bohrung fest eingesetzt. Dieser dritte Lagerzapfen 17 besitzt ebenfalls eine kugelförmige Lagerfläche 18, an die eine mit ihr zusammenwirkende .Lagerschale einer Kalotte 19 angepaßt ist. Letztere ist mit einer der Lagerschale gegenüberliegenden Gleitfläche 20 , querbeweglich auf einer zugehörigen Gleitfläche am zweiten Steuerhebel 4 gelagert. Der Lagerzapfen 17 und die Kalotte 19 dienen zur Bewegungsübertragung vom ersten Steuerhebel 3 bei Verschwenkung desselben durch die Schubstange 11'auf den zweiten Steuerhebel 4, mithin zu dessen synchroner Verschwenkung um dessen Lagerachse 7. In einer Bohrung des zweiten Steuerhebels 4 ist ein Lagerzapfen 21 befestigt, der im wesentlichen gleich ausgebildet ist wie der zweite Lagerzapfen 12 am ersten Steuerhebel 3 und eine kugelförmige Lagerfläche 22 besitzt, an deren Außenform eine Lagerschale einer Kalotte 23 angepaßt ist. Letztere ist um den Kugelzapfen verschwenkbar und-wirkt mit einer der Lagerschale gegenüberliegenden Stirnfläche 24 auf eine Stirnfläche am Ventilstößel 25 des zweiten Auslaßventiles 2 zu dessen Betätigung ein.The valve control mechanism shown in the figures is used to actuate two exhaust valves 1 and 2 an internal combustion engine. The two intake valves, not shown, of the internal combustion engine can be actuated by a valve control mechanism which is of the same or a similar design. The valve control mechanism shown consists of two control levers 3 and 4, each of which has a bearing bore 5 with a fixed bearing bush 6 and is pivotably arranged on a bearing axis 7 by means of this. The two bearing axles 7 are each fixed in place on a cylinder head of the internal combustion engine and there on bearing blocks, not shown. The first control lever 3 has a bearing pin 8 with a curved bearing surface 9, spaced apart from the bearing axis 7 and with a curved bearing surface 9, on the outer shape of which a bearing shell 10 is adapted, which is arranged on the end of a push rod 11. The latter cooperates with a camshaft, not shown, and can be deflected axially by a cam for pivoting the control lever 3. In addition, a further bearing journal 12 is arranged on the first control lever 3, which is also fastened in a receiving bore spatially from the bearing axis 7, but at a distance from the bearing journal 8. This journal 12 has a spherical bearing surface 13, on the outer shape of which a bearing shell of a spherical cap 14 cooperating is adapted, which cooperates with an end face 15 opposite the bearing shell with an end face on the valve lifter 16 of the exhaust valve 1 for actuating the same. Next to the second ball stud. 12 is at a greater distance from the bearing axis 7 on the control lever 3 still a third bearing pin 17 firmly inserted in a bore. This third bearing pin 17 also has a spherical bearing surface 18 to which a bearing shell cooperating with it is adapted to a spherical cap 19. The latter is with one the bearing surface opposite sliding surface 20, mounted transversely on an associated sliding surface on the second control lever 4. The bearing pin 17 and the spherical cap 19 are used to transmit motion from the first control lever 3 when the same is pivoted through the push rod 11 ′ to the second control lever 4, and consequently to pivot it synchronously about its bearing axis 7. A bearing pin 21 is fastened in a bore in the second control lever 4 , which is substantially the same as the second bearing pin 12 on the first control lever 3 and has a spherical bearing surface 22, on the outer shape of which a bearing shell of a spherical cap 23 is adapted. The latter is pivotable about the ball pin and acts with an end face 24 opposite the bearing shell on an end face on the valve tappet 25 of the second exhaust valve 2 to actuate it.

Die Lagerelemente am jeweiligen Steuerhebel 3 bzw. 4 sowie die Flächen der die Kraft und Bewegung zum und vom jeweiligen Steuerhebel übertragenden Lagerelemente sind durch die nachfolgend beschriebene erfindungsgemäße Schmiereinrichtung mit Schmieröl versorgbar. Jede der beiden Lagerachsen besitzt eine zentrale, eingangsseitig an eine nicht dargestellte Schmierölversorgung angeschlossene Zulaufbohrung 26 und einen hiervon abzweigenden, radial zu ihrer Umfangsfläche führenden Zulaufkanal 27. Darüber hinaus ist in jedem der beiden Steuerhebel 3 und-4 ein ringförmiger ölverteilerkanal in eine.obere ölverteilerkammer 28 sowie eine räumlich von dieser getrennte untere ölverteilerkammer 29 aufgeteilt. Die beiden ölverteilerkammern 28, 29 sind beim gezeigten Ausführungsbeispiel durch eine an zwei Umfangsstellen durch Stege 30 und 31 unterbrochene Radialnut in der Lagerbuchse 6 gebildet und außen jeweils durch die Wand der zugehörigen Lagerbohrung 5 im Steuerhebel 3 bzw. 4 begrenzt. Von jeder oberen ölverteilerkammer 28 führt jeweils wenigstens eine Schmierbohrung 32 und von jeder unteren ölverteilerkammer 29 jeweils wenigstens eine Schmierbohrung 33 durch die Lagerbuchse 6 zur jeweiligen Lagerachse 7; außerdem führt von der jeweiligen oberen ölverteilerkammer 28 eine Durchlaßbohrung 34 sowie von der jeweiligen unteren ölverteilerkammer 29 eine Durchlaßbohrung 35 durch die Lagerbuchse 6 zur jeweiligen Lagerachse 7. Darüber hinaus führen jeweils nur von der oberen ölverteilerkammer 28 abzweigende ölverteilerbohrungen 36 durch den Steuerhebel und die daran angeordneten Lagerzapfen und münden mit ihren Austrittsöffnungen an den verschiedenen Schmierstellen ein, die sich an den vorstehend beschriebenen, miteinander zusammenwirkenden Flächen der die Kraft und Bewegung zum und vom Steuerhebel 1 bzw. 2 übertragenden Lagerelemente befinden. Um einen Schmieröldurchtritt von den Lagerschalen der drei Kalotten 14, 19 und 23 zu den Schmierstellen an deren gegeüberliegenden Stirnflächen 15, 20 und 24 sowie an den Stirnflächen der beiden zu betätigenden Ventilstößel 16, 25 und der Gleitfläche am zweiten Steuerhebel 4 zu ermöglichen, ist in jeder Kalotte 14, 19 und 23 eine Durchlaßbohrung 37 eingeformt.The bearing elements on the respective control lever 3 or 4 and the surfaces of the bearing elements which transmit the force and movement to and from the respective control lever can be supplied with lubricating oil by the lubricating device according to the invention described below. Each of the two bearing axles has a central inlet bore 26, which is connected on the input side to a lubricating oil supply (not shown), and an inlet duct 27 which branches off therefrom and leads radially to its circumferential surface. In addition, in each of the two control levers 3 and -4 there is an annular oil distributor duct in an upper oil distributor chamber 28 and a spatially separate lower oil distribution chamber 29. In the exemplary embodiment shown, the two oil distributor chambers 28, 29 are formed by a radial groove in the bearing bush 6, which is interrupted at two circumferential locations by webs 30 and 31, and on the outside in each case by the wall of the associated bearing bore 5 limited in the control lever 3 or 4. At least one lubrication bore 32 leads from each upper oil distributor chamber 28 and at least one lubrication bore 33 leads from each lower oil distributor chamber 29 through the bearing bush 6 to the respective bearing axis 7; in addition, a passage bore 34 leads from the respective upper oil distributor chamber 28 and a passage bore 35 from the respective lower oil distributor chamber 29 through the bearing bush 6 to the respective bearing axis 7. In addition, only oil distributor holes 36 branching off from the upper oil distributor chamber 28 lead through the control lever and the arranged thereon Journal and open with their outlet openings at the various lubrication points, which are located on the above-described, interacting surfaces of the force and movement to and from the control lever 1 and 2 transmitting bearing elements. In order to enable lubricating oil to pass from the bearing shells of the three spherical caps 14, 19 and 23 to the lubrication points on their opposite end faces 15, 20 and 24 and on the end faces of the two valve lifters 16, 25 to be actuated and the sliding surface on the second control lever 4, in each dome 14, 19 and 23 a through hole 37 is formed.

Die beiden Durchlaßbohrungen 34 und 35 zur oberen bzw. unteren ölverteilerkammer 28 bzw. 29-sind nun derart in Bezug auf den Zulaufkanal 27 in der Lagerachse 7 angeordnet, daß die untere ölverteilerkammer 29 und damit deren wegführende Schmierbohrungen 33 in jeder Stellung der Steuerhebel 3 bzw. 4 über die Durchlaßbohrung 35 an den Zulaufkanal 27 in der jeweiligen Lagerachse 7 und damit an die Schmierölversorgung angeschlossen ist, während die obere ölverteilerkammer 28 mit den von ihr wegführenden Schmierbohrungen 32 und ölverteilerbohrungen 36 nur in jener Stellung der Stellhebel 3 bzw. 4 bei offenen Ventilen 1 und 2 - entsprechend Fig. 2 - über die Durchlaßbohrung 34 an den Zulaufkanal 27 in der jeweiligen Lagerachse 7 und damit an die Schmierölversorgung angeschlossen sind. Wie aus Fig. 2 ersichtlich, sind in geöffneter Stellung der Ventile 1 und 2 die Austrittsöffnungen der ölverteilerbohrungen 36 an den Schmierstellen durch die dort infolge der Krafteinwirkung der Schubstange 12 sowie der beiden Ventilstößel 16 und 25 an den miteinander gepaarten Lagerflächen herrschenden Flächenpressungen verschlossen, so daß kein Schmieröl an die betreffenden Schmierstellen austreten kann und die ölverteilerbohrungen 36 sowie die Durchlaßbohrungen 37 in den drei Kalotten 14, 19 und 23 in dieser Phase nur mit Drucköl aufgefüllt werden. Außerdem werden in dieser Phase über die von der oberen ölverteilerkammer 28 wegführenden Schmierbohrungen 32 die miteinander gepaarten Lagerflächen an der Lagerbuchse 6 und der zugehörigen Lagerachse 7 mit Drucköl versorgt.The two through bores 34 and 35 to the upper and lower oil distribution chambers 28 and 29 are now arranged in relation to the inlet channel 27 in the bearing axis 7 in such a way that the lower oil distribution chamber 29 and thus its lubricating holes 33 leading away in each position of the control lever 3 and 4 is connected via the through bore 35 to the inlet channel 27 in the respective bearing axis 7 and thus to the lubricating oil supply, while the upper oil distributor chamber 28 with the lubricating bores 32 and Ölver leading away from it divider bores 36 only in that position of the control levers 3 and 4 with open valves 1 and 2 - corresponding to FIG. 2 - via the passage bore 34 to the inlet channel 27 in the respective bearing axis 7 and thus to the lubricating oil supply. As can be seen from FIG. 2, in the open position of the valves 1 and 2, the outlet openings of the oil distributor bores 36 at the lubrication points are closed by the surface pressures prevailing there due to the force of the push rod 12 and the two valve tappets 16 and 25 on the paired bearing surfaces, so that no lubricating oil can escape to the relevant lubrication points and the oil distributor bores 36 and the through bores 37 in the three spherical caps 14, 19 and 23 are only filled with pressure oil in this phase. In addition, in this phase, the paired bearing surfaces on the bearing bush 6 and the associated bearing axis 7 are supplied with pressure oil via the lubricating bores 32 leading away from the upper oil distributor chamber 28.

Nach dem Schließen der Ventile, mithin nach einem Übergang der Teile des Ventilsteuermechanismus von einer Stellung gemäß Fig. 2 nach einer Stellung gemäß Fig. 1, sind die besagten Flächenpressungen an den miteinander zusammenwirkenden Lagerteilen wegen des in Fig. 1 mit S bezeichneten Ventilspieles nicht mehr vorhanden, so daß sich das in den ölverteilerbohrungen 36 sowie den Durchlaßbohrungen37 der Kalotten 14, 19, 23 gespeicherte Schmieröl infolge der in dieser Phase wieder von der Schmierölversorgung abgetrennten Durchlaßbohrung 34 entspannt. Diese Entspannung ist mit einer kleinen Volumenausdehnung des aufgespeicherten Schmieröles verbunden, die bewirkt, daß geringe ölmengen, die einerseits zur Schmierung ausreichen, andererseits aber kein Spritzen verursachen, an den einzelnen Schmierstellen austreten und sich in die Spiel-Spalte S zwischen den Flächen der miteinander gepaarten Lagerelemente verteilen. In der in Fig. 1 gezeigten Stellung der Teile des Ventilsteuermechanismus ist nur die untere ölverteilerkammer 29 über die Durchlaßbohrung 35 an die ölversorgung angeschlossen, so daß in dieser Phase Schmieröl über die abzweigenden Schmierbohrungen 33 an die miteinander gepaarten Flächen der Lagerbuchse 6 und der Lagerachse 7 gelangt. Die resultierende Abtriebskraft des eindringenden Schmieröles überlagert sich dabei der Gewichtskraft des jeweiligen Steuerhebels 3 bzw. 4, wenn, wie im vorliegenden Falle, die Abtriebskraft des eintretenden Schmieröles etwa zehnmal so groß ist wie die Gewichtskraft, so ist diese Kraft in der Lage, eine Pumpbewegung des Steuerhebels anzuregen. Die untere ölverteilerkammer 29 stellt in dieser Phase demnach eine ölquelle zur ölversorgung des Lagers zwischen Lagerwelle und Lagerbuchse dar. Bei Umschlagen der Lagerbelastung - im vorliegenden Falle bei öffnen der Ventile 1 und 2 - wird aus der ölquelle eine ölsenke, da das zwischen Lagerwelle und Lagerbuchse befindliche öl nur durch die Schmierbohrungen 33 in die untere ölverteilerkammer 29 abgedrängt werden kann. Der Druck beim Zurückdrängen des Schmieröles in die Ölver- . teilerkammer steigt logarithmisch an und erreicht rasch sehr hohe Werte, wodurch eine Rückstromsperre gegeben ist. Hierdurch ist eine gesicherte Tragfähigkeit des Lagers für den jeweiligen Steuerhebel gewährleistet.After closing the valves, and thus after a transition of the parts of the valve control mechanism from a position according to FIG. 2 to a position according to FIG. 1, said surface pressures on the interacting bearing parts are no longer due to the valve clearance denoted by S in FIG. 1 available, so that the lubricating oil stored in the oil distributor bores 36 and the through bores 37 of the spherical caps 14, 19, 23 relaxes as a result of the through bore 34 separated again from the lubricating oil supply in this phase. This relaxation is associated with a small volume expansion of the stored lubricating oil, which has the effect that small amounts of oil, which on the one hand are sufficient for lubrication but on the other hand do not cause splashing, at the individual lubrication points emerge and spread in the game column S between the surfaces of the paired bearing elements. In the position of the parts of the valve control mechanism shown in FIG. 1, only the lower oil distribution chamber 29 is connected to the oil supply via the passage bore 35, so that in this phase lubricating oil via the branching lubrication bores 33 to the paired surfaces of the bearing bush 6 and the bearing axis 7 reached. The resulting output force of the penetrating lubricating oil is superimposed on the weight of the respective control lever 3 or 4, if, as in the present case, the output force of the incoming lubricating oil is approximately ten times the weight, this force is capable of a pumping movement of the control lever. In this phase, the lower oil distribution chamber 29 thus represents an oil source for supplying oil to the bearing between the bearing shaft and the bearing bush. When the bearing load changes - in the present case when the valves 1 and 2 are opened - the oil source becomes an oil sink, since this is between the bearing shaft and the bearing bush located oil can only be pushed through the lubrication holes 33 into the lower oil distribution chamber 29. The pressure when the lubricating oil is pushed back into the oil reservoir. divider chamber increases logarithmically and quickly reaches very high values, which means that a non-return valve is provided. This ensures a secure load-bearing capacity of the bearing for the respective control lever.

Der. vorstehend beschriebene Schmierzyklus wiederholt sich bei jedem öffnen bzw. Schließen der Ventile.The. The lubrication cycle described above is repeated each time the valves are opened or closed.

Claims (5)

1. Ventilsteuermechanismus für Ein- bzw. Auslaßventile von Brennkraftmaschinen mit wenigstens einem Steuerhebel, der eine Lagerbohrung mit fest eingesetzter Lagerbuchse aufweist und über diese schwenkbar auf einer Lagerachse angeordnet ist, die eine an eine Schmierölversorgung angeschlossene Zulaufbohrung und wenigstens einen hiervon abzweigenden Zulaufkanal besitzt, der über Durchlaßbohrungen der Lagerbuchse und einen ringförmigen ölverteilerkanal an mehrere von diesem abzweigende, zu verschiedenen Schmierstellen führende und in letztere mit Austrittsöffnungen einmündende ölverteilerbohrungen angeschlossen ist, welche Schmierstellen sich an miteinander zusammenwirkenden Flächen der die Kraft und Bewegung zum und vom Steuerhebel übertragenden Lagerelemente befinden, dadurch gekennzeichnet, daß der ringförmige ölverteilerkanal in eine obere ölverteilerkammer (28), von der die zu den Schmierstellen führenden ölverteilerbohrungen (36) abzweigen, und eine räumlich von dieser getrennte untere ölverteilerkammer (29). aufgeteilt ist, von denen durch die Lagerbuchse (6) jeweils wenigstens eine Schmierbohrung (32, 33) sowie eine Durchlaßbohrung (34, 35) zur Lagerachse (7) wegführt, derart, daß die obere Ölverteilerkammer (28) nur in der Stellung des Steuerhebels (3', 4) bei offenen Ventilen (1, 2), mithin bei verschlossenen Austrittsöffnungen an den Schmierstellen, die untere ölverteilerkammer (29) hingegen ständig über den Zulaufkanal (27) der Lagerachse (7) an die Schmierölversorgung angeschlossen ist.1.Valve control mechanism for intake and exhaust valves of internal combustion engines with at least one control lever which has a bearing bore with a fixed bearing bush and is pivotably arranged over this on a bearing axis which has an inlet bore connected to a lubricating oil supply and at least one inlet duct branching therefrom, which Via through bores of the bearing bush and an annular oil distributor channel to several oil distributor bores which branch off from it and lead to different lubrication points and which open into the latter with outlet openings, which lubrication points are located on interacting surfaces of the bearing elements transmitting the force and movement to and from the control lever, characterized in that in that the annular oil distribution passage into an upper oil distribution crest e r (28) of the branch leading to the lubrication points oil distribution holes (36) and a spatially separate from this un tere oil distribution chamber (29). is divided, of which at least one lubrication bore (32, 33) and one passage bore (34, 35) lead away to the bearing axis (7) through the bearing bush (6), such that the upper oil distributor chamber (28) only in the position of the control lever (3 ', 4) with open valves (1, 2), thus with closed outlet openings at the lubrication points, the lower oil distribution chamber (29), on the other hand, is constantly connected to the lubricating oil supply via the inlet channel (27) of the bearing axis (7). 2. Ventilsteuermechanismus nach Anspruch 1, dadurch gekennzeichnet, daß die beiden Ölverteilerkammern (28, 29) durch eine, an zwei Umfangsstellen durch Stege (30,31) unterbrochene Radialnut in der Lagerbuchse (6) gebildet und außen durch die Wand der Lagerbohrung (5) im Steuerhebel (3, 4) begrenzt sind.2. Valve control mechanism according to claim 1, characterized in that the two oil distribution chambers (28, 29) by a, at two circumferential locations by webs (30,31) interrupted radial groove in the bearing bush (6) and outside through the wall of the bearing bore (5th ) in the control lever (3, 4) are limited. 3. Ventilsteuermechanismus nach Anspruch 1, dadurch gekennzeichnet, daß die zu schmierenden, Kraft und Bewegung zum und vom Steuerhebel (3, 4) übertragenden Flächen (9, 13, 22) an wenigstens einem Lagerzapfen (8, 12, 17, 21) und einem mit diesem zusammenwirkenden Kraft- und Bewegungsübertragungselement .(11, 14, 16, 19, 23, 25) zur Ventilbetätigung angeordnet sind.3. Valve control mechanism according to claim 1, characterized in that the to be lubricated, force and movement to and from the control lever (3, 4) transmitting surfaces (9, 13, 22) on at least one bearing pin (8, 12, 17, 21) and a force and movement transmission element (11, 14, 16, 19, 23, 25) cooperating with this are arranged for valve actuation. 4. Ventilsteuermechanismus nach Anspruch 3, dadurch gekennzeichnet, daß bei Verwendung zweier auf je einer Lagerachse (7) angeordneter, getrieblich aneinander gekoppelter Steuerhebel (3, 4) ein erster Lagerzapfen (8) am ersten Steuerhebel (3) lagerseitig gepaart ist mit einer Lagerschale (10) an einer nockenbetätigten Schubstange (11), je ein Lagerzapfen (12, 21) am ersten und zweiten Steuerhebel (3,bzw. 4) lagerseitig gepaart ist mit einer Lagerschale einer mit einer weiteren zu schmierenden Stirnfläche (15, 24) auf einen Ventilstößel (16, 25) einwirkenden Kalotte (14, 23), ein weiterer Lagerzapfen (17) am ersten Steuerhebel (3) gepaart ist mit einer Lagerschale einer am zweiten Steuerhebel (4) beweglich angeordneten Kalotte (19), und daß die Gleitflächen (9, 13, 18) der drei Lagerzapfen (8, 12, 17) am ersten Steuerhebel (3) sowie deren zugehörige Lagerschalen über ölverteilerbohrungen (36) im ersten Steuerhebel (3) sowie die Gleitfläche (22) am Lagerzapfen (21) des zweiten Steuerhebels (4) und dessen zugehörige Lagerschale über ölverteilerbohrungen (36) im zweiten Steuerhebel (4) mit Schmieröl versorgbar sind.4. Valve control mechanism according to claim 3, characterized in that when using two on a bearing axis (7) arranged, geared to each other control lever (3, 4) a first bearing pin (8) on the first control lever (3) is paired on the bearing side with a bearing shell (10) on a cam - actuated push rod (11), a bearing pin (12, 21) on the first and second control lever (3 or 4) is paired on the bearing side with a bearing shell with an end face (15, 24) to be lubricated a valve tappet (16, 25) acting dome (14, 23), a further bearing journal (17) on the first control lever (3) is paired with a bearing shell of a dome (19) movably arranged on the second control lever (4), and that the sliding surfaces (9, 13, 18) of the three bearing journals (8, 12, 17) on the first control lever (3) and their associated bearing shells Lubricating oil can be supplied via oil distributor bores (36) in the first control lever (3) and the sliding surface (22) on the bearing journal (21) of the second control lever (4) and its associated bearing shell via oil distributor bores (36) in the second control lever (4). 5. Ventilsteuermechanismus nach einem oder mehreren der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Lagerschale und die dieser gegenüberliegende Stirnfläche (15, 20, 24) der jeweiligen Kalotte (14, 19, 23) durch eine öldurchlaßbohrung (37) miteinander verbunden sind, die nur in der Stellung des Steuerhebels (3, 4) bei offenen Ventilen (1, 2) an die durch den zugehörigen Lagerzapfen (12, 17, 21) führende Ölverteilerbohrung (36) angeschlossen mit Schmieröl füllbar ist und diese raummäßig begrenzte ölmenge in der Stellung des Steuerhebels (3, 4) bei geschlossenen Ventilen (1, 2) in den Ventilspiel-Spalt (S) zwischen die Stirnfläche (15, 24) an der jeweiligen Kalotte (14, 19, 23) und Stirnfläche am Ventilstößel (16, 25) bzw. Gleitfläche am zweiten Steuerhebel (4) abgibt.5. Valve control mechanism according to one or more of the preceding claims, characterized in that the bearing shell and the end face (15, 20, 24) of the respective calotte (14, 19, 23) opposite this are connected to one another by an oil passage bore (37) can only be filled with lubricating oil in the position of the control lever (3, 4) with open valves (1, 2) connected to the oil distributor bore (36) leading through the associated bearing journal (12, 17, 21) and this limited amount of oil in the position the control lever (3, 4) with closed valves (1, 2) into the valve clearance gap (S) between the end face (15, 24) on the respective calotte (14, 19, 23) and end face on the valve tappet (16, 25 ) or sliding surface on the second control lever (4).
EP80103049A 1979-07-26 1980-05-31 Actuating mechanism for inlet or exhaust valves of internal-combustion engines Expired EP0023250B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19792930337 DE2930337A1 (en) 1979-07-26 1979-07-26 VALVE CONTROL MECHANISM FOR ONE OR EXHAUST VALVES FROM INTERNAL COMBUSTION ENGINES
DE2930337 1979-07-26

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EP0023250A1 true EP0023250A1 (en) 1981-02-04
EP0023250B1 EP0023250B1 (en) 1983-06-01

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EP (1) EP0023250B1 (en)
JP (1) JPS5620710A (en)
DD (1) DD152165A1 (en)
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DK (1) DK318480A (en)

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US4896635A (en) * 1988-12-27 1990-01-30 Ford Motor Company Friction reducing rocker arm construction
WO1999028602A1 (en) * 1997-11-26 1999-06-10 Volkswagen Aktiengesellschaft Cylinder head for an internal combustion engine with a pump-jet unit
WO2000040840A1 (en) * 1999-01-05 2000-07-13 Marimuthu Ramu Thiyagarajan A low cost new internal combustion engine with increased mechanical efficiency, fuel saver and pollution controlled
US6177112B1 (en) 1998-05-08 2001-01-23 Nestec S.A. Composite pastry and ice confectionery article and preparation thereof
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EP2090757A2 (en) * 2008-02-14 2009-08-19 MAN Nutzfahrzeuge Aktiengesellschaft Tilt lever assembly with a bearing with slots
CN111102028A (en) * 2019-12-20 2020-05-05 潍柴动力股份有限公司 Rocker arm assembly, valve distribution structure and engine
CN113039349A (en) * 2018-09-17 2021-06-25 乌伟·艾森拜斯 Variable valve mechanism with lubricant supply system
CN114183217A (en) * 2021-10-29 2022-03-15 东风商用车有限公司 Cast iron rocker arm structure

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Publication number Priority date Publication date Assignee Title
US4644914A (en) * 1984-08-29 1987-02-24 Toyota Jidosha Kabushiki Kaisha Valve mechanism of internal combustion engine
US4896635A (en) * 1988-12-27 1990-01-30 Ford Motor Company Friction reducing rocker arm construction
DE4235103B4 (en) * 1991-10-29 2005-02-03 Volkswagen Ag Camshaft valve control for an internal combustion engine with two rows of cylinders
WO1999028602A1 (en) * 1997-11-26 1999-06-10 Volkswagen Aktiengesellschaft Cylinder head for an internal combustion engine with a pump-jet unit
US6177112B1 (en) 1998-05-08 2001-01-23 Nestec S.A. Composite pastry and ice confectionery article and preparation thereof
WO2000040840A1 (en) * 1999-01-05 2000-07-13 Marimuthu Ramu Thiyagarajan A low cost new internal combustion engine with increased mechanical efficiency, fuel saver and pollution controlled
EP2090757A2 (en) * 2008-02-14 2009-08-19 MAN Nutzfahrzeuge Aktiengesellschaft Tilt lever assembly with a bearing with slots
EP2090757A3 (en) * 2008-02-14 2009-09-16 MAN Nutzfahrzeuge Aktiengesellschaft Tilt lever assembly with a bearing with slots
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CN101509401B (en) * 2008-02-14 2012-09-05 曼卡车和巴士股份公司 Tilt lever assembly with a bearing with slots
CN113039349A (en) * 2018-09-17 2021-06-25 乌伟·艾森拜斯 Variable valve mechanism with lubricant supply system
CN113039349B (en) * 2018-09-17 2023-06-27 乌伟·艾森拜斯 Variable valve train with lubricant supply system
CN111102028A (en) * 2019-12-20 2020-05-05 潍柴动力股份有限公司 Rocker arm assembly, valve distribution structure and engine
CN114183217A (en) * 2021-10-29 2022-03-15 东风商用车有限公司 Cast iron rocker arm structure

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Publication number Publication date
JPS6364602B2 (en) 1988-12-13
JPS5620710A (en) 1981-02-26
DE3063592D1 (en) 1983-07-07
DE2930337A1 (en) 1981-02-19
DD152165A1 (en) 1981-11-18
DK318480A (en) 1981-01-27
EP0023250B1 (en) 1983-06-01

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