EP1087109A2 - Valve drive for internal combustion engine - Google Patents

Valve drive for internal combustion engine Download PDF

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Publication number
EP1087109A2
EP1087109A2 EP00120615A EP00120615A EP1087109A2 EP 1087109 A2 EP1087109 A2 EP 1087109A2 EP 00120615 A EP00120615 A EP 00120615A EP 00120615 A EP00120615 A EP 00120615A EP 1087109 A2 EP1087109 A2 EP 1087109A2
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EP
European Patent Office
Prior art keywords
valve
piston
main piston
intermediate piston
throttle bore
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EP00120615A
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German (de)
French (fr)
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EP1087109A3 (en
EP1087109B1 (en
Inventor
Diethard Plohberger
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Innio Jenbacher GmbH and Co OG
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Jenbacher AG
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Priority to AT00120615T priority Critical patent/ATE249574T1/en
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    • 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
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic

Definitions

  • the present invention relates to a valve drive for a valve Internal combustion engine, the valve being arranged in a cylinder space Main piston is connected to open the valve with in the cylinder chamber inflowing pressure fluid can be acted upon and wherein a closing spring is provided which acts on the valve in the closing direction.
  • the object of the invention is therefore to provide a valve drive that is simpler can be produced and is essentially independent of the state of wear of the valve.
  • a throttle is provided via which throttled out part of the pressure fluid during the closing movement of the valve flows out of the cylinder space.
  • the throttle reduces the speed of the valve approaching the valve seat in such a way that it gently "
  • a compression spring is arranged to the cylinder space between the main piston and the intermediate piston in each Cycle with a sufficient amount of pressurized fluid for damping preferably provided that between the main piston and the intermediate piston . Because of the spring against the main and the Presses intermediate piston, pressure fluid is released into the spring when the spring is released Vacuumed in between.
  • the intermediate piston faces the pressure oil line Side has a preferably cone-shaped stop.
  • attack forms on the side of the intermediate piston facing the pressure oil line Cavity that ensures that the pressure oil regardless of the location of the Throttle bore can flow in and out freely via the pressure oil line.
  • the size of the throttle bore has a major influence on the damping. Proven if the diameter of the throttle bore is less than 10%, is preferably about 5 to 7% of the diameter of the intermediate piston.
  • FIGS. 1 to 3 the one according to the invention Show valve drive in different positions during a cycle.
  • the valve train consists of a poppet valve V in a known manner Closing spring S and a hydraulic main piston HK. This causes Supply of the cylinder chamber Z with pressure oil through the cross section D an opening of the Valve. When the oil pressure is cut off, valve V closes and the oil is excluded displaced the cylinder space Z.
  • the advantage of the arrangement according to the invention is that the damping path ⁇ s regardless of the distance s between the main piston HK and the intermediate piston ZK is.
  • the distance s changes over time with increasing valve wear.
  • the damping path ⁇ s is only a function of time, the diameter d Throttle bore B, the spring force of the spring F and the oil viscosity.
  • the throttle bore B can be made very precisely.
  • the leakage between the main piston HK and the intermediate piston ZK on the one hand and the Cylinder housing G, on the other hand, can be completely avoided by conventional seals are, so that there are no tolerance-related deviations of the Give damping path between a number of valve drives of an engine can.
  • the system is still self-regulating in that it is cold oil and / or large Oil viscosity of the distance increase ⁇ s turns out to be lower than with warm oil and / or small oil viscosity.
  • the closing speed of the Valve V due to the higher wall friction of the oil in the lines and the Flow resistance through the throttle B larger, so that a smaller overall Damping path ⁇ s is sufficient or is desirable.

Abstract

The actuator has an auxiliary piston (ZK) and a main piston (HK) held apart by a spring (F). Pressurised oil gains access through a restrictor bore (B) in the auxiliary valve to the main piston to open the valve. On the closing stroke the oil is rapidly ejected through the feed pipe (L) until a stop (A) on the auxiliary valve reaches the cylinder and the main cylinder continues to move over the distance (As) forcing the oil at a slower rate through the restrictor

Description

Die vorliegende Erfindung betrifft einen Ventilantrieb für ein Ventil eines Verbrennungsmotors, wobei das Ventil mit einem in einem Zylinderraum angeordneten Hauptkolben verbunden ist, der zum Öffnen des Ventils mit in den Zylinderraum einströmendem Druckfluid beaufschlagbar ist und wobei eine Schließfeder vorgesehen ist, die das Ventil in Schließrichtung beaufschlagt.The present invention relates to a valve drive for a valve Internal combustion engine, the valve being arranged in a cylinder space Main piston is connected to open the valve with in the cylinder chamber inflowing pressure fluid can be acted upon and wherein a closing spring is provided which acts on the valve in the closing direction.

Bei hydraulischen Ventilantrieben ist es günstig, die Schließbewegung des Ventils vor dem Aufsetzen des Ventiltellers derart zu bremsen, daß die Aufsetzgeschwindigkeit des Ventils auf seinem Sitz nicht zu hoch wird. In diesem Fall würde übermäßiger Ventilverschleiß auftreten. Bei den bekannten Einrichtungen taucht kurz vor Erreichen der Schließstellung des Ventils ein Kolben in einen Zylinder mit definiertem, kleinem Durchmesserunterschied ein. Durch den engen Spalt zwischen Kolben und Zylinder fließt Öl mit großer Geschwindigkeit und Druckdifferenz aus dem Zylinder durch den engen Spalt, wodurch die Aufsetzbewegung des Ventils gedämpft wird. Dieses Prinzip wird im übrigen auch bei allen Arten von hydraulischen Stoßdämpfern als Endanschlagdämpfung eingesetzt.With hydraulic valve actuators, it is advantageous to pre-close the valve to brake the mounting of the valve plate in such a way that the mounting speed the valve on its seat does not become too high. In this case it would be excessive Valve wear occur. In the known facilities dives shortly before reaching the closed position of the valve a piston in a cylinder with a defined, small Difference in diameter. Due to the narrow gap between the piston and cylinder oil flows through the cylinder at high speed and pressure difference narrow gap, which dampens the touchdown movement of the valve. This principle is also used in all types of hydraulic shock absorbers End stop cushioning used.

Der Nachteil dieser Anordnung liegt darin, daß aus Gründen der Fertigungstoleranz ein relativ großer Prozentsatz des Ventilhubes für den Dämpfungsvorgang verwendet werden muß, um ausreichende Dämpfung zu bekommen. Weiterhin hängt die Stärke der Dämpfung und damit die Aufsetzgeschwindigkeit des Ventils auf seinem Sitz in hohem Maß von der Durchmessertoleranz des Dämpferkolbens und -zylinders und damit vom Spaltquerschnitt ab. Weiterhin muß der Dämpferweg so groß ausgelegt werden, daß sowohl im Neuzustand als auch bei verschlissenem Ventil und Ventilsitz ausreichende Dämpfung erzielt wird. Der Unterschied im Dämpferweg zwischen neuem und verschlissenem Ventil/Ventilsitz kann jedoch bei Großmotoren durchaus bis zu 5 mm betragen. Durch die Notwendigkeit einer Überdimensionierung des Dämpferweges entstehen mit zunehmendem Ventilverschleiß zunehmende Energieverluste durch zu starke Dämpfung. Weiters wird die Ventilbewegung in Sitznähe zunehmend langsamer, sodaß es zu einer unerwünschten Veränderung des Ventilschließzeitpunktes kommen kann. The disadvantage of this arrangement is that for reasons of manufacturing tolerance relatively large percentage of valve lift used for the damping process must be to get sufficient cushioning. The strength also depends the damping and thus the speed of the valve in its seat of the diameter tolerance of the damper piston and cylinder and thus from the gap cross-section. Furthermore, the damper path must be designed so large be that both when new and when the valve and valve seat are worn sufficient damping is achieved. The difference in damper travel between new and worn valve / valve seat can, however, with large engines up to 5 mm. Due to the need to oversize the Damper travel arise with increasing valve wear Energy loss due to excessive damping. Furthermore, the valve movement in Closer to the seat increasingly slowly, so that there is an undesirable change in the Valve closing time can come.

Aufgabe der Erfindung ist es daher einen Ventilantrieb zu schaffen, der einfacher herstellbar und vom Verschleißzustand des Ventils im wesentlichen unabhängig ist.The object of the invention is therefore to provide a valve drive that is simpler can be produced and is essentially independent of the state of wear of the valve.

Dies wird erfindungsgemäß dadurch erreicht, daß eine Drossel vorgesehen ist, über die ein Teil des Druckfluids während der Schließbewegung des Ventils gedrosselt aus dem Zylinderraum abfließt.This is achieved according to the invention in that a throttle is provided via which throttled out part of the pressure fluid during the closing movement of the valve flows out of the cylinder space.

Durch die Drossel wird die Geschwindigkeit des sich dem Ventilsitz nähernden Ventils derart reduziert, daß es

Figure 00020001
sanft" aufsetzt.The throttle reduces the speed of the valve approaching the valve seat in such a way that it
Figure 00020001
gently "

Konstruktiv besonders einfach ist es, wenn im Zylinderraum auf der vom Ventil abgewandten Seite des Hauptkolbens ein relativ zum Hauptkolben bewegbarer Zwischenkolben angeordnet ist, der mit einer Drosselbohrung versehen ist. Der Zwischenkolben unterteilt den Zylinderraum, sodaß ein Teil des Druckfluids durch die Drosselbohrung hindurch abfließen muß.It is structurally particularly simple if in the cylinder space on the valve opposite side of the main piston a movable relative to the main piston Intermediate piston is arranged, which is provided with a throttle bore. The Intermediate piston divides the cylinder space, so that part of the pressure fluid through the Throttle bore must flow through.

Um den Zylinderraum zwischen dem Hauptkolben und dem Zwischenkolben bei jedem Zyklus mit einer für die Dämpfung ausreichenden Menge an Druckfluid zu füllen, ist vorzugsweise vorgesehen, daß zwischen dem Hauptkolben und dem Zwischenkolben eine Druckfeder angeordnet ist. Aufgrund der Feder, die gegen den Haupt- und den Zwischenkolben drückt, wird beim Entspannen der Feder Druckfluid in den Zwischenraum gesaugt.To the cylinder space between the main piston and the intermediate piston in each Cycle with a sufficient amount of pressurized fluid for damping preferably provided that between the main piston and the intermediate piston a compression spring is arranged. Because of the spring against the main and the Presses intermediate piston, pressure fluid is released into the spring when the spring is released Vacuumed in between.

Günstig ist es, wenn der Zwischenkolben auf der der Druckölleitung zugewandten Seite einen vorzugsweise zapfenförmigen Anschlag aufweist. Durch den Anschlag bildet sich auf der der Druckölleitung zugewandten Seite des Zwischenkolbens ein Hohlraum, der sicherstellt, daß das Drucköl unabhängig von der Lage der Drosselbohrung ungehindert über die Druckölleitung zu- und abfließen kann.It is expedient if the intermediate piston faces the pressure oil line Side has a preferably cone-shaped stop. By the attack forms on the side of the intermediate piston facing the pressure oil line Cavity that ensures that the pressure oil regardless of the location of the Throttle bore can flow in and out freely via the pressure oil line.

Wesentlichen Einfluß auf die Dämpfung hat die Größe der Drosselbohrung. Bewährt hat es sich, wenn der Durchmesser der Drosselbohrung weniger als 10 %, vorzugsweise etwa 5 bis 7 % des Durchmessers des Zwischenkolbens beträgt. The size of the throttle bore has a major influence on the damping. Proven if the diameter of the throttle bore is less than 10%, is preferably about 5 to 7% of the diameter of the intermediate piston.

Weitere Merkmale und Einzelheiten der vorliegenden Erfindung ergeben sich aus der nachfolgenden Beschreibung der Fig. 1 bis 3, die einen erfindungsgemäßen Ventilantrieb in unterschiedlichen Positionen während eines Zyklus zeigen.Further features and details of the present invention result from the following description of FIGS. 1 to 3, the one according to the invention Show valve drive in different positions during a cycle.

Der Ventiltrieb besteht in bekannter Art und Weise aus einem Tellerventil V mit Schließfeder S und einem hydraulischen Hauptkolben HK. Dieser bewirkt bei Versorgung des Zylinderraumes Z mit Drucköl durch den Querschnitt D ein Öffnen des Ventils. Wenn der Öldruck abgesteuert wird, schließt das Ventil V und das Öl wird aus dem Zylinderraum Z verdrängt.The valve train consists of a poppet valve V in a known manner Closing spring S and a hydraulic main piston HK. This causes Supply of the cylinder chamber Z with pressure oil through the cross section D an opening of the Valve. When the oil pressure is cut off, valve V closes and the oil is excluded displaced the cylinder space Z.

Funktionsbeschreibung der Aufschlagdämpfung:

  • Fig. 1: Beim Öffnen des Ventils wirkt der Öldruck auf den Zwischenkolben ZK. Zwischen dem Zwischenkolben ZK und dem Hauptkolben HK befindet sich ebenfalls Öl, das den Druck auf den Hauptkolben HK überträgt. Durch die Feder F und die Drosselbohrung B im Zwischenkolben ZK vergrößert sich der Abstand zwischen Zwischenkolben ZK und Hauptkolben HK während des Öffnungshubes des Ventils V um den Differenzweg Δs. Die Feder F drückt dabei den Zwischenkolben ZK und den Hauptkolben HK auseinander, wobei Öl durch die Drosselbohrung B in Richtung Federraum der Feder F fließt.
  • Fig. 2: Beim Schließen des Ventils V beträgt zu einem bestimmten Zeitpunkt der restliche Öffnungshub des Ventils Δs. Ab diesem Zeitpunkt liegt der Zwischenkolben ZK mit seinem zapfenförmigen Anschlag A am Zylindergehäuse G an. Damit das Ventil V vollständig schließen kann, muß nunmehr der Abstand zwischen Hauptkolben HK und Zwischenkolben ZK von s+Δs auf ursprünglich s verringert werden. Dies geschieht dadurch, daß die Feder F zusammengedrückt wird und das Öl aus dem Raum zwischen dem Hauptkolben HK und dem Zwischenkolben ZK durch die Drosselbohrung B entweicht. Die Beschaffenheit der Drosselbohrung B bestimmt daher die Aufsetzgeschwindigkeit des Ventils auf seinem Sitz VS. Die Feder F hat dabei nur einen geringen Einfluß, da sie im Vergleich zur Schließfeder S des Ventils V schwach ist.
  • Fig. 3: Zeigt den Endzustand und gleichzeitig den Ausgangszustand des Ventilhubes.
    • Functional description of impact damping:
  • Fig. 1: When the valve is opened, the oil pressure acts on the intermediate piston ZK. There is also oil between the intermediate piston ZK and the main piston HK, which transfers the pressure to the main piston HK. The spring F and the throttle bore B in the intermediate piston ZK increase the distance between the intermediate piston ZK and the main piston HK during the opening stroke of the valve V by the differential path Δs. The spring F presses the intermediate piston ZK and the main piston HK apart, oil flowing through the throttle bore B in the direction of the spring chamber of the spring F.
  • Fig. 2: When the valve V closes at a certain point in time, the remaining opening stroke of the valve is Δs. From this point in time, the intermediate piston ZK abuts the cylinder housing G with its peg-shaped stop A. So that the valve V can close completely, the distance between the main piston HK and the intermediate piston ZK must now be reduced from s + Δs to originally s. This is done in that the spring F is compressed and the oil escapes from the space between the main piston HK and the intermediate piston ZK through the throttle bore B. The nature of the throttle bore B therefore determines the placement speed of the valve on its seat VS. The spring F has only a slight influence since it is weak compared to the closing spring S of the valve V.
  • Fig. 3: Shows the final state and at the same time the initial state of the valve stroke.

    • Der Vorteil der erfindungsgemäßen Anordnung liegt darin, daß der Dämpfungsweg Δs unabhängig vom Abstand s zwischen dem Hauptkolben HK und dem Zwischenkolben ZK ist. Der Abstand s ändert sich im Lauf der Zeit mit zunehmendem Ventilverschleiß. Der Dämpfungsweg Δs ist jedoch nur eine Funktion der Zeit, des Durchmessers d der Drosselbohrung B, der Federkraft der Feder F und der Ölviskosität.The advantage of the arrangement according to the invention is that the damping path Δs regardless of the distance s between the main piston HK and the intermediate piston ZK is. The distance s changes over time with increasing valve wear. The damping path Δs is only a function of time, the diameter d Throttle bore B, the spring force of the spring F and the oil viscosity.

    Die Drosselbohrung B kann sehr genau hergestellt werden. Die Leckage zwischen dem Hauptkolben HK und dem Zwischenkolben ZK einerseits und dem Zylindergehäuse G andererseits kann durch übliche Dichtungen völlig vermieden werden, sodaß es insgesamt keine toleranzbedingten Abweichungen des Dämpfungsweges zwischen einer Anzahl von Ventilantrieben eines Motors geben kann.The throttle bore B can be made very precisely. The leakage between the main piston HK and the intermediate piston ZK on the one hand and the Cylinder housing G, on the other hand, can be completely avoided by conventional seals are, so that there are no tolerance-related deviations of the Give damping path between a number of valve drives of an engine can.

    Das System ist weiterhin insofern selbstregulierend, als bei kaltem Öl und/oder großer Ölviskosität der Abstandszuwachs Δs geringer ausfällt als bei warmem Öl und/oder kleiner Ölviskosität. Im ersteren Fall ist jedoch auch die Schließgeschwindigkeit des Ventils V durch die höhere Wandreibung des Öls in den Leitungen sowie der Durchflußwiderstand durch die Drossel B größer, sodaß insgesamt ein kleinerer Dämpfungsweg Δs ausreicht bzw. erwünscht ist.The system is still self-regulating in that it is cold oil and / or large Oil viscosity of the distance increase Δs turns out to be lower than with warm oil and / or small oil viscosity. In the former case, however, the closing speed of the Valve V due to the higher wall friction of the oil in the lines and the Flow resistance through the throttle B larger, so that a smaller overall Damping path Δs is sufficient or is desirable.

    Als Alternative zum beschriebenen Ausführungsbeispiel ist es vorstellbar, die Drosselwirkung durch sehr schnell arbeitende Mehrwegventile zu erreichen.As an alternative to the described embodiment, it is conceivable that Achieve throttling effect through very fast working reusable valves.

    Claims (7)

    Ventilantrieb für ein Ventil eines Verbrennungsmotors, wobei das Ventil mit einem in einem Zylinderraum angeordneten Hauptkolben verbunden ist, der zum Öffnen des Ventils mit in den Zylinderraum einströmendem Druckfluid beaufschlagbar ist und wobei eine Schließfeder vorgesehen ist, die das Ventil in Schließrichtung beaufschlagt, dadurch gekennzeichnet, daß im Zylinderraum (Z) auf der vom Ventil (V) abgewandten Seite des Hauptkolbens (HK) ein relativ zum Hauptkolben (HK) bewegbarer Zwischenkolben (ZK) angeordnet ist, der mit mindestens einer Drosselbohrung (B) versehen ist und daß zwischen dem Hauptkolben (HK) und dem Zwischenkolben (ZK) eine Druckfeder (F) angeordnet ist, die den Hauptkolben (HK) und den Zwischenkolben (ZK) während des Öffnungshubes des Ventils um einen Betrag (AS) auseinander drückt, wobei Druckfluid über die Drosselbohrung(en) (B) in den Raum zwischen Hauptkolben (HK) und Zwischenkolben (ZK) strömt, und daß am Ende der Schließbewegung des Ventils Hauptkolben (HK) und Zwischenkolben (ZK) zusammengedrückt werden, wobei ein Teil des Druckfluids über die Drosselbohrung(en) gedrosselt aus dem Raum zwischen Hauptkolben (HK) und Zwischenkolben (ZK) ausströmt.Valve drive for a valve of an internal combustion engine, the valve having a Main piston arranged in a cylinder space is connected to open of the valve with pressurized fluid flowing into the cylinder chamber and wherein a closing spring is provided which the valve in the closing direction acted upon, characterized in that in the cylinder chamber (Z) on the valve (V) side of the main piston (HK) facing away from the main piston (HK) movable intermediate piston (ZK) is arranged with at least one Throttle bore (B) is provided and that between the main piston (HK) and the intermediate piston (ZK) a compression spring (F) is arranged, the main piston (HK) and the intermediate piston (ZK) during the opening stroke of the valve an amount (AS) apart, with pressure fluid over the Throttle bore (s) (B) in the space between the main piston (HK) and Intermediate piston (ZK) flows, and that at the end of the closing movement of the valve Main piston (HK) and intermediate piston (ZK) are pressed together, whereby a Part of the pressure fluid throttled out of the room via the throttle bore (s) flows out between the main piston (HK) and the intermediate piston (ZK). Ventilantrieb nach Anspruch 1, dadurch gekennzeichnet, daß der Zwischenkolben (ZK) auf der der Druckölleitung (L) zugewandten Seite einen vorzugsweise zapfenförmigen Anschlag (A) aufweist.Valve drive according to claim 1, characterized in that the intermediate piston (ZK) on the side facing the pressure oil line (L) preferably one has a peg-shaped stop (A). Ventilantrieb nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Durchmesser (d) der Drosselbohrung (B) weniger als 10 Prozent des Durchmessers des Zwischenkolbens (ZK) beträgt.Valve drive according to claim 1 or 2, characterized in that the Diameter (d) of the throttle bore (B) less than 10 percent of the Diameter of the intermediate piston (ZK). Ventilantrieb nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Durchmesser (d) der Drosselbohrung (B) etwa 5 bis 7 Prozent des Durchmessers des Zwischenkolbens (ZK) beträgt.Valve drive according to one of claims 1 to 3, characterized in that the Diameter (d) of the throttle bore (B) about 5 to 7 percent of the diameter of the intermediate piston (ZK). Ventilantrieb nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß der Hauptkolben (HK) und der Zwischenkolben (ZK) den gleichen Durchmesser aufweisen und gemeinsam im selben Zylinder beweglich geführt sind. Valve drive according to one of claims 1 to 4, characterized in that the Main piston (HK) and the intermediate piston (ZK) have the same diameter have and are movably guided together in the same cylinder. Ventilantrieb nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Hauptkolben (HK) auf der vom Ventil abgewandten Seite nur von der Druckfeder (F) und dem Druckfluid im Zwischenraum zwischen Hauptkolben (HK) und Zwischenkolben (ZK) druckbeaufschlagt istValve drive according to one of claims 1 to 5, characterized in that the Main piston (HK) on the side facing away from the valve only from the compression spring (F) and the pressure fluid in the space between the main piston (HK) and Intermediate piston (ZK) is pressurized Ventilantrieb nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Zwischenraum zwischen Hauptkolben (HK) und Zwischenkolben (ZK) nur über die Drosselbohrung(en) im Zwischenkolben mit einer zum Öffnen und Schließen des Ventils periodisch Druckfluid zu- und abführenden Druckölleitung (6) in Fluid-Verbindung steht.Valve drive according to one of claims 1 to 6, characterized in that the Gap between the main piston (HK) and the intermediate piston (ZK) only over the Throttle bore (s) in the intermediate piston with one for opening and closing the Valve periodically pressure fluid supply and discharge pressure oil line (6) in fluid communication stands.
    EP00120615A 1999-09-22 2000-09-21 Valve drive for internal combustion engine Expired - Lifetime EP1087109B1 (en)

    Priority Applications (1)

    Application Number Priority Date Filing Date Title
    AT00120615T ATE249574T1 (en) 1999-09-22 2000-09-21 VALVE DRIVE FOR A VALVE OF AN INTERNAL COMBUSTION ENGINE

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    AT0161799A AT410696B (en) 1999-09-22 1999-09-22 VALVE DRIVE FOR A VALVE OF A COMBUSTION ENGINE
    AT161799 1999-09-22

    Publications (3)

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    EP1087109A2 true EP1087109A2 (en) 2001-03-28
    EP1087109A3 EP1087109A3 (en) 2002-08-14
    EP1087109B1 EP1087109B1 (en) 2003-09-10

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    EP (1) EP1087109B1 (en)
    AT (2) AT410696B (en)
    DE (1) DE50003618D1 (en)
    ES (1) ES2203385T3 (en)

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    WO2003027449A1 (en) * 2001-09-26 2003-04-03 Robert Bosch Gmbh Device for controlling an opening section in an internal combustion engine combustion cylinder
    DE102006012067A1 (en) * 2006-03-16 2007-09-20 Volkswagen Ag Hydraulic valve activation device for charge cycle valve, has fit designed between output shaft and guidance so that throttle flow takes place from piston sided pressure chamber into housing sided pressure chamber
    DE102004018359B4 (en) * 2003-04-12 2013-12-24 Mahle Ventiltrieb Gmbh Hydraulic actuator of particular gas exchange valves of an internal combustion engine
    ITBO20130057A1 (en) * 2013-02-13 2014-08-14 Gnutti Spa Trafilierie PUNTER WITH HYDRAULIC COMPENSATOR SYSTEM OF THE GAME USED IN A CINEMATISM, IN PARTICULAR IN THE KINEMATIC CHAIN OF CONNECTION BETWEEN A CAMSHAFT AND A VALVE IN AN ENDOTHERMAL ENGINE.
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    JP2004084670A (en) * 2002-08-28 2004-03-18 Man B & W Diesel As Valve operated with hydraulic pressure
    FR2878559B1 (en) * 2004-11-30 2009-07-03 Renault Sas DEVICE FOR ACTUATING THE VALVES OF A THERMAL MOTOR WITHOUT CAMSHAFT AND TWO-PART VALVE PISTON
    SE531535C2 (en) * 2006-02-14 2009-05-12 Cargine Engineering Ab Method for braking an actuator piston, as well as a pneumatic actuator
    DE102008054014A1 (en) * 2008-10-30 2010-05-06 Man Nutzfahrzeuge Aktiengesellschaft Gas exchange valve for internal combustion engines
    US8578897B2 (en) 2011-04-12 2013-11-12 Ford Global Technologies, Llc Valve system
    KR101251522B1 (en) * 2011-05-04 2013-04-05 현대자동차주식회사 Hydraulic valve apparatus

    Citations (6)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    CH243908A (en) * 1944-11-27 1946-08-15 Schweizerische Lokomotiv Fluid brake with check valve on the passive piston of hydraulically controlled valves of internal combustion engines.
    JPS60252111A (en) * 1984-05-28 1985-12-12 Yanmar Diesel Engine Co Ltd Damping mechanism of hydraulic valve device for internal-combustion engine
    US5275136A (en) * 1991-06-24 1994-01-04 Ford Motor Company Variable engine valve control system with hydraulic damper
    EP0652355A1 (en) * 1993-11-02 1995-05-10 Niigata Engineering Co., Ltd. Hydraulic intake/exhaust valve drive unit with damper
    DE4443169A1 (en) * 1994-12-05 1996-06-13 Dens Juergen Dipl Ing Dipl Wir Valve with variable electronic control for high-speed heat engine
    DE19749302A1 (en) * 1997-11-07 1999-05-12 Bayerische Motoren Werke Ag Hydraulic actuation device for gas changeover valve for internal combustion engine

    Family Cites Families (6)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP0255668B1 (en) * 1986-07-29 1990-01-03 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Hydraulic valve control device
    US4796573A (en) * 1987-10-02 1989-01-10 Allied-Signal Inc. Hydraulic engine valve lifter assembly
    EP0614507B1 (en) * 1991-11-29 1996-09-25 Caterpillar Inc. Engine valve seating velocity hydraulic snubber
    US5216988A (en) * 1992-10-15 1993-06-08 Siemens Automotive L.P. Dual bucket hydraulic actuator
    US5503120A (en) * 1995-01-18 1996-04-02 Siemens Automotive Corporation Engine valve timing control system and method
    BR9815101A (en) * 1997-11-21 2001-04-03 Diesel Engine Retarders Inc Valve actuation system for actuating engine valves in an internal combustion engine

    Patent Citations (7)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    CH243908A (en) * 1944-11-27 1946-08-15 Schweizerische Lokomotiv Fluid brake with check valve on the passive piston of hydraulically controlled valves of internal combustion engines.
    JPS60252111A (en) * 1984-05-28 1985-12-12 Yanmar Diesel Engine Co Ltd Damping mechanism of hydraulic valve device for internal-combustion engine
    US5275136A (en) * 1991-06-24 1994-01-04 Ford Motor Company Variable engine valve control system with hydraulic damper
    DE4411857A1 (en) * 1993-05-07 1994-11-10 Ford Werke Ag Hydraulically operated valve control device with hydraulic damping
    EP0652355A1 (en) * 1993-11-02 1995-05-10 Niigata Engineering Co., Ltd. Hydraulic intake/exhaust valve drive unit with damper
    DE4443169A1 (en) * 1994-12-05 1996-06-13 Dens Juergen Dipl Ing Dipl Wir Valve with variable electronic control for high-speed heat engine
    DE19749302A1 (en) * 1997-11-07 1999-05-12 Bayerische Motoren Werke Ag Hydraulic actuation device for gas changeover valve for internal combustion engine

    Non-Patent Citations (1)

    * Cited by examiner, † Cited by third party
    Title
    PATENT ABSTRACTS OF JAPAN vol. 010, no. 126 (M-477), 10. Mai 1986 (1986-05-10) -& JP 60 252111 A (YANMAR DIESEL KK), 12. Dezember 1985 (1985-12-12) *

    Cited By (9)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP1270881A1 (en) * 2001-06-12 2003-01-02 Visteon Global Technologies, Inc. Variable lift actuator
    US6584885B2 (en) 2001-06-12 2003-07-01 Visteon Global Technologies, Inc. Variable lift actuator
    WO2003027449A1 (en) * 2001-09-26 2003-04-03 Robert Bosch Gmbh Device for controlling an opening section in an internal combustion engine combustion cylinder
    DE102004018359B4 (en) * 2003-04-12 2013-12-24 Mahle Ventiltrieb Gmbh Hydraulic actuator of particular gas exchange valves of an internal combustion engine
    DE102006012067A1 (en) * 2006-03-16 2007-09-20 Volkswagen Ag Hydraulic valve activation device for charge cycle valve, has fit designed between output shaft and guidance so that throttle flow takes place from piston sided pressure chamber into housing sided pressure chamber
    DE102006012067B4 (en) * 2006-03-16 2016-03-24 Volkswagen Ag Hydraulic valve actuating device for a gas exchange valve
    ITBO20130057A1 (en) * 2013-02-13 2014-08-14 Gnutti Spa Trafilierie PUNTER WITH HYDRAULIC COMPENSATOR SYSTEM OF THE GAME USED IN A CINEMATISM, IN PARTICULAR IN THE KINEMATIC CHAIN OF CONNECTION BETWEEN A CAMSHAFT AND A VALVE IN AN ENDOTHERMAL ENGINE.
    DE102017113783A1 (en) 2017-06-21 2018-12-27 Man Truck & Bus Ag Power transmission device
    US10718237B2 (en) 2017-06-21 2020-07-21 Man Truck & Bus Ag Force transmission device

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    ATA161799A (en) 2002-11-15
    DE50003618D1 (en) 2003-10-16
    EP1087109A3 (en) 2002-08-14
    ATE249574T1 (en) 2003-09-15
    ES2203385T3 (en) 2004-04-16
    AT410696B (en) 2003-06-25
    EP1087109B1 (en) 2003-09-10
    US6382147B1 (en) 2002-05-07

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