EP2392789A1 - Electrohydraulic valve control - Google Patents

Electrohydraulic valve control Download PDF

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Publication number
EP2392789A1
EP2392789A1 EP11163107A EP11163107A EP2392789A1 EP 2392789 A1 EP2392789 A1 EP 2392789A1 EP 11163107 A EP11163107 A EP 11163107A EP 11163107 A EP11163107 A EP 11163107A EP 2392789 A1 EP2392789 A1 EP 2392789A1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
hydraulic valve
pressure
connection
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
EP11163107A
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German (de)
French (fr)
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EP2392789B1 (en
Inventor
Andreas Kufner
Michael Berger
Calin Petru Itoafa
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2392789A1 publication Critical patent/EP2392789A1/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
    • 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
    • F01L9/14—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 the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve

Definitions

  • the variability of the timing and the maximum stroke of the gas exchange valve is achieved in that a partial volume of acting as a so-called hydraulic linkage pressure chamber is continuously adjustable with open first hydraulic valve in the pressure relief chamber and accordingly the camshaft predetermined cam lift completely, partially or even not transferred to the gas exchange valve.
  • the present invention is based on the object to provide a valve control of the type mentioned in an alternative embodiment.
  • the second hydraulic valve should be arranged in the control line, that in case of incorrectly open first hydraulic valve, the connection from the pressure chamber to the hydraulic medium supply made and the connection is interrupted by the hydraulic fluid supply to the pressure relief space.
  • connection from the hydraulic fluid supply remains with the first hydraulic valve is independent of the switching position of the second hydraulic valve.
  • the tracking of leakage balancing hydraulic fluid from the hydraulic fluid supply in the pressure chamber is therefore not affected by the switching position of the second hydraulic valve. Consequently, the bypass line required in the cited prior art, which bypasses the two hydraulic valves connected in series there downstream of the hydraulic fluid supply and produces a direct connection controlled by a check valve from the hydraulic fluid supply to the pressure chamber, can be dispensed with.
  • the second hydraulic valve is also electrically energized, unlike the first hydraulic valve, however, be designed to be normally closed, in order to ensure the necessary emergency running properties of the internal combustion engine in the event of a power failure at both hydraulic valves.
  • the second hydraulic valve can also be provided in hydraulic or pneumatic pressure-actuated design and the two variants without pressure open or unpressurized closed.
  • the pneumatic valve design can be particularly advantageous in marine engines, which are equipped for starting the engine with a compressed air supply.
  • a manually operable second hydraulic valve can also be used.
  • FIG. 1 shows the essential components of an electro-hydraulic valve control 1 according to the invention for the variable actuation of a gas exchange valve 2 of an internal combustion engine based on a hydraulic circuit diagram. Shown are a master piston 3, which is driven by a cam 4 of a camshaft, and a slave piston 5, which drives the spring-loaded in the closing direction gas exchange valve 2.
  • the master piston 3 and the slave piston 5 define a hydraulic pressure chamber 6, which is connected via a control line 7 with a hydraulic pressure relief chamber 8 in the form of a spring-loaded pressure accumulator.
  • the control line 7 is connected by means of a check valve 9 with a hydraulic fluid supply 10 of the internal combustion engine and in the present case with the lubricant supply.
  • the check valve 9 is a ball check valve which opens toward the control line 7.
  • the variability of the valve actuation based on the correspondingly variable hydraulic fluid volume of the pressure chamber 6 extends maximum within the limits Opening stroke of the gas exchange valve 2 on the one hand, when the first hydraulic valve 11 during the entire stroke phase of the master piston 3 is in the closed position, and complete shutdown of the gas exchange valve 2 on the other hand, when the first hydraulic valve 11 is at least to the maximum elevation of the master piston 3 in the open position.
  • the valve control 1 comprises a second hydraulic valve 12, during the normal, ie error-free operation of the valve control 1 is open.
  • the run-flat operation of the internal combustion engine based on the shift position of the second hydraulic valve 12 is initiated by the second hydraulic valve 12 closing after detection of the incorrectly open first hydraulic valve 11, so that the hydraulic medium pressure forming in the pressure chamber 6 can no longer relieve pressure in the pressure accumulator 8.
  • the stroke predetermined by the master piston 3 is then completely transferred to the gas exchange valve 2 in accordance with the maximum opening stroke mentioned at the beginning.
  • the arrangement of the second hydraulic valve 12 in the control line 7 is such that the closed during the emergency operation second hydraulic valve 12 interrupts the connections from the first hydraulic valve 11 and from the hydraulic fluid supply 10 to the pressure accumulator 8.
  • the connection of the hydraulic fluid supply 10 with the pressure chamber 6 is maintained to compensate for operational hydraulic leaks from the pressure chamber 6.
  • the second hydraulic valve 12 is according to its symbolic representation of an electrically energized 2/2-way valve in the normally closed version. During normal operation of the valve control 1, the second hydraulic valve 12 is energized to be permanently open be and allow the infinitely adjustable Abregel hydraulic fluid from the pressure chamber 6 in the pressure accumulator 8.
  • FIGS. 2 to 4 Alternative embodiments of the second hydraulic valve are in the FIGS. 2 to 4 represented symbolically.
  • FIG. 2 shows a pressure-operated 2/2-way valve 212 in pressureless open design.
  • FIG. 3 shows a pressure-operated 2/2-way valve 312 in pressureless closed execution.
  • FIG. 4 shows a manually operated 2/2-way valve 412.
  • the switching speed of the second hydraulic valve 12 can be made significantly lower requirements than the first hydraulic valve 11. This is due to the fact that the second hydraulic valve 12 only has to switch from the open position to the closed position once at the start of the emergency operation. Accordingly, the second hydraulic valve 12 can be designed substantially more cost-effectively than the significantly faster switching first hydraulic valve 11.

Abstract

The controller (1) has an electrically energizable hydraulic valve (11) arranged in a control line (7), where the valve forms a connection from a pressure chamber (6) to a pressure relief chamber (8) when the valve is in a non-energized state, and interrupts the connection when the valve is in an energized state. Another valve (12) is arranged in the line such that the connection is formed from the pressure chamber to a hydraulic fluid supply (10), and connection from the fluid supply to the pressure relief chamber is interrupted when an error occurs during opening the former valve.

Description

Die Erfindung betrifft eine elektrohydraulische Ventilsteuerung zur variablen Betätigung eines Gaswechselventils einer Brennkraftmaschine, umfassend

  • einen von einem Nocken angetriebenen Geberkolben,
  • einen das Gaswechselventil antreibenden Nehmerkolben,
  • einen von dem Geberkolben und dem Nehmerkolben begrenzten Druckraum mit veränderlichem Volumen,
  • einen Druckentlastungsraum, der mit dem Druckraum über eine Steuerleitung verbindbar ist, die mittels eines zur Steuerleitung hin öffnenden Sperrventils mit der Hydraulikmittelversorgung der Brennkraftmaschine verbunden ist,
  • ein elektrisch bestrombares erstes Hydraulikventil, das in der Steuerleitung angeordnet ist und das die Verbindung vom Druckraum mit dem Druckentlastungsraum im unbestromten Zustand herstellt und im bestromten Zustand unterbricht,
  • und ein zweites Hydraulikventil, das in der Steuerleitung angeordnet ist und bei fehlerhaft offenem ersten Hydraulikventil die Verbindung vom Druckraum mit dem Druckentlastungsraum unterbricht.
The invention relates to an electro-hydraulic valve control for the variable actuation of a gas exchange valve of an internal combustion engine, comprising
  • a master piston driven by a cam,
  • a slave piston driving the gas exchange valve,
  • one of the master piston and the slave piston limited pressure chamber with variable volume,
  • a pressure relief space, which is connectable to the pressure chamber via a control line, which is connected by means of a control line opening towards the check valve with the hydraulic fluid supply of the internal combustion engine,
  • an electrically energizable first hydraulic valve, which is arranged in the control line and which establishes the connection from the pressure chamber to the pressure relief chamber in the de-energized state and interrupts in the energized state,
  • and a second hydraulic valve, which is arranged in the control line and interrupts the connection from the pressure chamber to the pressure relief space when the first hydraulic valve is open incorrectly.

Hintergrund der ErfindungBackground of the invention

Bei derartigen Ventilsteuerungen wird die Variabilität der Steuerzeiten und des Maximalhubs des Gaswechselventils dadurch erzielt, dass ein Teilvolumen des als so genanntes hydraulisches Gestänge wirkenden Druckraums bei geöffnetem ersten Hydraulikventil stufenlos in den Druckentlastungsraum abregelbar ist und dementsprechend der von der Nockenwelle vorgegebene Nockenhub vollständig, teilweise oder gar nicht auf das Gaswechselventil übertragen wird.In such valve controls, the variability of the timing and the maximum stroke of the gas exchange valve is achieved in that a partial volume of acting as a so-called hydraulic linkage pressure chamber is continuously adjustable with open first hydraulic valve in the pressure relief chamber and accordingly the camshaft predetermined cam lift completely, partially or even not transferred to the gas exchange valve.

Eine wesentliche Verantwortung für die Funktionssicherheit der Ventilsteuerung übernimmt folglich das erste Hydraulikventil, dessen Schaltfunktion unter allen Betriebsbedingungen der Brennkraftmaschine präzise und reproduzierbar gewährleistet sein muss. Das stromlos geöffnete erste Hydraulikventil birgt jedoch das nie vollständig auszuschließende Risiko einer Fehlfunktion, bei der es nicht mehr schließt. Die Folge ist eine unkontrollierte Stilllegung des oder der zugehörigen Gaswechselventile.An essential responsibility for the reliability of the valve control consequently assumes the first hydraulic valve whose switching function must be ensured under all operating conditions of the internal combustion engine precise and reproducible. However, the normally open first hydraulic valve harbors the risk of a malfunction that can never be completely ruled out, in which it no longer closes. The result is an uncontrolled shutdown of the associated gas exchange valves or.

Im Hinblick auf ausreichende Notlaufeigenschaften der Brennkraftmaschine (Limp-Home-Mode) ist es in der gattungsgemäßen DE 10 2008 049 181 A1 vorgeschlagen, das Hydrauliksystem der Ventilsteuerung um ein zweites Hydraulikventil zu ergänzen, das im Normalbetrieb der Ventilsteuerung geöffnet ist und im Falle der Fehlfunktion schließt, um die Verbindung vom Druckraum mit dem Druckentlastungsraum zu unterbrechen. Durch diese Maßnahme wird auch bei permanent offen stehendem ersten Hydraulikventil - beispielsweise aufgrund einer elektrischen Stromunterbrechung oder eines mechanischen Defekts am ersten Hydraulikventil - ein für die Hubübertragung auf das Gaswechselventil ausreichender Druckaufbau im Druckraum ermöglicht, indem das zweite Hydraulikventil während des Notlaufbetriebs geschlossen ist und eine Druckentlastung des Druckraums verhindert.With regard to sufficient emergency running properties of the internal combustion engine (limp home mode), it is in the generic DE 10 2008 049 181 A1 proposed to supplement the hydraulic system of the valve control by a second hydraulic valve, which is open during normal operation of the valve control and closes in case of malfunction, to interrupt the connection from the pressure chamber to the pressure relief space. By this measure, even with permanently open first hydraulic valve - for example, due to an electrical current interruption or a mechanical defect on the first hydraulic valve - sufficient for Hubübertragung on the gas exchange valve pressure build-up in the pressure chamber allows by the second hydraulic valve is closed during emergency operation and a pressure relief the pressure chamber prevented.

Aufgabe der ErfindungObject of the invention

Der vorliegenden Erfindung liegt die Aufgabe zu Grunde, eine Ventilsteuerung der eingangs genannten Art in einer alternativen Ausgestaltung anzugeben.The present invention is based on the object to provide a valve control of the type mentioned in an alternative embodiment.

Zusammenfassung der ErfindungSummary of the invention

Die Lösung dieser Aufgabe ergibt sich aus den kennzeichnenden Merkmalen des Anspruchs 1, während vorteilhafte Weiterbildungen und Ausgestaltungen der Erfindung den Unteransprüchen entnehmbar sind. Demnach soll das zweite Hydraulikventil so in der Steuerleitung angeordnet sein, dass bei fehlerhaft offenem ersten Hydraulikventil die Verbindung vom Druckraum mit der Hydraulikmittelversorgung hergestellt und die Verbindung von der Hydraulikmittelversorgung mit dem Druckentlastungsraum unterbrochen ist.The solution of this problem arises from the characterizing features of claim 1, while advantageous developments and refinements of the invention are the dependent claims can be removed. Accordingly, the second hydraulic valve should be arranged in the control line, that in case of incorrectly open first hydraulic valve, the connection from the pressure chamber to the hydraulic medium supply made and the connection is interrupted by the hydraulic fluid supply to the pressure relief space.

Mit anderen Worten bleibt die Verbindung von der Hydraulikmittelversorgung mit dem ersten Hydraulikventil unabhängig von der Schaltstellung des zweiten Hydraulikventils bestehen. Das Nachführen von Leckage ausgleichendem Hydraulikmittel aus der Hydraulikmittelversorgung in den Druckraum wird dementsprechend nicht durch die Schaltstellung des zweiten Hydraulikventils beeinträchtigt. Folglich kann die im eingangs zitierten Stand der Technik erforderliche Bypassleitung, die die beiden dort stromabwärts der Hydraulikmittelversorgung in Reihe geschalteten Hydraulikventile umgeht und eine mittels eines Rückschlagventils gesteuerte, direkte Verbindung von der Hydraulikmittelversorgung mit dem Druckraum herstellt, entfallen.In other words, the connection from the hydraulic fluid supply remains with the first hydraulic valve is independent of the switching position of the second hydraulic valve. The tracking of leakage balancing hydraulic fluid from the hydraulic fluid supply in the pressure chamber is therefore not affected by the switching position of the second hydraulic valve. Consequently, the bypass line required in the cited prior art, which bypasses the two hydraulic valves connected in series there downstream of the hydraulic fluid supply and produces a direct connection controlled by a check valve from the hydraulic fluid supply to the pressure chamber, can be dispensed with.

In Weiterbildung der Erfindung soll das zweite Hydraulikventil ebenfalls elektrisch bestrombar, anders als das erste Hydraulikventil jedoch stromlos geschlossen ausgebildet sein, um auch im Falle eines Stromausfalls an beiden Hydraulikventilen die erforderlichen Notlaufeigenschaften der Brennkraftmaschine zu gewährleisten.In a further development of the invention, the second hydraulic valve is also electrically energized, unlike the first hydraulic valve, however, be designed to be normally closed, in order to ensure the necessary emergency running properties of the internal combustion engine in the event of a power failure at both hydraulic valves.

Als Alternative kann das zweite Hydraulikventil auch in hydraulisch oder pneumatisch druckbetätigbarer Ausführung und den beiden Varianten drucklos offen oder drucklos geschlossen vorgesehen sein. Die pneumatische Ventilausführung kann insbesondere bei Schiffsmotoren vorteilhaft sein, die für den Motorstart mit einer Druckluftversorgung ausgestattet sind. In diesem Anwendungsfall kann zudem auch ein manuell betätigbares zweites Hydraulikventil zum Einsatz kommen.As an alternative, the second hydraulic valve can also be provided in hydraulic or pneumatic pressure-actuated design and the two variants without pressure open or unpressurized closed. The pneumatic valve design can be particularly advantageous in marine engines, which are equipped for starting the engine with a compressed air supply. In this case, a manually operable second hydraulic valve can also be used.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus den Zeichnungen, in denen Ausführungsbeispiele der Erfindung schematisch dargestellt sind. Es zeigen:

Figur 1
einen hydraulischen Schaltplan einer erfindungsgemäßen elektrohydraulischen Ventilsteuerung;
Figur 2
ein zweites Hydraulikventil in druckbetätigbarer und drucklos offener Ausführung,
Figur 3
ein zweites Hydraulikventil in druckbetätigbarer und drucklos geschlossener Ausführung und
Figur 4
ein zweites Hydraulikventil in manuell betätigbarer Ausführung.
Further features of the invention will become apparent from the following description and from the drawings, in which embodiments of the invention are shown schematically. Show it:
FIG. 1
a hydraulic circuit diagram of an electro-hydraulic valve control according to the invention;
FIG. 2
a second hydraulic valve in pressure-actuated and pressure-less open Execution,
FIG. 3
a second hydraulic valve in pressure-actuated and pressure-free closed version and
FIG. 4
a second hydraulic valve in manually operable version.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Figur 1 zeigt die wesentlichen Komponenten einer erfindungsgemäßen elektrohydraulischen Ventilsteuerung 1 zur variablen Betätigung eines Gaswechselventils 2 einer Brennkraftmaschine anhand eines hydraulischen Schaltplans. Dargestellt sind ein Geberkolben 3, der von einem Nocken 4 einer Nockenwelle angetrieben ist, und ein Nehmerkolben 5, der das in Schließrichtung federkraftbeaufschlagte Gaswechselventil 2 antreibt. Der Geberkolben 3 und der Nehmerkolben 5 begrenzen einen hydraulischen Druckraum 6, der über eine Steuerleitung 7 mit einem hydraulischen Druckentlastungsraum 8 in Form eines federbelasteten Druckspeichers verbunden ist. Die Steuerleitung 7 ist mittels eines Sperrventils 9 mit einer Hydraulikmittelversorgung 10 der Brennkraftmaschine und vorliegend mit deren Schmiermittelversorgung verbunden. Bei dem Sperrventil 9 handelt es sich um ein zur Steuerleitung 7 hin öffnendes Kugelrückschlagventil. FIG. 1 shows the essential components of an electro-hydraulic valve control 1 according to the invention for the variable actuation of a gas exchange valve 2 of an internal combustion engine based on a hydraulic circuit diagram. Shown are a master piston 3, which is driven by a cam 4 of a camshaft, and a slave piston 5, which drives the spring-loaded in the closing direction gas exchange valve 2. The master piston 3 and the slave piston 5 define a hydraulic pressure chamber 6, which is connected via a control line 7 with a hydraulic pressure relief chamber 8 in the form of a spring-loaded pressure accumulator. The control line 7 is connected by means of a check valve 9 with a hydraulic fluid supply 10 of the internal combustion engine and in the present case with the lubricant supply. The check valve 9 is a ball check valve which opens toward the control line 7.

Ein in der Steuerleitung 7 angeordnetes erstes Hydraulikventil 11, das als schnell schaltendes, elektrisch ansteuerbares 2/2-Wegeventil in stromlos geöffneter Bauweise ausgeführt ist, sorgt in Abhängigkeit von dessen Bestromungszustand dafür, dass die Verbindung vom Druckraum 6 mit dem Druckspeicher 8 hergestellt oder unterbrochen ist. Folglich wird ein Hydraulikmittelfluss durch die Steuerleitung 7 hindurch freigegeben oder gesperrt, wobei während der Betätigung des Geberkolbens 3 ein stufenlos einstellbares Teilvolumen aus dem Druckraum 6 in den Druckspeicher 8 ausgeschoben wird. Die auf dem dementsprechend veränderlichen Hydraulikmittelvolumen des Druckraums 6 basierende Variabilität der Ventilbetätigung erstreckt sich innerhalb der Grenzen maximalen Öffnungshubs des Gaswechselventils 2 einerseits, wenn sich das erste Hydraulikventil 11 während der gesamten Hubphase des Geberkolbens 3 in Schließstellung befindet, und vollständiger Abschaltung des Gaswechselventils 2 andererseits, wenn sich das erste Hydraulikventil 11 zumindest bis zur Maximalerhebung des Geberkolbens 3 in Offenstellung befindet.A arranged in the control line 7 first hydraulic valve 11, which is designed as a fast-switching, electrically controllable 2/2-way valve in normally open design, depending on the Bestromungszustand ensures that the connection of the pressure chamber 6 to the accumulator 8 or interrupted is. Consequently, a hydraulic fluid flow is released or blocked by the control line 7, wherein during the actuation of the master piston 3, a continuously adjustable partial volume from the pressure chamber 6 is pushed into the pressure accumulator 8. The variability of the valve actuation based on the correspondingly variable hydraulic fluid volume of the pressure chamber 6 extends maximum within the limits Opening stroke of the gas exchange valve 2 on the one hand, when the first hydraulic valve 11 during the entire stroke phase of the master piston 3 is in the closed position, and complete shutdown of the gas exchange valve 2 on the other hand, when the first hydraulic valve 11 is at least to the maximum elevation of the master piston 3 in the open position.

Für den Fall, dass das erste Hydraulikventil 11 während des Betriebs der Brennkraftmaschine fehlerhaft offen stehen bleibt - wie oben erwähnt, kommt als Ursache hierfür insbesondere eine unterbrochene Stromversorgung des ersten Hydraulikventils 11 in Betracht - und dies zur vollständigen Stilllegung des Gaswechselventils 2 bei entsprechend inakzeptablem Betriebsverhalten der Brennkraftmaschine führen würde, umfasst die Ventilsteuerung 1 ein zweites Hydraulikventil 12, das während des normalen, d.h. fehlerfreien Betriebs der Ventilsteuerung 1 geöffnet ist. Der auf der Schaltstellung des zweiten Hydraulikventils 12 basierende Notlaufbetrieb der Brennkraftmaschine wird dadurch eingeleitet, dass das zweite Hydraulikventil 12 nach Detektion des fehlerhaft offen stehenden ersten Hydraulikventils 11 schließt, so dass sich der im Druckraum 6 ausbildende Hydraulikmitteldruck nicht mehr in den Druckspeicher 8 entlasten kann. Im idealen Falle eines vollständig inkompressiblen und leckagedichten Druckraums 6 wird dann der vom Geberkolben 3 vorgegebene Hub entsprechend dem eingangs genannten maximalen Öffnungshub vollständig auf das Gaswechselventil 2 übertragen.In the event that the first hydraulic valve 11 during the operation of the internal combustion engine faulty remains open - as mentioned above, as the cause of this particular interrupted power supply of the first hydraulic valve 11 into consideration - and this to complete decommissioning of the gas exchange valve 2 in accordance with unacceptable performance would lead the internal combustion engine, the valve control 1 comprises a second hydraulic valve 12, during the normal, ie error-free operation of the valve control 1 is open. The run-flat operation of the internal combustion engine based on the shift position of the second hydraulic valve 12 is initiated by the second hydraulic valve 12 closing after detection of the incorrectly open first hydraulic valve 11, so that the hydraulic medium pressure forming in the pressure chamber 6 can no longer relieve pressure in the pressure accumulator 8. In the ideal case of a completely incompressible and leak-tight pressure chamber 6, the stroke predetermined by the master piston 3 is then completely transferred to the gas exchange valve 2 in accordance with the maximum opening stroke mentioned at the beginning.

Die Anordnung des zweiten Hydraulikventils 12 in der Steuerleitung 7 ist derart, dass das während des Notlaufbetriebs geschlossene zweite Hydraulikventil 12 die Verbindungen vom ersten Hydraulikventil 11 und von der Hydraulikmittelversorgung 10 mit dem Druckspeicher 8 unterbricht. Hingegen bleibt die Verbindung von der Hydraulikmittelversorgung 10 mit dem Druckraum 6 erhalten, um betriebsbedingte Hydraulikmittelleckagen aus dem Druckraum 6 auszugleichen. Bei dem zweiten Hydraulikventil 12 handelt es sich gemäß seiner symbolhaften Darstellung um ein elektrisch bestrombares 2/2-Wegeventil in stromlos geschlossener Ausführung. Während des Normalbetriebs der Ventilsteuerung 1 wird das zweite Hydraulikventil 12 bestromt, um permanent geöffnet zu sein und das stufenlos einstellbare Abregeln von Hydraulikmittel aus dem Druckraum 6 in den Druckspeicher 8 zu ermöglichen.The arrangement of the second hydraulic valve 12 in the control line 7 is such that the closed during the emergency operation second hydraulic valve 12 interrupts the connections from the first hydraulic valve 11 and from the hydraulic fluid supply 10 to the pressure accumulator 8. On the other hand, the connection of the hydraulic fluid supply 10 with the pressure chamber 6 is maintained to compensate for operational hydraulic leaks from the pressure chamber 6. The second hydraulic valve 12 is according to its symbolic representation of an electrically energized 2/2-way valve in the normally closed version. During normal operation of the valve control 1, the second hydraulic valve 12 is energized to be permanently open be and allow the infinitely adjustable Abregel hydraulic fluid from the pressure chamber 6 in the pressure accumulator 8.

Alternative Ausgestaltungen des zweiten Hydraulikventils sind in den Figuren 2 bis 4 symbolhaft dargestellt.Alternative embodiments of the second hydraulic valve are in the FIGS. 2 to 4 represented symbolically.

Figur 2 zeigt ein druckbetätigtes 2/2-Wegeventil 212 in drucklos offener Ausführung. FIG. 2 shows a pressure-operated 2/2-way valve 212 in pressureless open design.

Figur 3 zeigt ein druckbetätigtes 2/2-Wegeventil 312 in drucklos geschlossener Ausführung. FIG. 3 shows a pressure-operated 2/2-way valve 312 in pressureless closed execution.

Figur 4 zeigt ein manuell betätigtes 2/2-Wegeventil 412. FIG. 4 shows a manually operated 2/2-way valve 412.

An die Umschaltgeschwindigkeit des zweiten Hydraulikventils 12 können deutlich geringere Anforderungen als an das erste Hydraulikventil 11 gestellt werden. Dies liegt darin begründet, dass das zweite Hydraulikventil 12 lediglich einmal zu Beginn des Notlaufbetriebs von der Offenstellung in die Schließstellung umschalten muss. Dementsprechend kann das zweite Hydraulikventil 12 wesentlich kostengünstiger als das deutlich schneller schaltende erste Hydraulikventil 11 ausgeführt sein.At the switching speed of the second hydraulic valve 12 can be made significantly lower requirements than the first hydraulic valve 11. This is due to the fact that the second hydraulic valve 12 only has to switch from the open position to the closed position once at the start of the emergency operation. Accordingly, the second hydraulic valve 12 can be designed substantially more cost-effectively than the significantly faster switching first hydraulic valve 11.

Bezugszahlenreference numerals

11
Ventilsteuerungvalve control
22
GaswechselventilGas exchange valve
33
Geberkolbenmaster piston
44
Nockencam
55
Nehmerkolbenslave piston
66
Druckraumpressure chamber
77
Steuerleitungcontrol line
88th
Druckentlastungsraum / DruckspeicherPressure relief chamber / pressure accumulator
99
Sperrventilcheck valve
1010
HydraulikmittelversorgungHydraulic medium supply
1111
erstes Hydraulikventilfirst hydraulic valve
1212
zweites Hydraulikventilsecond hydraulic valve

Claims (5)

Elektrohydraulische Ventilsteuerung (1) zur variablen Betätigung eines Gaswechselventils (2) einer Brennkraftmaschine, umfassend ■ einen von einem Nocken (4) angetriebenen Geberkolben (3), ■ einen das Gaswechselventil (2) antreibenden Nehmerkolben (5), ■ einen von dem Geberkolben (3) und dem Nehmerkolben (5) begrenzten Druckraum (6) mit veränderlichem Volumen, ■ einen Druckentlastungsraum (8), der mit dem Druckraum (6) über eine Steuerleitung (7) verbindbar ist, die mittels eines zur Steuerleitung (7) hin öffnenden Sperrventils (9) mit der Hydraulikmittelversorgung (10) der Brennkraftmaschine verbunden ist, ■ ein elektrisch bestrombares erstes Hydraulikventil (11), das in der Steuerleitung (7) angeordnet ist und das die Verbindung vom Druckraum (6) mit dem Druckentlastungsraum (8) im unbestromten Zustand herstellt und im bestromten Zustand unterbricht, ■ und ein zweites Hydraulikventil (12, 212, 312, 412), das in der Steuerleitung (7) angeordnet ist und bei fehlerhaft offenem ersten Hydraulikventil (11) die Verbindung vom Druckraum (6) mit dem Druckentlastungsraum (8) unterbricht,
dadurch gekennzeichnet, dass das zweite Hydraulikventil (12, 212, 312, 412) so in der Steuerleitung (7) angeordnet ist, dass bei fehlerhaft offenem ersten Hydraulikventil (11) die Verbindung vom Druckraum (6) mit der Hydraulikmittelversorgung (10) hergestellt und die Verbindung von der Hydraulikmittelversorgung (10) mit dem Druckentlastungsraum (8) unterbrochen ist. Electrohydraulic valve control (1) for the variable actuation of a gas exchange valve (2) of an internal combustion engine, comprising ■ a master piston (3) driven by a cam (4), ■ a slave piston (5) driving the gas exchange valve (2), ■ a pressure chamber (6) of variable volume bounded by the master piston (3) and the slave piston (5), ■ a pressure relief chamber (8) which is connectable to the pressure chamber (6) via a control line (7) which is connected to the hydraulic medium supply (10) of the internal combustion engine by means of a check valve (9) opening towards the control line (7), ■ an electrically energizable first hydraulic valve (11), which is arranged in the control line (7) and which establishes the connection from the pressure chamber (6) to the pressure relief chamber (8) in the de-energized state and interrupts in the energized state, ■ and a second hydraulic valve (12, 212, 312, 412) which is arranged in the control line (7) and interrupts the connection from the pressure chamber (6) to the pressure relief chamber (8) when the first hydraulic valve (11) is incorrectly opened,
characterized in that the second hydraulic valve (12, 212, 312, 412) is arranged in the control line (7), that when incorrectly open first hydraulic valve (11) the connection from the pressure chamber (6) with the hydraulic fluid supply (10) and the connection from the hydraulic fluid supply (10) to the pressure relief chamber (8) is interrupted. Elektrohydraulische Ventilsteuerung (1) nach Anspruch 1, dadurch gekennzeichnet, dass das zweite Hydraulikventil (12) elektrisch bestrombar und stromlos geschlossen ausgebildet ist.Electrohydraulic valve control (1) according to claim 1, characterized in that the second hydraulic valve (12) is formed electrically energized and normally closed. Elektrohydraulische Ventilsteuerung (1) nach Anspruch 1, dadurch gekennzeichnet, dass das zweite Hydraulikventil (212) druckbetätigbar und drucklos offen ausgebildet ist.Electrohydraulic valve control (1) according to claim 1, characterized in that the second hydraulic valve (212) is formed druckbetätigbar and open without pressure. Elektrohydraulische Ventilsteuerung (1) nach Anspruch 1, dadurch gekennzeichnet, dass das zweite Hydraulikventil (312) druckbetätigbar und drucklos geschlossen ausgebildet ist.Electrohydraulic valve control (1) according to claim 1, characterized in that the second hydraulic valve (312) is formed druckbetätigbar and depressurized closed. Elektrohydraulische Ventilsteuerung (1) nach Anspruch 1, dadurch gekennzeichnet, dass das zweite Hydraulikventil (412) manuell betätigbar ausgebildet ist.Electrohydraulic valve control (1) according to claim 1, characterized in that the second hydraulic valve (412) is designed to be manually operable.
EP11163107.3A 2010-06-01 2011-04-20 Electrohydraulic valve control Not-in-force EP2392789B1 (en)

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DE102010022346A DE102010022346A1 (en) 2010-06-01 2010-06-01 Electrohydraulic valve control

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US9863293B2 (en) 2012-08-01 2018-01-09 GM Global Technology Operations LLC Variable valve actuation system including an accumulator and a method for controlling the variable valve actuation system
DE102012221354A1 (en) 2012-11-22 2013-01-24 Schaeffler Technologies AG & Co. KG Hydraulic unit for cylinder head of internal combustion engine with hydraulically variable gas exchange valve train, has hydraulic connection, which is provided between high pressure chamber and medium-pressure chamber
DE102015216866A1 (en) 2015-09-03 2017-03-09 Schaeffler Technologies AG & Co. KG Electrohydraulic valve control with variable valve lift and heat engine

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US20110290204A1 (en) 2011-12-01
EP2392789B1 (en) 2016-06-08
DE102010022346A1 (en) 2011-12-01

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