EP0245614B1 - Poppet valve control device for a reciprocating piston internal-combustion engine - Google Patents

Poppet valve control device for a reciprocating piston internal-combustion engine Download PDF

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Publication number
EP0245614B1
EP0245614B1 EP87103881A EP87103881A EP0245614B1 EP 0245614 B1 EP0245614 B1 EP 0245614B1 EP 87103881 A EP87103881 A EP 87103881A EP 87103881 A EP87103881 A EP 87103881A EP 0245614 B1 EP0245614 B1 EP 0245614B1
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EP
European Patent Office
Prior art keywords
valve
poppet valve
armature
bearing
damping
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
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EP87103881A
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German (de)
French (fr)
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EP0245614A1 (en
Inventor
Hans Dipl.-Ing. Mezger
Hans-Joachim Dr. Dipl. Ing. Esch
Reinhard Könneker
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Dr Ing HCF Porsche AG
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Dr Ing HCF Porsche AG
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Classifications

    • 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • 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
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L1/462—Valve return spring arrangements
    • 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2105—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids comprising two or more coils
    • F01L2009/2109—The armature being articulated perpendicularly to the coils axes

Definitions

  • the invention relates to a device for actuating a gas exchange valve designed as a poppet valve of a reciprocating piston internal combustion engine according to the preamble of claim 1.
  • Such a valve actuation device is known from EP-PS 0 118 591.
  • Two electromagnets which are excited out of phase with each other, form an oscillation system with two coil springs, which rest on both sides of an armature disk attracted by the electromagnets.
  • the poppet valve connected to the armature disk is moved back and forth and thereby opens or closes a fluid passage opening.
  • a tight closing of the poppet valve should also be ensured if the end positions of the two stroke movements have tolerances caused by the production.
  • the characterizing features of claim 1 serve to solve this problem.
  • the torsion bar spring used for valve actuation does not have any oscillating masses which negatively influence the oscillating system. Even the rocker arm rigidly connected to the torsion bar spring, which is in operative connection with the poppet valve, has only a very small reduced mass, so that the armature articulated on the valve lever follows the alternating excitations of the electromagnets almost without inertia and can control the poppet valve accordingly.
  • a similar torsion bar spring is known from DE-AS 1 120 804 for a purely mechanical valve control actuated by a cam.
  • the use of a torsion bar spring for an electromagnetic valve control has the decisive advantage that it becomes functional in the first place by eliminating the translationally moved spring masses and correspondingly reducing the inertial forces and can be operated with a still reasonable amount of energy for the power supply of the electromagnets.
  • a resilient tolerance compensation is achieved in that the free end of the valve lever rests on a sliding sleeve which is longitudinally guided on the valve stem and is arranged at a short distance from a holding sleeve.
  • the torsion bar spring is rotatably connected at one end to the valve lever and is mounted in two bearing blocks arranged on both sides of the valve lever; at the other end, the torsion bar is clamped in a rotationally fixed manner in a holding bush screwed to the cylinder head.
  • the armature which is mounted longitudinally movably in the center of the two electromagnets, is articulated on the valve lever in such a way that its distance from the longitudinal axis of the poppet valve is considerably smaller than its distance from the longitudinal axis of the torsion bar or the center of the bearing of the valve lever. In this way, an adapted path translation can be achieved, from the valve stroke of the poppet valve, which is optimized from a thermodynamic point of view, to the stroke movement of the armature which is useful for commercially available electromagnets.
  • a hydraulic damping device is installed in the cylinder head above the valve stem.
  • damping discs are located in an oil-filled, cylindrical damping space.
  • a magnet housing 2 is fixed to the cylinder head 1 of a reciprocating piston internal combustion engine, in which a first electromagnet 3 and a second electromagnet 4 are fixedly attached at a distance a1 from one another.
  • an armature disk 6 which is fastened to an armature 5 and which is drawn towards the respectively excited electromagnet 3 or 4.
  • the armature is mounted at its free end in a bearing 7 of the magnet housing 2.
  • the other end of the armature 5 is screwed into a rod head 8 which is articulated with a pin 9 to a fork 10 of a one-armed valve lever 11; the just milled rod head 8 lies with lateral play between the fork 10.
  • the front end of the fork 10 engages between a thrust washer 13 resting on a shoulder of the valve stem 12 and a sliding sleeve 14 which is longitudinally movable on the valve stem 12 and is compensate by a helical spring 15 against a holding sleeve 16 fastened to the valve stem 12 is supported.
  • a small distance b is provided between the sliding sleeve 14 and the holding sleeve 16 in order to enable a resilient tolerance compensation between the armature stroke a2 and the valve stroke s of the poppet valve 17.
  • a damping sleeve 18 is fastened which, when the poppet valve 17 is closed, penetrates into the oil-filled damping cylinder 19 formed in the cylinder head, in which a plurality of damping disks 20 lie.
  • the end is designed as a bearing tube 25 with two radially projecting collars.
  • the bearing tube 25 is mounted on both sides in a bearing block 27 or 28 screwed to the cylinder head 1; the collars 26 lying on the end faces of the bearing blocks 27, 28 secure the bearing tube 25 against axial displacement.
  • one end of a cylindrical torsion bar spring 29 is fastened in the bearing tube 25 with a serration connection 30.
  • the other end of the torsion bar spring 29 is also non-rotatably connected with a serration connection 30 in a holding bush 31 which is provided with elongated holes 32 and is flanged to the cylinder head 1.
  • the distance c1 of the articulation point of the armature 5 on the valve lever to the longitudinal axis of the poppet valve 17 is smaller than the distance c2 to the center of the bearing of the valve lever 17 in order to be able to translate away from the armature stroke a2 to the valve stroke s.
  • the electromagnet 3 is energized.
  • the electromagnet 3 is de-energized and at the same time the electromagnet 4 is energized, but because of the large distance a2 it cannot exert any noticeable force on the armature disk.
  • the initial movement to open the poppet valve is effected by the tensioned torsion bar 29, which is only relaxed on half of the armature stroke. From here, the armature disk 6 is applied to the electromagnet 4 by the strongly progressively increasing magnetic force of the electromagnet 4 and the inertia force of the valve mechanism, the poppet valve 17 going into the open position and the torsion bar spring 29 being tensioned again, this time in the other direction of rotation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Magnetically Actuated Valves (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Description

Die Erfindung betrifft eine Vorrichtung zum Betätigen eines als Tellerventil ausgebildeten Gaswechselventils einer Hubkolben-Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a device for actuating a gas exchange valve designed as a poppet valve of a reciprocating piston internal combustion engine according to the preamble of claim 1.

Eine derartige Ventilbetätigungsvorrichtung ist aus EP-PS 0 118 591 bekannt. Zwei phasenverschoben zueinander erregte Elektromagnete bilden mit zwei Schraubenfedern, die beidseits an einer durch die Elektromagnete angezogenen Ankerscheibe anliegen, ein Schwingsystem. Im Rhythmus dieser Schwingung wird das mit der Ankerscheibe verbundene Tellerventil hin- und herbewegt und öffnet bzw. schließt dabei eine Fluid-Durchtrittsöffnung. Wenn eine solche Vorrichtung zum Betätigen eines Gaswechsel-Tellerventils einer Hubkolben-Brennkraftmaschine verwendet wird, ist es wichtig, die Masse des Federsystems möglichst klein zu halten, um einerseits eine präzise Steuerung über den ganzen Drehzahlbereich der Brennkraftmaschine zu erhalten und andererseits den Energiebedarf für die Elektromagnete auf eine minimale Größe zu beschränken. Außerdem soll auch dann ein dichtes Schließen des Tellerventils sichergestellt werden, wenn die Endlagen der beiden Hubbewegungen durch die Fertigung bedingte Toleranzen aufweisen.Such a valve actuation device is known from EP-PS 0 118 591. Two electromagnets, which are excited out of phase with each other, form an oscillation system with two coil springs, which rest on both sides of an armature disk attracted by the electromagnets. In the rhythm of this vibration, the poppet valve connected to the armature disk is moved back and forth and thereby opens or closes a fluid passage opening. If such a device is used to actuate a gas exchange poppet valve of a reciprocating piston internal combustion engine, it is important to keep the mass of the spring system as small as possible in order to obtain precise control over the entire speed range of the internal combustion engine on the one hand and the energy requirement for the electromagnets on the other hand to be kept to a minimum size. In addition, a tight closing of the poppet valve should also be ensured if the end positions of the two stroke movements have tolerances caused by the production.

Es ist die Aufgabe der Erfindung, eine Ventilbetätigung mit möglichst geringen bewegten Federmassen zu schaffen und ein dichtes Schließen des Tellerventils durch eine elastisch nachgiebige Verbindung zwischen dem freien Ende des Ventilhebels und dem Schaft des Tellerventils sicherzustellen.It is the object of the invention to create a valve actuation with the smallest possible moving spring masses and to ensure tight closing of the poppet valve by means of an elastically flexible connection between the free end of the valve lever and the stem of the poppet valve.

Zur Lösung dieser Aufgabe dienen die kennzeichnenden Merkmale des Anspruchs 1. Die zur Ventilbetätigung verwendete Drehstabfeder besitzt keine, das Schwingsystem negativ beeinflussende, oszillierende Massen. Auch der mit der Drehstabfeder starr verbundene, in Wirkverbindung mit dem Tellerventil stehende Schlepphebel hat nur eine sehr geringe reduzierte Masse, so daß der am Ventilhebel angelenkte Anker nahezu trägheitslos den wechselweisen Erregungen der Elektromagnete folgen und das Tellerventil entsprechend steuern kann.The characterizing features of claim 1 serve to solve this problem. The torsion bar spring used for valve actuation does not have any oscillating masses which negatively influence the oscillating system. Even the rocker arm rigidly connected to the torsion bar spring, which is in operative connection with the poppet valve, has only a very small reduced mass, so that the armature articulated on the valve lever follows the alternating excitations of the electromagnets almost without inertia and can control the poppet valve accordingly.

Eine ähnliche Drehstabfeder ist zwar aus DE-AS 1 120 804 bekannt für eine rein mechanische, durch einen Nocken betätigte Ventilsteuerung. Jedoch bringt die Anwendung einer Drehstabfeder für eine elektromagnetische Ventilsteuerung den entscheidenden Vorteil, daß sie durch Wegfall der translatorisch bewegten Federmassen und entsprechende Reduzierung der Massenkräfte überhaupt erst richtig funktionsfähig wird und mit einem noch vertretbaren Energieaufwand für die Stromversorgung der Elektromagnete betrieben werden kann.A similar torsion bar spring is known from DE-AS 1 120 804 for a purely mechanical valve control actuated by a cam. However, the use of a torsion bar spring for an electromagnetic valve control has the decisive advantage that it becomes functional in the first place by eliminating the translationally moved spring masses and correspondingly reducing the inertial forces and can be operated with a still reasonable amount of energy for the power supply of the electromagnets.

Ein federnder Toleranzausgleich ist erreicht, indem das freie Ende des Ventilhebels an einer auf dem Ventilschaft längsgeführten federnd und mit geringem Abstand zu einer Haltehülse angeordneten Schiebehülse anliegt.A resilient tolerance compensation is achieved in that the free end of the valve lever rests on a sliding sleeve which is longitudinally guided on the valve stem and is arranged at a short distance from a holding sleeve.

In vorteilhafter Ausgestaltung der Erfindung ist die Drehstabfeder an ihrem einen Ende drehfest mit dem Ventilhebel verbunden und in zwei, zu beiden Seiten des Ventilhebels angeordneten Lagerböcken gelagert; am anderen Ende ist der Drehstab in einer mit dem Zylinderkopf verschraubten Haltebuchse drehfest eingespannt. Der zentrisch zu den beiden Elektromagneten längsbeweglich gelagerte Anker ist an dem Ventilhebel so angelenkt, daß sein Abstand zur Längsachse des Tellerventils erheblich kleiner ist als sein Abstand zur Längsachse des Drehstabes bzw. der Lagermitte des Ventilhebel. Auf diese Weise läßt sich eine angepaßte Wegübersetzung erzielen, von dem nach thermodynamischen Gesichtspunkten optimierten Ventilhub des Tellerventils zu der für handelsübliche Elektromagnete sinnvollen Hubbewegung des Ankers.In an advantageous embodiment of the invention, the torsion bar spring is rotatably connected at one end to the valve lever and is mounted in two bearing blocks arranged on both sides of the valve lever; at the other end, the torsion bar is clamped in a rotationally fixed manner in a holding bush screwed to the cylinder head. The armature, which is mounted longitudinally movably in the center of the two electromagnets, is articulated on the valve lever in such a way that its distance from the longitudinal axis of the poppet valve is considerably smaller than its distance from the longitudinal axis of the torsion bar or the center of the bearing of the valve lever. In this way, an adapted path translation can be achieved, from the valve stroke of the poppet valve, which is optimized from a thermodynamic point of view, to the stroke movement of the armature which is useful for commercially available electromagnets.

Um beim Schließen des Tellerventils den Aufprall des Ventiltellers am Ventilsitz zu dämpfen, ist oberhalb des Ventilschaftes im Zylinderkopf eine hydraulische Dämpfungsvorrichtung angebracht. Mehrere Dämpfungsscheiben liegen in einem ölgefüllten zylindrischen Dämpfungsraum. Wenn die am oberen Ende des Ventilschaftes befestigte Dämpfungshülse in den Dämpfungsraum eindringt, wird das zwischen den Dämpfungsscheiben befindliche Öl durch definierte Drosselspalte hindurch verdrängt und bewirkt so ein sanfteres, geräuscharmeres Aufsetzen des Ventiltellers auf den Ventilsitz.In order to dampen the impact of the valve disc on the valve seat when the poppet valve closes, a hydraulic damping device is installed in the cylinder head above the valve stem. Several damping discs are located in an oil-filled, cylindrical damping space. When the damping sleeve attached to the upper end of the valve stem penetrates into the damping space, the oil between the damping disks is displaced through defined throttle gaps, resulting in a gentler, quieter installation of the valve plate on the valve seat.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend erläutert.An embodiment of the invention is shown in the drawing and is explained below.

Es zeigtIt shows

  • Fig. 1 Frontansicht der erfindungsgemäßen Ventilsteuerung mit Längsschnitt durch das Tellerventil,1 front view of the valve control according to the invention with a longitudinal section through the poppet valve,
  • Fig. 2 Seitenansicht der Ventilsteuerung mit Längsschnitt durch die Lagerung der Drehstabfeder,2 side view of the valve control with longitudinal section through the bearing of the torsion bar,
  • Fig. 3 Draufsicht auf die Ventilsteuerung.Fig. 3 top view of the valve control.

Am Zylinderkopf 1 einer Hubkolben-Brennkraftmaschine ist ein Magnetgehäuse 2 befestigt, in dem mit Abstand a1 zueinander ein erster Elektromagnet 3 und ein zweiter Elektromagnet 4 fest angebracht sind. In dem Freiraum zwischen den Elektromagneten 3 und 4 liegt eine an einem Anker 5 befestigte Ankerscheibe 6, die zu dem jeweils erregten Elektromagnet 3 oder 4 hingezogen wird. Der Anker ist an seinem freien Ende in einem Lager 7 des Magnetgehäuses 2 gelagert. Das andere Ende des Ankers 5 ist in einen Stangenkopf 8 geschraubt, der mit einem Stift 9 an eine Gabel 10 eines einarmigen Ventilhebels 11 angelenkt ist; der eben abgefräste Stangenkopf 8 liegt dabei mit seitlichem Spiel zwischen der Gabel 10.A magnet housing 2 is fixed to the cylinder head 1 of a reciprocating piston internal combustion engine, in which a first electromagnet 3 and a second electromagnet 4 are fixedly attached at a distance a1 from one another. In the space between the electromagnets 3 and 4 there is an armature disk 6 which is fastened to an armature 5 and which is drawn towards the respectively excited electromagnet 3 or 4. The armature is mounted at its free end in a bearing 7 of the magnet housing 2. The other end of the armature 5 is screwed into a rod head 8 which is articulated with a pin 9 to a fork 10 of a one-armed valve lever 11; the just milled rod head 8 lies with lateral play between the fork 10.

Das vordere Ende der Gabel 10 greift zwischen eine, auf einem Absatz des Ventilschaftes 12 aufliegende Druckscheibe 13 und eine auf dem Ventilschaft 12 längsbewegliche Schiebehülse 14 ein, die durch eine Schraubenfeder 15 gegen eine am Ventilschaft 12 befestigte Haltehülse 16 abgestützt ist. Zwischen der Schiebehülse 14 und der Haltehülse 16 ist ein geringer Abstand b vorgesehen, um einen federnden Toleranzausgleich zwischen dem Ankerhub a2 und dem Ventilhub s des Tellerventils 17 zu ermöglichen. Am oberen Ende des Ventilschaftes 12 ist eine Dämpfungshülse 18 befestigt, die beim Schließen des Tellerventils 17 in den im Zylinderkopf ausgebildeten, ölgefüllten Dämpfungszylinder 19 eindringt, in dem mehrere Dämpfungsscheiben 20 liegen.The front end of the fork 10 engages between a thrust washer 13 resting on a shoulder of the valve stem 12 and a sliding sleeve 14 which is longitudinally movable on the valve stem 12 and is abge by a helical spring 15 against a holding sleeve 16 fastened to the valve stem 12 is supported. A small distance b is provided between the sliding sleeve 14 and the holding sleeve 16 in order to enable a resilient tolerance compensation between the armature stroke a2 and the valve stroke s of the poppet valve 17. At the upper end of the valve stem 12, a damping sleeve 18 is fastened which, when the poppet valve 17 is closed, penetrates into the oil-filled damping cylinder 19 formed in the cylinder head, in which a plurality of damping disks 20 lie.

Dabei verdrängt sie das Öl in die Ölzulaufbohrung 21 sowie in die Drosselspalte 22. Mit dieser Dämpfungsvorrichtung ist eine Geräuschminderung des Ventiltriebes und eine Verringerung des Verschleißes am Ventilteller 23 und Sitzring 24 erreicht. Die Höhe der Dämpfung läßt sich durch den ÖI-Zulaufdruck und die Bemessung der Drosselspalte einstellen.In doing so, it displaces the oil into the oil inlet bore 21 and into the throttle gap 22. With this damping device, the valve train is reduced in noise and the wear on the valve plate 23 and seat ring 24 is reduced. The amount of damping can be adjusted by the oil inlet pressure and the dimensioning of the throttle gap.

Wichtig für eine präzise Ventilsteuerung ist eine gute Lagerung des Ventilhebels 11. Hierzu ist der endseitig als Lagerrohr 25 mit zwei radial vorstehenden Bunden ausgebildet. Das Lagerrohr 25 ist an beiden Seiten in einem am Zylinderkopf 1 angeschraubten Lagerbock 27 bzw. 28 gelagert; die stirnseitig an den Lagerböcken 27, 28 anliegenden Bunde 26 sichern das Lagerrohr 25 gegen Axialverschiebung.Good positioning of the valve lever 11 is important for precise valve control. For this purpose, the end is designed as a bearing tube 25 with two radially projecting collars. The bearing tube 25 is mounted on both sides in a bearing block 27 or 28 screwed to the cylinder head 1; the collars 26 lying on the end faces of the bearing blocks 27, 28 secure the bearing tube 25 against axial displacement.

Im Bereich des einen Lagerbockes 27 ist in dem Lagerrohr 25 das eine Ende einer zylindrischen Drehstabfeder 29 mit einer Kerbzahnverbindung 30 befestigt. Das andere Ende der Drehstabfeder 29 ist ebenfalls mit einer Kerbzahnverbindung 30 in einer Haltebuchse 31 drehfest, die mit Langlöchern 32 versehen ist und an den Zylinderkopf 1 angeflanscht ist. Der Abstand c1 der Anlenkstelle des Ankers 5 am Ventilhebel zur Längsachse des Tellerventils 17 ist kleiner als der Abstand c2 zur Lagermitte des Ventilhebels 17, um eine Wegübersetzung vom Ankerhub a2 zum Ventilhub s realisieren zu können. In der gezeichneten Schließlage des Tellerventils 17 ist der Elektromagnet 3 erregt. Er zieht die Ankerscheibe 6 an und hält die Drehstabfeder gespannt. Zum Öffnen des Tellerventils 17 wird der Elektromagnet 3 entregt und gleichzeitig der Elektromagnet 4 erregt, der aber wegen des großen Abstandes a2 noch keine merkliche Kraft auf die Ankerscheibe ausüben kann. Die Anfangsbewegung zum Öffnen des Tellerventils wird bewirkt durch die gespannte Drehstabfeder 29, die erst auf der Hälfte des Ankerhubs entspannt ist. Ab hier wird die Ankerscheibe 6 durch die stark progressiv ansteigende Magnetkraft des Elektromagnets 4 sowie die Trägheitskraft des Ventilmechanismus an den Elektromagnet 4 angelegt, wobei das Tellerventil 17 in Offenstellung geht und die Drehstabfeder 29 wieder, diesmal in der anderen Drehrichtung gespannt wird.In the area of the bearing block 27, one end of a cylindrical torsion bar spring 29 is fastened in the bearing tube 25 with a serration connection 30. The other end of the torsion bar spring 29 is also non-rotatably connected with a serration connection 30 in a holding bush 31 which is provided with elongated holes 32 and is flanged to the cylinder head 1. The distance c1 of the articulation point of the armature 5 on the valve lever to the longitudinal axis of the poppet valve 17 is smaller than the distance c2 to the center of the bearing of the valve lever 17 in order to be able to translate away from the armature stroke a2 to the valve stroke s. In the drawn closed position of the poppet valve 17, the electromagnet 3 is energized. He pulls the armature plate 6 and keeps the torsion bar under tension. To open the poppet valve 17, the electromagnet 3 is de-energized and at the same time the electromagnet 4 is energized, but because of the large distance a2 it cannot exert any noticeable force on the armature disk. The initial movement to open the poppet valve is effected by the tensioned torsion bar 29, which is only relaxed on half of the armature stroke. From here, the armature disk 6 is applied to the electromagnet 4 by the strongly progressively increasing magnetic force of the electromagnet 4 and the inertia force of the valve mechanism, the poppet valve 17 going into the open position and the torsion bar spring 29 being tensioned again, this time in the other direction of rotation.

Beim Schließen des Tellerventils 17 wiederholt sich der eben beschriebene Vorgang in der umgekehrten Reihenfolge. Die Verstellkraft wird hierbei auf das Tellerventil über die Schiebehülse und Schraubenfeder aufgebracht. Die federnde Betätigung sorgt für eine gleichzeitige Anlage der Ankerscheibe am Elektromagnet und des Ventiltellers am Sitzring, auch dann, wenn fertigungsbedingte oder temperaturbedingte Toleranzabweichungen des Abstandes a2 oder des Ventilhubes s auftreten.When closing the poppet valve 17, the process just described is repeated in the reverse order. The adjusting force is applied to the poppet valve via the sliding sleeve and coil spring. The resilient actuation ensures that the armature disc rests on the electromagnet and the valve disk on the seat ring at the same time, even if manufacturing-related or temperature-related tolerance deviations of the distance a2 or the valve stroke s occur.

Claims (10)

1. A device for actuating a gas-reversing poppet valve (17) guided longitudinally in the cylinder head (1) of a reciprocating-piston internal combustion engine, having two electromagnets (3, 4) alternately periodically energized and reciprocating an armature (5) against the force of a spring (29), the said armature (5) opening and closing the poppet valve (17), characterized in that the spring is in the form of a torsion-bar spring (29), held rotationally rigidly at one end on the cylinder head (1) and connected rotationally rigidly at its other end to a one-armed valve lever (11) in the bearing area thereof, the valve lever (11) being articulated on the armature (5) and engaging with its free end (10) on the valve shaft (12) of the poppet valve (17), and the free end of the valve lever (11) resting in the closing direction of the poppet valve (17) on a sliding sleeve (14) guided longitudinally on the valve shaft (12) and supported by means of a helical spring (15) on a holding sleeve (16) secured to the valve shaft (12), the sliding sleeve (14) and the holding sleeve (16) being at a short distance (b) from each other.
2. A device according to Claim 1, characterized in that the distance (c1) of the articulation point (pin 9) of the armature (5) from the longitudinal axis of the poppet valve (17) is less than the distance (c2) to the centre of the bearing of the valve lever (11
3. A device according to Claim 1, characterized in that the valve lever (11) is formed at its free end as a fork (10) extending slightly beyond the articulation point (pin 9).
4. A device according to any one of Claims 1 to 3, characterized in that the closing movement of the poppet valve (17) is damped by a hydraulic damping device (18, 19, 20, 21, 22).
5. A device according to Claim 4, characterized in that the damping device comprises a damping sleeve (18) secured at one end to the valve shaft (12), an oil-filled damping cylinder (19) provided with damping discs (20) and an oil-supply bore (21) and throttle gaps (22).
6. A device according to any one of Claims 1 to 3, characterized in that the valve lever (11) is constructed at one end as a bearing tube (25) mounted at its two ends in bearing blocks (27,28).
7. A device according to Claim 6, characterized in that the torsion-bar spring (29) projects with one end through the bearing tube (25) and is connected rotationally rigidly to the bearing tube (25) in the region of one bearing block (28).
8. A device according to Claims 1 and 7, characterized in that the torsion-bar spring (29) is clamped with its other end rotationally rigidly in a holding bush (31) flange-mounted on the cylinder head (1).
9. A device according to Claim 8, characterized in that the rotational position of the holding bush (31) can be set by pivoting in longitudinal holes (32).
10. A device according to any one of Claims 1 to 9, characterized in that it is constructed for actuating two poppet valves simultaneously.
EP87103881A 1986-05-16 1987-03-17 Poppet valve control device for a reciprocating piston internal-combustion engine Expired - Lifetime EP0245614B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863616540 DE3616540A1 (en) 1986-05-16 1986-05-16 DEVICE FOR ACTUATING A GAS EXCHANGE VALVE OF A PISTON PISTON COMBUSTION ENGINE
DE3616540 1986-05-16

Publications (2)

Publication Number Publication Date
EP0245614A1 EP0245614A1 (en) 1987-11-19
EP0245614B1 true EP0245614B1 (en) 1990-09-26

Family

ID=6300980

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87103881A Expired - Lifetime EP0245614B1 (en) 1986-05-16 1987-03-17 Poppet valve control device for a reciprocating piston internal-combustion engine

Country Status (5)

Country Link
US (1) US4762095A (en)
EP (1) EP0245614B1 (en)
JP (1) JPS62271915A (en)
DE (2) DE3616540A1 (en)
ES (1) ES2018491B3 (en)

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Also Published As

Publication number Publication date
ES2018491B3 (en) 1991-04-16
JPS62271915A (en) 1987-11-26
DE3765167D1 (en) 1990-10-31
DE3616540C2 (en) 1989-11-30
DE3616540A1 (en) 1987-11-19
EP0245614A1 (en) 1987-11-19
US4762095A (en) 1988-08-09

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