EP0255668B1 - Hydraulic valve control device - Google Patents

Hydraulic valve control device Download PDF

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Publication number
EP0255668B1
EP0255668B1 EP87110729A EP87110729A EP0255668B1 EP 0255668 B1 EP0255668 B1 EP 0255668B1 EP 87110729 A EP87110729 A EP 87110729A EP 87110729 A EP87110729 A EP 87110729A EP 0255668 B1 EP0255668 B1 EP 0255668B1
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EP
European Patent Office
Prior art keywords
working piston
hydraulic chamber
valve
hydraulic
brake element
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EP87110729A
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German (de)
French (fr)
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EP0255668A3 (en
EP0255668A2 (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 of EP0255668A2 publication Critical patent/EP0255668A2/en
Publication of EP0255668A3 publication Critical patent/EP0255668A3/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
    • 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

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 when the valve was suddenly placed 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, as soon as the volume of the working area 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 working area Initiates valve closing movement.
  • the hydraulic fluid thus displaced by the working piston flows towards the end of the closing movement on its way into the working space via a damping gap.
  • This damping gap is formed by an attachment on the working piston and the cylinder wall surrounding the working piston.
  • this arrangement shows a device for hydraulic length compensation. This is particularly the case if the profile of the attachment on the working piston and / or the cylinder wall area interacting with it during gap formation ensures that the gap width changes according to a predetermined function during the valve closing movement, i.e. that the damping does not remain constant, must be ensured be that, despite operational or wear-related dimensional changes in the area of the valve, the association between the described gap function on the one hand and certain movement phases of the valve closing movement on the other hand is maintained.
  • auxiliary piston which is movably mounted in the working piston, which is partially hollow, and which can be displaced in its longitudinal axis acts on the valve stem.
  • a targeted leakage must be provided between the auxiliary piston and the working piston.
  • the resulting pressure loss in the hydraulic system must always be compensated for with a deterioration in efficiency.
  • this arrangement leads to a valve opening movement that can no longer be precisely determined, because depending on the hydraulic pressure in the working space and in the working chamber, the auxiliary piston is moved once, which leads to rapid valve movement because of the small piston cross section, and at other times it becomes - much slower - the other the piston is significantly larger in cross section.
  • the object of the invention is to provide a simple device for the hydraulic control of globe valves, which ensures a precisely definable braking of the valve closing movement, also taking into account operational or wear-related dimensional changes in the area of the valve.
  • a movable connection of the 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 will always develop in such a way that there is a balance of forces between the force storage elements and the hydraulic pressure.
  • the device according to the invention has the advantage that the valve opening movement is transmitted in a precisely definable manner by the rigid coupling between the valve and the working piston. B. by the length compensation element from the above. scripture does not occur here.
  • Claim 3 describes a simple, constructive design of the brake element and working piston.
  • Claim 5 deals with an advantageous embodiment of the counter surface forming the throttle gap together with the braking element. If, for this purpose, a throttle disc movably mounted outside the working piston and supported at at least two stops is provided, an additional damping gap can be formed between the throttle disc and a wall of the device with a corresponding shape, thus creating a second hydraulic working space. As a result, a significantly larger filling cross section is released during the filling phase of the hydraulic space.
  • the braking process is now subdivided into a pre-braking phase, in which the throttle disc - advantageously almost independently of the viscosity of the hydraulic medium - is moved against one of the stops, and a subsequent, reinforced final braking phase.
  • the throttle disc is also provided with breakthroughs outside the damping gap area, the filling of the hydraulic chamber and of the hydraulic space located between the disc and the braking element takes place again during the valve opening movement, so that a desired rapid valve opening movement is made possible.
  • a throttle bore connecting the hydraulic chamber in the interior of the brake element with the partial hydraulic chamber located between the throttle disc and the working piston avoids undesirably strong oscillating movements of the braking element in the working piston. Such oscillating movements are dampened in terms of intensity by partial overflow of hydraulic medium between the two hydraulic spaces mentioned.
  • Claim 8 describes a leakage hole provided in the working piston, via which a subset of the hydraulic medium located in the hydraulic chamber is discharged as a function of the forces acting on the braking element.
  • the discharge takes place in a room which is not pressurized by the pressure of the hydraulic medium in order to avoid the risk of vapor bubbles forming in the hydraulic room - caused by high flow velocities.
  • the inlet mouth of that leakage bore is advantageously disclosed when the forces acting on the brake element from the outside assume very high values, in particular when the brake element is in contact with the walls forming the damping gap.
  • a cam 1 acts on a drive piston 2, which actuates an axially displaceable working piston 43 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 opening 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 or on its upper stop 15 formed by the housing 12.
  • the throttle disc 13 is provided with openings 16 and divides the hydraulic space 3 into two annular 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 disc 13 and braking element 8) or the damping gap 20 (formed of the throttle plate 13 and its upper stop 15) are connected to the hydraulic chamber 3.
  • a connection between the hydraulic chamber 10 and the partial hydraulic chamber 18 is established via a throttle bore 23 in the braking element 8.
  • 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 disc 13 rests on the hollow cylinder 14 forming its lower stop. 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 chamber 3 is now enlarged - be it by the upward movement of the drive piston 2 or by opening the control valve 21 - the force of the valve spring 22 causes the valve to close, the valve stem 7 presses the working piston 4 upward and the hydraulic fluid flows out of 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 of its upper stop 15.
  • FIG. 5 A modified form of the working piston 4 and of the braking element 10 is shown in FIG. 5.
  • a leakage bore 24 is provided in the sleeve 5, the inlet opening 25 of which is closed by a collar 26 of the brake element 10 in the position of the brake element shown in FIG. 5. If, at the end of the braking process, the rounded upper end of the braking element 10 rests on the throttle disk 13 and this on its upper stop 15, then a further upward movement of the working piston 4 opens the inlet opening 25 of the leakage bore 24, as a result of which part of the one located in the hydraulic chamber 10 Hydraulic fluid is discharged. That leakage bore 24 is absolutely necessary in the embodiment of the brake element 10 shown here, which, in contrast to the brake element shown in FIG.
  • That lacquer bore 24 also offers advantages if, as not shown, the throttle opening 11 shown in FIG. 4 is provided on the brake element 10 in addition to the throttle bore 23. Since that throttle opening 11 must have a very narrow cross-section for functional reasons, sufficient emptying of the hydraulic chamber 10 during the valve closing movement could be called into question in exceptional cases. The result would be a so-called inflation of the braking element 8 or the hydraulic chamber 10; the desired braking function would then no longer be ensured. In those cases, a corresponding subset of hydraulic fluid can be discharged via the leakage hole 24 that then opens.
  • the present invention of the earth is not limited to the exemplary embodiment shown. Rather, what is essential is the general idea of the invention, according to which the working piston is provided with a blind hole, in which a braking element, which is supported by an energy accumulator on the working piston, is formed and forms one of the surfaces of the damping gap in order to brake the valve closing movement in a definable manner, also taking operational or wear-related factors into account To ensure dimensional changes in the area of the valve.

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

Description

Die Erfindung bezieht sich auf eine Vorrichung 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 Ventihubverlaufs 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 when the valve was suddenly placed 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 vergrö-Bert 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 Dämpfungsspalt. Dieser Dämpfungsspalt 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, as soon as the volume of the working area 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 working area Initiates valve closing movement. The hydraulic fluid thus displaced by the working piston flows towards the end of the closing movement on its way into the working space via a damping gap. This damping gap is formed by an attachment on the working piston and the cylinder wall surrounding the working piston.

Weiterhin zeigt diese Anordnung eine Vorrichtung zum hydraulischen Längenausgleich. Denn insbesondere dann, wenn durch geeignete Profilgebung des Aufsatzes auf dem Arbeitskolben und/oder des mit ihm bei der Spaltbildung zusammenwirkenden Zylinderwandbereichs dafür gesorgt ist, daß sich die Spaltweite nach einer vorgegebenen Funktion während der Ventilschließbewegung ändert, die Dämpfung also nicht konstant bleibt, muß sichergestellt sein, daß trotz betriebs- oder verschleißbedingten Dimensionsänderungen im Bereich des Ventils die Zuordnung zwischen der beschriebenen Spaltfunktion einerseits und bestimmten Bewegungsphasen der Ventilschließbewegung andererseits gewahrt bleibt.Furthermore, this arrangement shows a device for hydraulic length compensation. This is particularly the case if the profile of the attachment on the working piston and / or the cylinder wall area interacting with it during gap formation ensures that the gap width changes according to a predetermined function during the valve closing movement, i.e. that the damping does not remain constant, must be ensured be that, despite operational or wear-related dimensional changes in the area of the valve, the association between the described gap function on the one hand and certain movement phases of the valve closing movement on the other hand is maintained.

Bei der bekannten Anordnung wirkt deshalb auf den Ventilschaft nur ein kleiner, im zum Teil hohl ausgeführten Arbeitskolben beweglich gelagerter und in seiner Längsachse verschiebbarer Hilfskolben. Dieser begrenzt an seiem freien Ende eine im Inneren des Arbeitskolbens befindliche zweite hydraulische Arbeitskammer, welche mit dem oben angeführten hydraulischen Arbeitsraum über eine Bohrung im Arbeitskolben und ein darin angeordnetes Rückschlagventil verbunden ist.In the known arrangement, therefore, only a small auxiliary piston which is movably mounted in the working piston, which is partially hollow, and which can be displaced in its longitudinal axis acts on the valve stem. This delimits at its free end a second hydraulic working chamber located inside the working piston, which is connected to the above-mentioned hydraulic working chamber via a bore in the working piston and a check valve arranged therein.

Diese Anordnung weist jedoch mehrere Nachteile auf:However, this arrangement has several disadvantages:

Zum einen muß zwischen Hilfskolben und Arbeitskolben eine gezielte Leckage vorgesehen sein. Der dadurch bedingte Druckverlust im Hydrauliksystem muß unter Wirkungsgradverschlechterung stets wieder ausgeglichen werden. Des weiteren führt diese Anordnung zu einer nicht mehr exakt festlegbaren Ventilöffnungsbewegung, denn in Abhängigkeit des hydraulischen Drucks im Arbeitsraum und in der Arbeitskammer wird einmal der Hilfskolben bewegt, was wegen des geringen Kolbenquerschnitts zu einer schnellen Ventilbewegung führt, ein andermal wird - wesentlich langsamer - der im Querschnitt deutlich größere Arbeitskolben vorangetrieben.On the one hand, a targeted leakage must be provided between the auxiliary piston and the working piston. The resulting pressure loss in the hydraulic system must always be compensated for with a deterioration in efficiency. Furthermore, this arrangement leads to a valve opening movement that can no longer be precisely determined, because depending on the hydraulic pressure in the working space and in the working chamber, the auxiliary piston is moved once, which leads to rapid valve movement because of the small piston cross section, and at other times it becomes - much slower - the other the piston is significantly larger in cross section.

Aufgabe der Erfindung ist es, eine einfache Vorrichtung zur hydraulischen Steuerung von Hubventilen zu schaffen, welche eine genau definierbare Abbremsung der Ventilschließbewegung auch unter Berücksichtigung von betriebs- oder verschleißbedingten Dimensionsänderungen im Bereich des Ventils gewährleistet.The object of the invention is to provide a simple device for the hydraulic control of globe valves, which ensures a precisely definable braking of the valve closing movement, also taking into account operational or wear-related dimensional changes in the area of the valve.

Diese Aufgabe wird durch die kennzeichnenden Merkmale des Anspruchs 1 gelöst. Eine bewegliche Anbindung des 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. Zudem weist die erfindungsgemäße Vorrichtung den Vorteil auf, daß die Ventilöffnungsbewegung durch die starre Kopplung zwischen Ventil und Arbeitskolben genau definierbar übertragen wird, eine Verfälschung wie z. B. durch das Längenausgleichselement aus der o.g. Schrift tritt hierbei nicht auf.This object is achieved by the characterizing features of claim 1. A movable connection of the 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 will always develop in such a way that there is a balance of forces between the force storage elements and the hydraulic pressure. In addition, the device according to the invention has the advantage that the valve opening movement is transmitted in a precisely definable manner by the rigid coupling between the valve and the working piston. B. by the length compensation element from the above. Scripture does not occur here.

Eine vorteilhafte Weiterbildung der Erfindung ist nach Anspruch 2 gegeben, denn ein sich im Verlauf der Ventilschließbewegung verändernder, insbesondere verengender Dämpfungsspalt erlaubt 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 a damping gap that changes in the course of the valve closing movement, in particular narrowing, allows an optimal design with regard to the dynamics of charge change 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, konstruktive Ausgestaltung von Bremselement und Arbeitskolben.Claim 3 describes a simple, constructive design of the brake element and working piston.

Eine vorteilhafte Weiterbildung der Erfindung ist in Anspruch 4 aufgeführt. 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 den Dämpfungsspalt verdrängt, sondern bedingt durch das Kräftegleichgewicht zum Teil auch über Drosselöffnungen aus dieser Hydraulikkammer gefördert. Dies führt vor allem gegen Ende der Ventilschließbewegung zu einer verstärkten Abbremsung. Eine Ausbildung der Drosselöffnungen 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 4. 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 gap, but is also partly conveyed out of this hydraulic chamber via throttle openings due to the balance of forces. This leads to increased braking, especially towards the end of the valve closing movement. A design of the throttle openings as a sharp-edged aperture eli minimizes the influence of different hydraulic viscosities. The device according to the invention thus ensures an almost constant braking function that is independent of the temperature of the hydraulic medium.

Anspruch 5 behandelt eine vorteilhafte Ausbildung der zusammen mit dem Bremselement den Drosselspalt bildenden Gegenfläche. Wird hierfür eine außerhalb des Arbeitskolbens beweglich gelagerte und an mindestens zwei Anschlägen abstützbare Drosselscheibe vorgesehen, so kann bei entsprechender Formgebung ein zusätzlicher Dämpfungsspalt zwischen der Drosselscheibe und einer Wandung der Vorrichtung gebildet werden, womit quasi ein zweiter hydraulischer Arbeitsraum geschaffen wird. Dadurch wird während der Befüllungsphase des Hydraulikraumes ein deutlich größerer Befüllungsquerschnitt freigegeben. Der Abbremsvorgang unterteilt sich nun in eine Vorbremsphase, in welcher die Drosselscheibe - vorteilhafterweise nahezu unabhängig von der Viskosität des Hydraulikmediums - gegen einen der Anschläge bewegt wird, und in eine sich daran anschließende, verstärkte Endbremsphase.Claim 5 deals with an advantageous embodiment of the counter surface forming the throttle gap together with the braking element. If, for this purpose, a throttle disc movably mounted outside the working piston and supported at at least two stops is provided, an additional damping gap can be formed between the throttle disc and a wall of the device with a corresponding shape, thus creating a second hydraulic working space. As a result, a significantly larger filling cross section is released during the filling phase of the hydraulic space. The braking process is now subdivided into a pre-braking phase, in which the throttle disc - advantageously almost independently of the viscosity of the hydraulic medium - is moved against one of the stops, and a subsequent, reinforced final braking phase.

Ist die Drosselscheibe, wie Anspruch 6 beschreibt, zudem außerhalb des Dämpfungsspaltbereichs mit Druchbrüchen versehen, so erfolgt bei dier Ventilöffnungsbewegung die Befüllung der Hydraulikkammer sowie des zwischen Scheibe und Bremselement befindllichen Hydraulikraumes nochmals beschleunigt, sodaß eine gewünschte schnelle Ventilöffnungsbewegung ermöglicht wird.If, as described in claim 6, the throttle disc is also provided with breakthroughs outside the damping gap area, the filling of the hydraulic chamber and of the hydraulic space located between the disc and the braking element takes place again during the valve opening movement, so that a desired rapid valve opening movement is made possible.

Eine gemäß Anspruch 7 die Hydraulikkammer im Inneren des Bremselementes mit dem zwischen Drosselscheibe und Arbeitskolben liegenden Teilhydraulikraum verbindende Drosselbohrung vermeidet unerwünscht starke Schwingbewegungen des Bremselementes im Arbeitskolben. Durch teilweises Überströmen von Hydraulikmedium zwischen den beiden genannten Hydraulikräumen werden derartige Schwingbewegungen intensitätsmäßig gedämpft.A throttle bore connecting the hydraulic chamber in the interior of the brake element with the partial hydraulic chamber located between the throttle disc and the working piston avoids undesirably strong oscillating movements of the braking element in the working piston. Such oscillating movements are dampened in terms of intensity by partial overflow of hydraulic medium between the two hydraulic spaces mentioned.

Anspruch 8 beschreibt eine im Arbeitskolben vorgesehene Leckagebohrung, über welche in Abhängigkeit von den auf das Bremselement einwirkenden Kräften eine Teilmenge des in der Hydraulikkammer befindlichen Hydraulikmediums abgeführt wird. Die Abfuhr erfolgt dabei in einen Raum, welcher nicht vom Druck des Hydraulikmediums beaufschlagt ist, um die Gefahr von Dampfblasenbildung im Hydraulikraum - hervorgerufen durch hohe Strömungsgeschwindigkeiten - zu vermeiden. Offengelegt ist die Eintrittsmündung jener Leckagebohrung vorteilhafterweise dann, wenn die von außen auf das Bremselement wirkenden Kräfte sehr hohe Werte annehmen, also insbesondere dann, wenn das Bremselement an den den Dämpfungsspalt bildenden Wandungen anliegt.Claim 8 describes a leakage hole provided in the working piston, via which a subset of the hydraulic medium located in the hydraulic chamber is discharged as a function of the forces acting on the braking element. The discharge takes place in a room which is not pressurized by the pressure of the hydraulic medium in order to avoid the risk of vapor bubbles forming in the hydraulic room - caused by high flow velocities. The inlet mouth of that leakage bore is advantageously disclosed when the forces acting on the brake element from the outside assume very high values, in particular when the brake element is in contact with the walls forming the damping gap.

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,
  • Fig. 5 eine andere Ausführungsform von Bremselement und Arbeitszylinder, ebenfalls 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
  • 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,
  • Fig. 5 shows another embodiment of the braking element and working cylinder, also 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 43 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 Drosselöffnung 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 oder an ihrem oberen vom Gehäuse 12 gebildeten Anschlag 15 ab. Die Drosselscheibe 13 ist mit Durchbrüchen 16 versehen und 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. Über eine Drosselbohrung 23 im Bremselement 8 ist eine Verbindung zwischen der Hydraulikkammer 10 und dem Teilhydraulikraum 18 hergestellt. 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 43 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 opening 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 or on its upper stop 15 formed by the housing 12. The throttle disc 13 is provided with openings 16 and divides the hydraulic space 3 into two annular 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 disc 13 and braking element 8) or the damping gap 20 (formed of the throttle plate 13 and its upper stop 15) are connected to the hydraulic chamber 3. A connection between the hydraulic chamber 10 and the partial hydraulic chamber 18 is established via a throttle bore 23 in the braking element 8. 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 dem ihren unteren Anschlag bildenden Hohlzylinder 14 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 21 - 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 disc 13, as shown in FIG. 3, rests on the hollow cylinder 14 forming its lower stop. 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 chamber 3 is now enlarged - be it by the upward movement of the drive piston 2 or by opening the control valve 21 - the force of the valve spring 22 causes the valve to close, the valve stem 7 presses the working piston 4 upward and the hydraulic fluid flows out of 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 of 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 Drosselöffnung 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, wodurch nahezu unabhängig von der augenblicklichen Viskosität des Hydraulikmediums oder einer Längenänderung des Ventilschafts 7 stets die gewünschte Spaltfunktion gewährleistet ist. Durch Überströmen des Hydraulikmediums vom Teilhydraulikraum 18 über die Drosselbohrung 23 in die Hydraulikkammer 10 wird dabei eine gewünschte Schwingungsdämpfung erzielt.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 virtually 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 opening 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, whereby the desired splitting function is always ensured almost independently of the instantaneous viscosity of the hydraulic medium or a change in length of the valve stem 7. By overflowing the hydraulic medium from the partial hydraulic chamber 18 through the throttle bore 23 into the hydraulic chamber 10, a desired vibration damping is achieved.

Eine abgeänderte.Form des Arbeitskolbens 4 sowie des Bremselementes 10 ist in Fig. 5 dargestellt. Dabei ist in der Hülse 5 eine Leckagebohrung 24 vorgesehen, deren Eintrittsöffnung 25 von einem Bund 26 des Bremselementes 10 in der in Fig. 5 dargestellten Position des Bremselementes verschlossen ist. Liegt gegen Ende des Bremsvorganges das Bremselement 10 mit seinem abgerundeten oberen Ende an der Drosselscheibe 13 und diese an ihrem oberen Anschlag 15 an, so öffnet eine weitere Aufwärtsbewegung des Arbeitskolbens 4 die Eintrittsmündung 25 der Leckagebohrung 24, wodurch ein Teil der in der Hydraulikkammer 10 befindlichen Hydraulikflüssigkeit abgeführt wird. Jene Leckagebohrung 24 ist bei der hier gezeigten Ausführung des Bremselementes 10, welches im Gegensatz zu dem in Fig. 4 dargestellten Bremselement lediglich mit der Drosselbohrung 23, nicht aber mit der Drosselöffnung 11 versehen ist, unbedingt erforderlich, um die Hydraulikflüssigkeit aus dem sich bei der Ventilschließbewegung weiter verkleindernden Teilhydraulikräumen 17 und 18 abzuführen. Jene Lackagebohrung 24 bietet aber auch Vorteile, wenn - wie nicht dargestellt - am Bremselement 10 zusätzlich zur Drosselbohrung 23 die in Fig. 4 gezeigte Drosselöffnung 11 vorgesehen ist. Da jene Drosselöffnung 11 aus Funktionsgründen einen sehr engen Querschnitt aufweisen muß, könnte in Ausnahmefällen eine ausreichende Entleerung der Hydraulikkammer 10 während der Ventilschließbewegung in Frage gestellt sein. Ein sog. Aufpumpen des Bremselementes 8 bzw. der Hydraulikkammer 10 wäre die Folge; die gewünschte Bremsfunktion wäre dann nicht mehr sichergestellt. In jenen Fällen kann über die sich dann öffnende Leckagebohrung 24 eine entsprechende Teilmenge von Hydraulikflüssigkeit abgeführt werden.A modified form of the working piston 4 and of the braking element 10 is shown in FIG. 5. In this case, a leakage bore 24 is provided in the sleeve 5, the inlet opening 25 of which is closed by a collar 26 of the brake element 10 in the position of the brake element shown in FIG. 5. If, at the end of the braking process, the rounded upper end of the braking element 10 rests on the throttle disk 13 and this on its upper stop 15, then a further upward movement of the working piston 4 opens the inlet opening 25 of the leakage bore 24, as a result of which part of the one located in the hydraulic chamber 10 Hydraulic fluid is discharged. That leakage bore 24 is absolutely necessary in the embodiment of the brake element 10 shown here, which, in contrast to the brake element shown in FIG. 4, is only provided with the throttle bore 23, but not with the throttle opening 11, in order to remove the hydraulic fluid from which To remove valve closing movement further reducing partial hydraulic rooms 17 and 18. That lacquer bore 24 also offers advantages if, as not shown, the throttle opening 11 shown in FIG. 4 is provided on the brake element 10 in addition to the throttle bore 23. Since that throttle opening 11 must have a very narrow cross-section for functional reasons, sufficient emptying of the hydraulic chamber 10 during the valve closing movement could be called into question in exceptional cases. The result would be a so-called inflation of the braking element 8 or the hydraulic chamber 10; the desired braking function would then no longer be ensured. In those cases, a corresponding subset of hydraulic fluid can be discharged via the leakage hole 24 that then opens.

Selbstverständlich bleibt die vorliegende Erdfindung nicht auf das gezeigte Ausführungsbeispiel beschränkt. Wesentlich ist vielmehr der allgemeine Erfindungsgedanke, wonach der Arbeitskolben mit einem Sackloch versehen ist, worin ein über einen Kraftspeicher am Arbeitskolben abgestütztes Bremselement geführt ist, welches eine der Flächen des Dämfpungsspaltes bildet, um eine definierbare Abbremsung der Ventilschließbewegung auch unter Berücksichtgung von betriebs- oder verschleißbedingten Dimensionsänderungen im Bereich des Ventils zu gewährleisten.Of course, the present invention of the earth is not limited to the exemplary embodiment shown. Rather, what is essential is the general idea of the invention, according to which the working piston is provided with a blind hole, in which a braking element, which is supported by an energy accumulator on the working piston, is formed and forms one of the surfaces of the damping gap in order to brake the valve closing movement in a definable manner, also taking operational or wear-related factors into account To ensure dimensional changes in the area of the valve.

Claims (8)

1. A device for the hydraulic control of reciprocating valves on piston engines where the opening movement s transmitted through a hydraulic chamber (3) and a working piston (4) directly to the valve (7) and the closing movement is triggered by a force-storage element (22) acting upon the valve (7), while for the fluid then displaced by the working piston (4) a damping gap (19) which is formed by the working piston (4) and a non-displaceable wall (15) of the hydraulic chamber (3) is provided, characterised in that the working piston (4) is provided with a blind hole in which there is guided a brake element (8) supported through a force-storage means (9) on the working piston (4) and displaceable in the direction of movement of the working piston which brake element forms one of the surfaces of the damping gap.
2. A device according to Claim 1, characterised in that the brake element (8) in the region of the damping gap (19) and/or the counter-surface (13) operative in the formation of the damping gap has a profile differing from the cylindrical form.
3. A device according to Claim 1 or 2, characterised in that the brake element (8) is of substantially cylindrical form.
4. A device according to any one of the preceding Claims characterised in that the brake element (8) is made hollow and, together with the blind hole, forms a hydraulic chamber (10) which is connected through at least one constricted opening (11) with the hydraulic chamber (3).
5. A device according to any one of the preceding Claims, characterised in that the element forming the effective counter-surface is made as an orifice plate (13) mounted movably outside the working piston (4) and supportable on stops.
6. A device according to Claim 5, characterised in that the surface of the orifice plate (13) outside the region of the damping gap is provided with through-holes (16).
7. A device according to any one of the preceding Claims, characterised in that, in the brake element (8) of hollow formation, there is provided a constricted bore (23) which connects the hydraulic chamber (10) with the part-hydraulic chamber (18) formed by the working piston (4) and the orifice plate (13).
8. A device according to one of the preceding Claims, characterised in that a leakage bore (24) issuing from the blind hole is provided, the exit opening of which bore lies on a side of the working piston (4) remote from the hydraulic chamber (3) and the entry opening (25) of which bore is laid open or blocked by the brake element (8) in dependence upon the forces acting upon it.
EP87110729A 1986-07-29 1987-07-24 Hydraulic valve control device Expired - Lifetime EP0255668B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3625652 1986-07-29
DE3625652 1986-07-29

Publications (3)

Publication Number Publication Date
EP0255668A2 EP0255668A2 (en) 1988-02-10
EP0255668A3 EP0255668A3 (en) 1988-03-23
EP0255668B1 true EP0255668B1 (en) 1990-01-03

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ID=6306228

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Application Number Title Priority Date Filing Date
EP87110729A Expired - Lifetime EP0255668B1 (en) 1986-07-29 1987-07-24 Hydraulic valve control device

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EP (1) EP0255668B1 (en)
DE (1) DE3761320D1 (en)
ES (1) ES2012474B3 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01134018A (en) * 1987-11-19 1989-05-26 Honda Motor Co Ltd Valve system for internal combustion engine
DE3833459A1 (en) * 1988-10-01 1990-04-05 Audi Ag Hydraulic valve gear for an internal combustion engine
AT410696B (en) 1999-09-22 2003-06-25 Jenbacher Ag VALVE DRIVE FOR A VALVE OF A COMBUSTION ENGINE
DE102006012067B4 (en) * 2006-03-16 2016-03-24 Volkswagen Ag Hydraulic valve actuating device for a gas exchange valve
DE102016219227A1 (en) * 2016-10-05 2018-04-05 Schaeffler Technologies AG & Co. KG Gas exchange valve drive with a damper chamber connected to a pressure chamber via a throttle
DE102017113783A1 (en) 2017-06-21 2018-12-27 Man Truck & Bus Ag Power transmission device

Family Cites Families (4)

* 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.
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
DE3511819A1 (en) * 1985-03-30 1986-10-09 Robert Bosch Gmbh, 7000 Stuttgart VALVE CONTROL DEVICE

Also Published As

Publication number Publication date
ES2012474B3 (en) 1990-04-01
DE3761320D1 (en) 1990-02-08
EP0255668A3 (en) 1988-03-23
EP0255668A2 (en) 1988-02-10

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