EP0254967A2 - Hydraulic valve control device - Google Patents

Hydraulic valve control device Download PDF

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Publication number
EP0254967A2
EP0254967A2 EP87110247A EP87110247A EP0254967A2 EP 0254967 A2 EP0254967 A2 EP 0254967A2 EP 87110247 A EP87110247 A EP 87110247A EP 87110247 A EP87110247 A EP 87110247A EP 0254967 A2 EP0254967 A2 EP 0254967A2
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EP
European Patent Office
Prior art keywords
throttle
working piston
valve
gap
hydraulic
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.)
Granted
Application number
EP87110247A
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German (de)
French (fr)
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EP0254967A3 (en
EP0254967B1 (en
Inventor
Jurij Gartner
Peter Langen
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication date
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Publication of EP0254967A2 publication Critical patent/EP0254967A2/en
Publication of EP0254967A3 publication Critical patent/EP0254967A3/en
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Publication of EP0254967B1 publication Critical patent/EP0254967B1/en
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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
    • 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
    • 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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a device of the type specified in the preamble of the first claim.
  • Freely controllable hydraulic devices for influencing the course of the valve stroke are sufficiently known in principle. In some cases, only the maximum valve lift can be regulated, or it is possible to additionally influence the rising or falling flank of the valve lift curve. If the falling flank is influenced, the sudden change in the valve speed, which would occur if the valve abruptly touched down on the valve seat ring, must be avoided by interposing a simple hydraulic braking device; the valve speed is continuously throttled until the valve is finally put on.
  • Such a generic arrangement is known for example from DE-OS 35 37 630.
  • a drive piston actuated by a cam acts on a working piston assigned to the valve via a hydraulic working space.
  • a valve spring acts on the valve itself, which initiates the valve closing movement as soon as the volume of the work space is increased - be it by the cam-controlled backward movement of the drive piston or by targeted control of the valve lift, i.e. a freely controllable discharge of the hydraulic fluid from the work space .
  • the thereby from Hydraulic fluid displaced by the working piston flows towards the end of the closing movement on its way into the working space via a throttle gap.
  • This throttle gap is formed by an attachment on the working piston and the cylinder wall surrounding the working piston.
  • a disadvantage of this arrangement is the extremely strong braking towards the end of the valve closing process.
  • the valve closing movement triggered by the valve spring is initially strongly accelerated, and then abruptly braked as soon as the throttle gap opposes a clear resistance to the flowing hydraulic medium. Then the hydraulic fluid passes the throttle gap at high speed for the first time, so that there is a risk of vapor bubble formation and cavitation damage.
  • the system is then subjected to high forces, since large amounts of energy have to be destroyed. As a result, the entire system can be mechanically loaded in an impermissibly high manner.
  • the throttle gap in the generic arrangement is designed in such a way that it has a cross section narrowing towards the end of the valve closing movement, the initial braking action of the throttle gap begins too abruptly during the valve closing movement.
  • the object of the invention is therefore to provide a simple device for the hydraulic control of globe valves, in which the valve closing movement is initially slowed down and only decelerated towards the end of the braking phase.
  • a throttle disc that moves freely between stops in the hydraulic chamber splits the braking process into a pre-braking phase, during which the throttle disc is moved against a stop and the amount of hydraulic that is displaced in the process via two damping devices gap (formed by the throttle disc and working piston or throttle disc and housing) is pushed, and an end braking phase during which the throttle disc rests against a stop, thereby closing a damping gap, and only the damping gap formed by the working piston and the throttle disc is significantly more effective .
  • This division also significantly reduces the influence of different hydraulic viscosities, such as those that occur during the warm-up phase of the piston machine.
  • Claim 3 describes a simple design of the throttle disc to ensure that the damping gap cross-sections narrow continuously in the course of the valve closing movement.
  • the throttle disk as described in claim 4, is also provided with openings outside the damping gap area, the filling of the partial hydraulic space between the throttle disk and the working piston takes place significantly accelerated during the valve opening movement, so that a desired rapid valve opening movement is made possible.
  • Claim 5 describes an advantageous embodiment of the working piston.
  • a movable connection of a brake element forming the damping gap to the working piston that transmits the valve movement ensures a constant braking effect, regardless of length tolerances, because the damping gap becomes are always trained in such a way that there is a balance of forces between the energy storage elements and the hydraulic pressure.
  • a cam 1 acts on a drive piston 2, which actuates an axially displaceable working piston 4 via a hydraulic chamber 3.
  • This consists of a sleeve 5 and an end plate 6, which rests on the free end of a valve stem 7 of a valve, not shown.
  • An essentially cylindrical brake element 8 is mounted in the interior of the sleeve 5 so as to be longitudinally displaceable and is supported on the end plate 6 by a spring 9.
  • the hydraulic chamber 10 formed in the interior of the braking element 8 is connected to the hydraulic working space 3 via a throttle bore 11 in the braking element 8.
  • a throttle disk 13 movably mounted in the housing 12 of the device is supported either on the hollow cylinder 14 screwed into the housing 12 and forming the raceway for the sleeve 5 (stop 23) or on its upper stop 15 formed by the housing 12.
  • the throttle disc 13 has a central opening 24 and a circumferential collar 25 and is provided with openings 16. It divides the hydraulic space 3 into two ring-shaped partial hydraulic spaces 17 and 18, which are connected to one another via the openings 16 and via the damping gap 19 (formed by throttle disk 13 and braking element 8) or the damping gap 20 (formed by throttle disk 13 and its upper stop) 15) are connected to the hydraulic room 3.
  • a part of the hydraulic volume located in the hydraulic space 3 can be discharged via a control valve 21.
  • a valve spring 22 acts on the valve stem 7 of the lift valve in a known manner.
  • the throttle disk 13 During the valve opening movement, the throttle disk 13, as shown in FIG. 3, rests on its lower stop 23. Due to the pressure applied by the drive piston 2 in the hydraulic chamber 3 and in the hydraulic chamber 10, the working piston 4 moves downward and the lift valve is opened. If the hydraulic space 3 is now enlarged - be it by the upward movement of the drive piston 2 or by opening the control valve 16 - this causes Force of the valve spring 22 causes a closing movement of the valve, the valve stem 7 presses the working piston 4 upward and the hydraulic fluid flows from the partial hydraulic chamber 18 via the damping gap 19 and the openings 16 and the damping gap 20. In this pre-braking phase, the throttle disc 13 moves in the direction its upper stop 15.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

1. A device for hydraulic control of reciprocating valves on piston engines, the opening movement being transmitted directly to the valve via a hydraulic chamber and a working piston and the closing movement being triggered by an energy accumulating element engaging the valve, a throttle gap formed by the working piston and a stationary wall of the hydraulic chamber being provided for the fluid displaced in the process by the working cylinder, characterised in that a freely-movable orifice plate (13) is provided in the hydraulic chamber (3) between an abutment (23) and a stationary abutment (15) on the casing, and divides the throttle gap into a first damping gap (19) formed by the orifice plate (13) and the working piston (4), and a second damping gap (20) formed by the orifice plate (13) and the abutment (15) on the casing.

Description

Die Erfindung bezieht sich auf eine Vorrichtung der im Oberbegriff des ersten Anspruchs angegebenen Art.The invention relates to a device of the type specified in the preamble of the first claim.

Frei ansteuerbare hydraulische Vorrichtungen zur Beeinflussung des Ventilhubverlaufs sind vom Prinzip her hinreichend bekannt. Dabei kann teilweise nur der maximale Ventilhub geregelt werden oder es ist eine zusätzliche Beeinflussung der ansteigenden bzw. abfallenden Flanke des Ventilhubverlaufs möglich. Bei Beeinflussung der abfallenden Flanke muß die sprunghafte Änderung der Ventilgeschwindigkeit, welche sich beim schlagartigen Aufsetzen des Ventils auf dem Ventilsitzring einstellen würde, durch Zwischenschalten einer einfachen hydraulischen Bremseinrichtung vermieden werden; dabei wird die Ventilgeschwindigkeit bis zum endgültigen Aufsetzen des Ventils kontinuierlich gedrosselt.Freely controllable hydraulic devices for influencing the course of the valve stroke are sufficiently known in principle. In some cases, only the maximum valve lift can be regulated, or it is possible to additionally influence the rising or falling flank of the valve lift curve. If the falling flank is influenced, the sudden change in the valve speed, which would occur if the valve abruptly touched down on the valve seat ring, must be avoided by interposing a simple hydraulic braking device; the valve speed is continuously throttled until the valve is finally put on.

Eine solche gattungsbildende Anordnung ist beispielsweise aus der DE-OS 35 37 630 bekannt.
Dabei wirkt ein von einem Nocken betätigter Antriebskolben über einen hydraulischen Arbeitsraum auf einen dem Ventil zugeordneten Arbeitskolben. Am Ventil selbst greift eine Ventilfeder an, welche, sobald der Arbeitsraum in seinem Volumen vergrößert wird - sei es durch die vom Nocken gesteuerte Rückwärtsbewegung des Antriebskolbens oder durch gezielte Absteuerung des Ventilhubs, also einer frei ansteuerbaren Ableitung der Hydraulikflüssigkeit aus dem Arbeitsraum - die Ventilschließbewegung einleitet. Die dadurch vom Arbeitskolben verdrängte Hydraulikflüssigkeit strömt gegen Ende der Schließbewegung auf ihrem Weg in den Arbeitsraum über einen Drosselspalt. Dieser Drosselspalt wird dabei von einem Aufsatz auf dem Arbeitskolben und der den Arbeitskolben umgebenden Zylinderwand gebildet.Such a generic arrangement is known for example from DE-OS 35 37 630.
In this case, a drive piston actuated by a cam acts on a working piston assigned to the valve via a hydraulic working space. A valve spring acts on the valve itself, which initiates the valve closing movement as soon as the volume of the work space is increased - be it by the cam-controlled backward movement of the drive piston or by targeted control of the valve lift, i.e. a freely controllable discharge of the hydraulic fluid from the work space . The thereby from Hydraulic fluid displaced by the working piston flows towards the end of the closing movement on its way into the working space via a throttle gap. This throttle gap is formed by an attachment on the working piston and the cylinder wall surrounding the working piston.

Ein Nachteil dieser Anordnung ist in der extrem starken Abbremsung gegen Ende des Ventilschließvorganges zu sehen. Die von der Ventilfeder ausgelöste Ventilschließbewegung erfolgt zunächst stark beschleunigt, um danach, sobald der Drosselspalt dem abströmenden Hydraulikmedium einen deutlichen Widerstand entgegensetzt, abrupt abgebremst zu werden. Dann passiert die Hydraulikflüssigkeit im ersten Augenblick den Drosselspalt mit hoher Geschwindigkeit, sodaß die Gefahr von Dampfblasenbildung und Kavitationsschäden besteht. Im Anschluß daran wird das System mit hohen Kräften beaufschlagt, da große Energiemengen vernichtet werden müssen. Dadurch kann das gesamte System in unzulässig hoher Weise mechanisch belastet werden.A disadvantage of this arrangement is the extremely strong braking towards the end of the valve closing process. The valve closing movement triggered by the valve spring is initially strongly accelerated, and then abruptly braked as soon as the throttle gap opposes a clear resistance to the flowing hydraulic medium. Then the hydraulic fluid passes the throttle gap at high speed for the first time, so that there is a risk of vapor bubble formation and cavitation damage. The system is then subjected to high forces, since large amounts of energy have to be destroyed. As a result, the entire system can be mechanically loaded in an impermissibly high manner.

Zwar ist der Drosselspalt in der gattungsbildenden Anordnung so gestaltet, daß er einen sich gegen Ende der Ventilschließbewegung verengenden Querschnitt aufweist, aber dennoch setzt bei der Ventilschließbewegung die erstmalige Bremswirkung des Drosselspaltes zu abrupt ein.Although the throttle gap in the generic arrangement is designed in such a way that it has a cross section narrowing towards the end of the valve closing movement, the initial braking action of the throttle gap begins too abruptly during the valve closing movement.

Aufgabe der Erfindung ist es deshalb, eine einfache Vorrichtung zur hydraulischen Steuerung von Hubventilen zu schaffen, bei welcher die Ventilschließbewegung zunächst schwach vorgebremst und erst gegen Ende der Bremsphase verstärkt verzögert wird.The object of the invention is therefore to provide a simple device for the hydraulic control of globe valves, in which the valve closing movement is initially slowed down and only decelerated towards the end of the braking phase.

Die Aufgabe wird durch die kennzeichnenden Merkmale des ersten Anspruchs gelöst.
Eine im Hydraulikraum zwischen Anschlägen freibewegliche Drosselscheibe spaltet den Bremsvorgang auf in eine Vorbremsphase, während derer die Drosselscheibe gegen einen Anschlag bewegt wird und die dabei verdrängte Hydraulikmenge über zwei Dämpfungs spalte (gebildet von Drosselscheibe und Arbeitskolben bzw. von Drosselscheibe und Gehäuse) geschoben wird, und eine Endbremsphase, während derer die Drosselscheibe an einem Anschlag anliegt, dadurch ein Dämpfungsspalt geschlossen ist, und nurmehr der vom Arbeitskolben und der Drosselscheibe gebildete Dämpfungsspalt deutlich verstärkt wirksam ist.
Durch diese Aufteilung wird auch der Einfluß unterschiedlicher Hydraulikviskositäten, wie sie beispielsweise in der Warmlaufphase der Kolbenmaschine auftreten, deutlich reduziert.The object is achieved by the characterizing features of the first claim.
A throttle disc that moves freely between stops in the hydraulic chamber splits the braking process into a pre-braking phase, during which the throttle disc is moved against a stop and the amount of hydraulic that is displaced in the process via two damping devices gap (formed by the throttle disc and working piston or throttle disc and housing) is pushed, and an end braking phase during which the throttle disc rests against a stop, thereby closing a damping gap, and only the damping gap formed by the working piston and the throttle disc is significantly more effective .
This division also significantly reduces the influence of different hydraulic viscosities, such as those that occur during the warm-up phase of the piston machine.

Ein e vorteilhafte Weiterbildung der Erfindung ist nach Anspruch 2 gegeben, denn sich im Verlauf der Ventilschließbewegung verändernde, insbesondere verengende Dämpfungsspalte erlauben eine optimale Auslegung im Hinblick auf Ladungswechseldynamik und mechanische Standfestigkeit.
Einerseits ist eine schnelle Ventilschließbewegung erwünscht, andererseits darf das Ventil nicht schlagartig aufsetzen, denn die mechanischen Belastungen und Druckschwingungen (Kavitationsschäden) in der Hydraulik würden das System zerstören.An advantageous further development of the invention is given according to claim 2, because changing, in particular narrowing damping gaps in the course of the valve closing movement allow an optimal design with regard to charge cycle dynamics and mechanical stability.
On the one hand, a quick valve closing movement is desired, on the other hand, the valve must not abruptly touch down because the mechanical loads and pressure vibrations (cavitation damage) in the hydraulics would destroy the system.

Anspruch 3 beschreibt eine einfache Ausbildung der Drosselscheibe zur Sicherstellung von sich im Verlauf der Ventilschließbewegung kontinuierlich verengenden Dämpfungsspalt-Querschnitten.Claim 3 describes a simple design of the throttle disc to ensure that the damping gap cross-sections narrow continuously in the course of the valve closing movement.

Ist die Drosselscheibe, wie Anspruch 4 beschreibt, zudem außerhalb des Dämpfungsspaltbereichs mit Durchbrüchen versehen, so erfolgt bei der Ventilöffnungsbewegung speziell die Befüllung des zwischen Drosselscheibe und Arbeitskolben befindlichen Teilhydraulikraumes deutlich beschleunigt, sodaß eine gewünschte schnelle Ventilöffnungsbewegung ermöglicht wird.If the throttle disk, as described in claim 4, is also provided with openings outside the damping gap area, the filling of the partial hydraulic space between the throttle disk and the working piston takes place significantly accelerated during the valve opening movement, so that a desired rapid valve opening movement is made possible.

Anspruch 5 beschreibt eine vorteilhafte Ausbildung des Arbeitskolbens. Eine bewegliche Anbindung eines den Dämpfungsspalt bildenden Bremselementes an dem die Ventilbewegung übertragenden Arbeitskolben stellt unabhängig von Längentoleranzen eine konstante Bremswirkung sicher, denn der Dämpfungsspalt wird sich stets in der Weise ausbilden, daß zwischen den Kraftspeicherelementen und dem hydraulischen Druck ein Kräftegleichgewicht herrscht.Claim 5 describes an advantageous embodiment of the working piston. A movable connection of a brake element forming the damping gap to the working piston that transmits the valve movement ensures a constant braking effect, regardless of length tolerances, because the damping gap becomes are always trained in such a way that there is a balance of forces between the energy storage elements and the hydraulic pressure.

Eine vorteilhafte Weiterbildung der Erfindung ist in Anspruch 6 ausgeführt. Durch die hohle Ausbildung des Bremselementes wird in seinem Inneren zusammen mit dem Sackloch des Arbeitskolbens eine Hydraulikkammer gebildet. Im Verlauf der Ventilschließbewegung wird die Hydraulikflüssigkeit nicht nur vom Arbeitskolben über die Dämfpungsspalte verdrängt, sondern bedingt durch das Kräftegleichgewicht zum Teil auch über die Drosselöffnung aus dieser Hydraulikkammer gefördert. Dies führt vor allem gegen Ende der Ventilschließbewegung zu einer verstärkten Abbremsung. Eine Ausbildung der Drosselöffnung als scharfkantige Blende eliminiert zugleich den Einfluß unterschiedlicher Hydraulikviskositäten. Somit ist mit der erfindungsgemäßen Vorrichtung eine nahezu konstante, von der Temperatur des Hydraulikmediums unabhängige Bremsfunktion gewährleistet.An advantageous development of the invention is set out in claim 6. Due to the hollow design of the braking element, a hydraulic chamber is formed in its interior together with the blind hole of the working piston. In the course of the valve closing movement, the hydraulic fluid is not only displaced from the working piston via the damping gaps, but, due to the balance of forces, is also partly conveyed out of this hydraulic chamber via the throttle opening. This leads to increased braking, especially towards the end of the valve closing movement. Designing the throttle opening as a sharp-edged orifice also eliminates the influence of different hydraulic viscosities. Thus, the device according to the invention ensures an almost constant braking function that is independent of the temperature of the hydraulic medium.

Im folgenden wird anhand der Abbildungen ein bevorzugtes Ausführungsbeispiel näher beschrieben, wobei zur einfachen Erläuterung zwei verschiedene Stadien im Verlauf der Ventilbewegung dargestellt sind. Es zeigt:

  • Fig. 1 eine Gesamtansicht der erfindungsgemäßen Ventilanordnung.
  • Fig. 2 eine perspektivisch vergrößerte Ansicht der Drosselscheibe
  • Fig. 3 einen vergrößerten Ausschnitt der hydraulischen Bremsvorrichtung während der Ventilöffnungsbewegung
  • Fig. 4 den gleichen Ausschnitt wie Fig. 3 in der Endphase der Ventilschließbewegung.
A preferred exemplary embodiment is described in more detail below with the aid of the figures, two different stages in the course of the valve movement being shown for simple explanation. It shows:
  • Fig. 1 is an overall view of the valve assembly according to the invention.
  • Fig. 2 is a perspective enlarged view of the throttle plate
  • Fig. 3 shows an enlarged section of the hydraulic brake device during the valve opening movement
  • Fig. 4 shows the same section as Fig. 3 in the final phase of the valve closing movement.

Dargestellt sind dabei nur die zum Verständnis notwendigen Teile. In einer nicht weiter dargestellten Hubkolbenbrennkraftmaschine wirkt ein Nocken 1 auf einen Antriebskolben 2, welcher über einen Hydraulikraum 3 einen axial verschiebbaren Arbeitskolben 4 betätigt. Dieser besteht aus einer Hülse 5 und einer Abschlußscheibe 6, welche auf dem freien Ende eines Ventilschafts 7 eines nicht weiter dargestellten Ventils aufliegt. Ein im wesentlichen zylindrisch ausgebildetes Bremselement 8 ist im Inneren der Hülse 5 längsverschiebbar gelagert und stützt sich über eine Feder 9 an der Abschlußscheibe 6 ab. Die im Inneren des Bremselementes 8 gebildete Hydraulikkammer 10 steht über eine Drosselbohrung 11 im Bremselement 8 mit dem hydraulischen Arbeitsraum 3 in Verbindung. Eine im Gehäuse 12 der Vorrichtung beweglich gelagerte Drosselscheibe 13 stützt sich entweder auf dem in das Gehäuse 12 eingeschraubten und die Laufbahn für die Hülse 5 bildenden Hohlzylinder 14 (Anschlag 23) oder an ihrem oberen vom Gehäuse 1 2 gebildeten Anschlag 15 ab. Die Drosselscheibe 13 weist eine mittige Öffnung 24 und einen umlaufenden Kragen 25 auf und ist mit Durchbrüchen 16 versehen. Sie unterteilt den Hydraulikraum 3 in zwei ringförmige Teilhydraulikräume 17 und 18, welche miteinander über die Durchbrüche 16 verbunden sind und über den Dämpfungsspalt 19 (gebildet von Drosselscheibe 13 und Bremselement 8) bzw. den Dämpfungsspalt 20 (gebildet von der Drosselscheibe 13 und deren oberen Anschlag 15) mit dem Hydraulikraum 3 in Verbindung stehen. Ein Teil des im Hydraulikraum 3 befindlichen Hydraulikvolumens kann über ein Steuerventil 21 abgeführt werden. Am Ventilschaft 7 des Hubventils greift in bekannter Weise eine Ventilfeder 22 an.Only the parts necessary for understanding are shown. In a reciprocating piston internal combustion engine, not shown, a cam 1 acts on a drive piston 2, which actuates an axially displaceable working piston 4 via a hydraulic chamber 3. This consists of a sleeve 5 and an end plate 6, which rests on the free end of a valve stem 7 of a valve, not shown. An essentially cylindrical brake element 8 is mounted in the interior of the sleeve 5 so as to be longitudinally displaceable and is supported on the end plate 6 by a spring 9. The hydraulic chamber 10 formed in the interior of the braking element 8 is connected to the hydraulic working space 3 via a throttle bore 11 in the braking element 8. A throttle disk 13 movably mounted in the housing 12 of the device is supported either on the hollow cylinder 14 screwed into the housing 12 and forming the raceway for the sleeve 5 (stop 23) or on its upper stop 15 formed by the housing 12. The throttle disc 13 has a central opening 24 and a circumferential collar 25 and is provided with openings 16. It divides the hydraulic space 3 into two ring-shaped partial hydraulic spaces 17 and 18, which are connected to one another via the openings 16 and via the damping gap 19 (formed by throttle disk 13 and braking element 8) or the damping gap 20 (formed by throttle disk 13 and its upper stop) 15) are connected to the hydraulic room 3. A part of the hydraulic volume located in the hydraulic space 3 can be discharged via a control valve 21. A valve spring 22 acts on the valve stem 7 of the lift valve in a known manner.

Während der Ventilöffnungsbewegung liegt die Drosselscheibe 13, wie Fig. 3 zeigt, an ihrem unteren Anschlag 23 auf. Durch den vom Antriebskolben 2 aufgebrachten Druck im Hydraulikraum 3 und in der Hydraulikkammer 10 bewegt sich der Arbeitskolben 4 nach unten und das Hubventil wird geöffnet. Wird nun der Hydraulikraum 3 vergrößert - sei es durch Aufwärtsbewegung des Antriebskolbens 2 oder durch Öffnen des Steuerventils 16 - so bewirkt die Kraft der Ventilfeder 22 eine Schließbewegung des Ventils, der Ventilschaft 7 drückt den Arbeitskolben 4 nach oben und dabei strömt die Hydraulikflüssigkeit aus dem Teilhydraulikraum 18 über den Dämpfungsspalt 19 und die Durchbrüche 16 und den Dämpfungsspalt 20. In dieser Vorbremsphase bewegt sich die Drosselscheibe 13 in Richtung ihres oberen Anschlags 15.During the valve opening movement, the throttle disk 13, as shown in FIG. 3, rests on its lower stop 23. Due to the pressure applied by the drive piston 2 in the hydraulic chamber 3 and in the hydraulic chamber 10, the working piston 4 moves downward and the lift valve is opened. If the hydraulic space 3 is now enlarged - be it by the upward movement of the drive piston 2 or by opening the control valve 16 - this causes Force of the valve spring 22 causes a closing movement of the valve, the valve stem 7 presses the working piston 4 upward and the hydraulic fluid flows from the partial hydraulic chamber 18 via the damping gap 19 and the openings 16 and the damping gap 20. In this pre-braking phase, the throttle disc 13 moves in the direction its upper stop 15.

In der in Fig. 4 gezeigten Endbremsphase des Ventilschließvorgangs liegt die Drosselscheibe 13 an ihren oberen Anschlag 15 an und der Dämpfungsspalt 20 ist quasi geschlossen. Dadurch steigt der Druck im Teilhydraulikraum 18 so stark an, daß das Bremselement 8 nach unten gepreßt und die Hydraulikkammer 10 verkleinert wird. Hydraulikflüssigkeit tritt solange über die Drosselbohrung 11 in den Hydraulikraum 3, bis der Dämpfungsspalt 19 wieder ausreichenden Querschnitt zur Abführung von Hydraulikflüssigkeit aus dem Teilhydraulikraum 18 aufweist. Dies führt zu einer alternierenden, sozusagen schwingenden Bewegung des Bremselementes 8 im Arbeitskolben 4. In the final braking phase of the valve closing process shown in FIG. 4, the throttle disk 13 lies against its upper stop 15 and the damping gap 20 is quasi closed. As a result, the pressure in the partial hydraulic chamber 18 rises so much that the brake element 8 is pressed downward and the hydraulic chamber 10 is reduced. Hydraulic fluid flows into the hydraulic space 3 via the throttle bore 11 until the damping gap 19 again has a sufficient cross section for the discharge of hydraulic fluid from the partial hydraulic space 18. This leads to an alternating, so to speak, oscillating movement of the braking element 8 in the working piston 4.

Claims (6)

1. Vorrichtung zur hydraulischen Steuerung von Hubventilen an Kolbenmaschinen, wobei die Öffnungsbewegung über einen Hydraulikraum und einen Arbeitskolben direkt auf das Ventil übertragen wird und die Schließbewegung durch ein am Ventil angreifendes Kraftspeicherelement ausgelöst wird, wobei für die dabei vom Arbeitskolben verdrängte Flüssigkeit ein Drosselspalt, gebildet vom Arbeitskolben und einer ortsfesten Wandung des Hydraulikraumes vorgesehen ist,
dadurch gekennzeichnet, daß eine im Hydraulikraum (3) zwischen einem orstfesten Gehäuseanschlag (15) und einem Anschlag (23) freibewegliche Drosselscheibe (13) vorgesehen ist, welche den Drosselspalt unterteilt in einen ersten Dämpfungspalt (19), gebildet von Drosselscheibe (13) und Arbeitskolben (4) und einen zweiten Dämpfungsspalt (20), gebildet von Drosselscheibe (13) und Gehäuseanschlag (15).1.Device for the hydraulic control of lift valves on piston machines, the opening movement being transmitted directly to the valve via a hydraulic chamber and a working piston and the closing movement being triggered by an energy storage element acting on the valve, a throttle gap being formed for the liquid displaced by the working piston is provided by the working piston and a stationary wall of the hydraulic space,
characterized in that a freely movable throttle disc (13) is provided in the hydraulic chamber (3) between a stationary housing stop (15) and a stop (23), which divides the throttle gap into a first damping gap (19), formed by throttle disc (13) and Working piston (4) and a second damping gap (20), formed by throttle disc (13) and housing stop (15). 2. Vorrichtung nach Anspruch 1,
dadurch gekennzeichnet, daß die beiden Dämpfungsspalte (19) und (20) sich mit der Bewegung der Drosselscheibe (13) und/oder des Arbeitskolbens (4) verändernde, insbesondere verengende Querschnitte aufweisen.2. Device according to claim 1,
characterized in that the two damping gaps (19) and (20) have changing, in particular narrowing, cross sections with the movement of the throttle disc (13) and / or the working piston (4). 3. Vorrichtung nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die Drosselscheibe (13) einen um ihre mittige Öffnung (24) winkelig gegen die Scheibenebene angeordneten umlaufenden Kragen (25) aufweist, wel cher im wesentlichen die Dämpfungsspalte (19) und (20) bildet.3. Device according to claim 1 or 2,
characterized in that the throttle disc (13) has a circumferential collar (25) arranged around its central opening (24) at an angle to the plane of the disc, wel cher essentially forms the damping gaps (19) and (20). 4. Vorrichtung nach einem der vorangegangenen Ansprüche,
dadurch gekennzeichnet, daß die Fläche der Drosselscheibe (13) außerhalb des Bereichs der Dämpfungsspalte mit Durchbrüchen (16) versehen ist.4. Device according to one of the preceding claims,
characterized in that the area of the throttle disc (13) is provided with openings (16) outside the region of the damping gaps. 5. Vorrichtung nach einem der vorangegangenen Ansprüche,
dadurch gekennzeichnet, daß der Arbeitskolben (4) mit einem Sackloch versehen ist, worin ein über einen Kraftspeicher (9) am Arbeitskolben (4) abgestütztes, im wesentlichen zylindrisch geformtes Bremselement (8), dessen abgerundet ausgebildetes freies Ende mit der Drosselscheibe (13) den Dämpfungsspalt (19) bildet, axial verschiebbar gelagert ist.5. Device according to one of the preceding claims,
characterized in that the working piston (4) is provided with a blind hole, in which a substantially cylindrically shaped brake element (8) supported on the working piston (4) via an energy accumulator (9), the rounded free end of which is connected to the throttle disc (13) forms the damping gap (19), is axially displaceably mounted. 6. Vorrichtung nach Anspruch 5,
dadurch gekennzeichnet, daß das Bremselement (8) hohl ausgeführt ist und über mindestens eine Drosselöffnung (11) eine Verbindung zwischen dem Sackloch und dem Hydraulikraum (3) herstellt.6. The device according to claim 5,
characterized in that the braking element (8) is hollow and establishes a connection between the blind hole and the hydraulic chamber (3) via at least one throttle opening (11).
EP87110247A 1986-07-29 1987-07-16 Hydraulic valve control device Expired EP0254967B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863625627 DE3625627A1 (en) 1986-07-29 1986-07-29 DEVICE FOR HYDRAULIC CONTROL OF LIFT VALVES
DE3625627 1986-07-29

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EP0254967A2 true EP0254967A2 (en) 1988-02-03
EP0254967A3 EP0254967A3 (en) 1988-03-30
EP0254967B1 EP0254967B1 (en) 1989-11-08

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ID=6306210

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EP87110247A Expired EP0254967B1 (en) 1986-07-29 1987-07-16 Hydraulic valve control device

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EP (1) EP0254967B1 (en)
DE (2) DE3625627A1 (en)
ES (1) ES2011471B3 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994009265A1 (en) * 1992-10-15 1994-04-28 Siemens Automotive Corporation Dual bucket hydraulic actuator
GB2277777A (en) * 1993-05-07 1994-11-09 Ford Motor Co I.C.engine hydraulic valve gear with an hydraulic damper
EP1232336A1 (en) * 1999-09-17 2002-08-21 Diesel Engine Retarders, Inc. Captive volume accumulator for a lost motion system

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4027630C1 (en) * 1990-08-31 1991-12-05 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De

Citations (5)

* 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.
JPS59229011A (en) * 1983-06-08 1984-12-22 Yanmar Diesel Engine Co Ltd Valve operating mechanism of internal-combustion engine
DE3537630A1 (en) * 1984-10-31 1986-04-30 Volkswagen AG, 3180 Wolfsburg Valve arrangement especially for an internal combustion engine
JPS6193214A (en) * 1984-10-12 1986-05-12 Sumitomo Heavy Ind Ltd Hydraulic type exhaust valve opening and closing device
EP0196441A1 (en) * 1985-03-30 1986-10-08 Robert Bosch Gmbh Valve control system

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE751538C (en) * 1943-03-03 1952-11-04 Kloeckner Humboldt Deutz Ag Pressurized fluid drive, especially for valves on internal combustion engines

Patent Citations (5)

* 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.
JPS59229011A (en) * 1983-06-08 1984-12-22 Yanmar Diesel Engine Co Ltd Valve operating mechanism of internal-combustion engine
JPS6193214A (en) * 1984-10-12 1986-05-12 Sumitomo Heavy Ind Ltd Hydraulic type exhaust valve opening and closing device
DE3537630A1 (en) * 1984-10-31 1986-04-30 Volkswagen AG, 3180 Wolfsburg Valve arrangement especially for an internal combustion engine
EP0196441A1 (en) * 1985-03-30 1986-10-08 Robert Bosch Gmbh Valve control system

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 10, Nr. 270 (M-517)[2326], 13. September 1986; & JP-A-61 93 214 (SUMITOMO HEAVY IND. LTD) 12-05-1986 *
PATENT ABSTRACTS OF JAPAN, Band 9, Nr. 103 (M-377)[1826], 8. Mai 1985; & JP-A-59 229 011 (YANMAR DIESEL K.K.) 22-12-1984 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1994009265A1 (en) * 1992-10-15 1994-04-28 Siemens Automotive Corporation Dual bucket hydraulic actuator
GB2277777A (en) * 1993-05-07 1994-11-09 Ford Motor Co I.C.engine hydraulic valve gear with an hydraulic damper
GB2277777B (en) * 1993-05-07 1996-03-27 Ford Motor Co A hydraulically operated valve assembly
EP1232336A1 (en) * 1999-09-17 2002-08-21 Diesel Engine Retarders, Inc. Captive volume accumulator for a lost motion system
EP1232336A4 (en) * 1999-09-17 2009-08-05 Diesel Engine Retarders Inc Captive volume accumulator for a lost motion system

Also Published As

Publication number Publication date
EP0254967A3 (en) 1988-03-30
DE3625627C2 (en) 1988-06-23
DE3760968D1 (en) 1989-12-14
DE3625627A1 (en) 1988-02-04
ES2011471B3 (en) 1990-01-16
EP0254967B1 (en) 1989-11-08

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