EP2329116B1 - Electrohydraulic valve controller - Google Patents

Electrohydraulic valve controller Download PDF

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Publication number
EP2329116B1
EP2329116B1 EP09782988.1A EP09782988A EP2329116B1 EP 2329116 B1 EP2329116 B1 EP 2329116B1 EP 09782988 A EP09782988 A EP 09782988A EP 2329116 B1 EP2329116 B1 EP 2329116B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
hydraulic valve
pressure relief
chamber
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.)
Not-in-force
Application number
EP09782988.1A
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German (de)
French (fr)
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EP2329116A1 (en
Inventor
Michael Haas
Nicola Morelli
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2329116A1 publication Critical patent/EP2329116A1/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
    • 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
    • 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
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/12—Fail safe operation

Definitions

  • Such a valve control goes out of the class considered as generic EP 0 931 912 A2 out.
  • 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 the hydraulic valve open in the pressure relief chamber and, accordingly, the predetermined camshaft camshaft completely, partially or not at all to the gas exchange valve is transmitted.
  • a key responsibility for the reliability of the valve control therefore assumes the hydraulic valve whose switching function must be ensured under all operating conditions of the engine precise and reproducible.
  • the present invention is therefore based on the object, a valve control of the type mentioned in such a way that it has a sufficient emergency running even in case of malfunction of the hydraulic valve. This is to be understood that even in run-flat operation sufficient for a successful change of charge of the internal combustion engine valve lift can be generated.
  • valve control should comprise a further hydraulic valve which is arranged in the control line between the hydraulic valve and the pressure relief space and which blocks the hydraulic fluid flow through the control line into the pressure relief space when the hydraulic valve is open incorrectly.
  • the hydraulic valve is formed normally open
  • the further hydraulic valve is also designed to be electrically controlled and normally open.
  • a major advantage of this design is the favorable energy balance of the valve control, since then the additional hydraulic valve would be energized only during emergency operation. Nevertheless, there is also the possibility of providing the further hydraulic valve as a normally closed version and / or instead of selecting electrical control of a hydraulic, pneumatic or mechanical control.
  • the hydraulic valve should be designed much faster switching than the other hydraulic valve. Since can be dispensed with the normal functionality of the valve control during the limited-time emergency operation, the other hydraulic valve can remain permanently closed and thus be designed as a comparatively slow-switching and cost-effective valve.
  • FIGURE shows a hydraulic circuit diagram of an electrohydraulic valve control according to the invention.
  • an electro-hydraulic valve control 1 for the variable actuation of a gas exchange valve 2 of an internal combustion engine are disclosed by means of a hydraulic circuit diagram. Shown are a master piston 3, which is driven by a cam-like cam follower 4 by a cam 5 of a camshaft 6, and a slave piston 7, by means of a valve bridge 8, a pair of identical gas exchange valves 2, i. Inlet or exhaust valves, against the force acting in the closing direction of the valve springs 9 drives.
  • the master piston 3 and the slave piston 7 define a hydraulic pressure chamber 10, which is connected via a control line 11 with a hydraulic pressure relief chamber 12.
  • hydraulic valve 13 which is formed according to the drawn circuit symbol electrically controllable and normally open design ensures that a hydraulic fluid flow through the control line 11 through is released or blocked and accordingly the pressure chamber 10 a variable volume during actuation the master piston 3 has.
  • the continuously variable variability of the valve actuation produced thereby extends within the limits of the maximum opening stroke of the gas exchange valves 2 on the one hand, when the hydraulic valve 13 is in the closed position during the entire stroke phase of the master piston 3, and complete shutdown of the gas exchange valves 2, if the hydraulic valve 13 at least until to the maximum elevation of the master piston 3 is in the open position.
  • the connected to a hydraulic fluid supply 14 of the internal combustion engine and in the present case at the lubricant supply by means of a check valve 15 pressure relief chamber 12 has a spring-loaded pressure accumulator 16 known construction and is for the purpose of balancing leak-induced hydraulic fluid losses from the pressure chamber 10 via a bypass line 17 to the pressure chamber 10 is connected.
  • a non-return valve 18 arranged in the bypass line 17 causes a hydraulic fluid flow to be released through the bypass line 17 into the pressure chamber 10 and blocked in the pressure relief chamber 12.
  • the valve control 1 comprises a further hydraulic valve 19 which is arranged in the control line 11 between the hydraulic valve 13 and the pressure relief chamber 12 and during normal, ie error-free operation of the valve control 1 is open.
  • the further hydraulic valve 19 allows emergency operation of the internal combustion engine.
  • the further hydraulic valve 19 which is also electrically controlled and normally open according to its switching symbol, significantly lower requirements than the hydraulic valve 13 can be made. This is due to the fact that the further hydraulic valve 19 only has to switch from the open position to the closed position once at the beginning of the emergency operation. Accordingly, the further hydraulic valve 19 be executed much cheaper than the much faster switching hydraulic valve 13.

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

Description

Gebiet der ErfindungField of the invention

Die Erfindung betrifft eine elektrohydraulische Ventilsteuerung zur variablen Betätigung eines Gaswechselventils einer Brennkraftmaschine. Die Ventilsteuerung umfasst:

  • ▪ einen von einer Nockenwelle angetriebenen Geberkolben,
  • ▪ einen das Gaswechselventil antreibenden Nehmerkolben,
  • ▪ einen von dem Geberkolben und dem Nehmerkolben begrenzten Druckraum mit veränderlichem Volumen,
  • ▪ einen an eine Hydraulikmittelversorgung der Brennkraftmaschine angeschlossen Druckentlastungsraum,
  • ▪ eine den Druckraum mit dem Druckentlastungsraum verbindende Steuerleitung und ein darin angeordnetes, elektrisch ansteuerbares Hydraulikventil, das einen Hydraulikmittelfluss durch die Steuerleitung freigibt oder sperrt,
  • ▪ eine den Druckraum mit dem Druckentlastungsraum verbindende Bypassleitung und ein darin angeordnetes Rückschlagventil, das einen Hydraulikmittelfluss durch die Bypassleitung in den Druckraum freigibt und in den Druckentlastungsraum sperrt.
The invention relates to an electro-hydraulic valve control for the variable actuation of a gas exchange valve of an internal combustion engine. The valve control includes:
  • ▪ a master piston driven by a camshaft,
  • ▪ a slave piston driving the gas exchange valve,
  • ▪ a pressure chamber of variable volume bounded by the master piston and the slave piston,
  • A pressure relief space connected to a hydraulic fluid supply of the internal combustion engine,
  • A control line connecting the pressure chamber to the pressure relief chamber and an electrically controllable hydraulic valve arranged therein which releases or blocks a hydraulic fluid flow through the control line,
  • ▪ A bypass line connecting the pressure chamber to the pressure relief chamber and a non-return valve arranged therein, which releases a hydraulic fluid flow through the bypass line into the pressure chamber and blocks it into the pressure relief chamber.

Hintergrund der ErfindungBackground of the invention

Eine derartige Ventilsteuerung geht aus der als gattungsbildend betrachteten EP 0 931 912 A2 hervor. Die Variabilität der Steuerzeiten und des Maximalhubs des Gaswechselventils wird dadurch erzielt, dass ein Teilvolumen des als so genanntes hydraulisches Gestänge wirkenden Druckraums bei geöffnetem 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. Eine wesentliche Verantwortung für die Funktionssicherheit der Ventilsteuerung übernimmt folglich das Hydraulikventil, dessen Schaltfunktion unter allen Betriebsbedingungen der Brennkraftmaschine präzise und reproduzierbar gewährleistet sein muss.Such a valve control goes out of the class considered as generic EP 0 931 912 A2 out. 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 the hydraulic valve open in the pressure relief chamber and, accordingly, the predetermined camshaft camshaft completely, partially or not at all to the gas exchange valve is transmitted. A key responsibility for the reliability of the valve control therefore assumes the hydraulic valve whose switching function must be ensured under all operating conditions of the engine precise and reproducible.

Da jedoch ein nicht mehr schließendes Hydraulikventil mit einer Stilllegung des oder der zugehörigen Gaswechselventile einhergeht und eine Fehlfunktion des Hydraulikventils nie vollständig ausgeschlossen werden kann, mangelt es der in der zitierten Druckschrift vorgeschlagenen Ventilsteuerung an Notlaufeigenschaften, die einen zumindest eingeschränkten Weiterbetrieb der Brennkraftmaschine ermöglichen.However, since a no longer closing hydraulic valve associated with a shutdown of the associated gas exchange valves and malfunction of the hydraulic valve can never be completely ruled out, it lacks the valve control proposed in the cited document on emergency running properties that allow at least limited continued operation of the engine.

Aufgabe der ErfindungObject of the invention

Der vorliegenden Erfindung liegt daher die Aufgabe zu Grunde, eine Ventilsteuerung der eingangs genannten Art so fortzubilden, dass diese auch im Falle einer Fehlfunktion des Hydraulikventils eine ausreichende Notlaufeigenschaft aufweist. Hierunter ist zu verstehen, dass auch im Notlaufbetrieb ein für einen erfolgreichen Ladungswechsel der Brennkraftmaschine ausreichender Ventilhub erzeugt werden kann.The present invention is therefore based on the object, a valve control of the type mentioned in such a way that it has a sufficient emergency running even in case of malfunction of the hydraulic valve. This is to be understood that even in run-flat operation sufficient for a successful change of charge of the internal combustion engine valve lift can be generated.

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 die Ventilsteuerung ein weiteres Hydraulikventil umfassen, das in der Steuerleitung zwischen dem Hydraulikventil und dem Druckentlastungsraum angeordnet ist und das bei fehlerhaft offenem Hydraulikventil den Hydraulikmittelfluss durch die Steuerleitung in den Druckentlastungsraum sperrt. Durch diese Maßnahme wird auch bei permanent offen stehendem Hydraulikventil - beispielsweise aufgrund einer elektrischen Stromunterbrechung oder eines mechanischen Defekts am Hydraulikventil - ein für die Hubübertragung auf das Gaswechselventil ausreichender Druckaufbau im Druckraum ermöglicht, indem das weitere Hydraulikventil während des Notlaufbetriebs geschlossen und somit eine Druckentlastung des Druckraums verhindert wird.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 valve control should comprise a further hydraulic valve which is arranged in the control line between the hydraulic valve and the pressure relief space and which blocks the hydraulic fluid flow through the control line into the pressure relief space when the hydraulic valve is open incorrectly. By this measure, even with permanently open hydraulic valve - for example, due to an electrical current interruption or a mechanical failure on the hydraulic valve - sufficient for Hubübertragung on the gas exchange valve pressure build-up in the pressure chamber made possible by the other hydraulic valve during the emergency operation closed and thus a pressure relief of the pressure chamber is prevented.

Für den im Sinne der Erfindung zweckmäßigen Fall, dass das Hydraulikventil stromlos offen ausgebildet ist, kann es vorgesehen sein, dass das weitere Hydraulikventil ebenfalls elektrisch ansteuerbar und stromlos offen ausgebildet ist. Ein wesentlicher Vorteil dieser Auslegung ist die günstige Energiebilanz der Ventilsteuerung, da dann das weitere Hydraulikventil lediglich während des Notlaufbetriebs zu bestromen wäre. Ungeachtet dessen besteht dennoch auch die Möglichkeit, das weitere Hydraulikventil als stromlos geschlossene Ausführung vorzusehen und/oder statt dessen elektrischer Ansteuerung eine hydraulische, pneumatische oder mechanische Ansteuerung zu wählen.For the purposes of the invention expedient case that the hydraulic valve is formed normally open, it may be provided that the further hydraulic valve is also designed to be electrically controlled and normally open. A major advantage of this design is the favorable energy balance of the valve control, since then the additional hydraulic valve would be energized only during emergency operation. Nevertheless, there is also the possibility of providing the further hydraulic valve as a normally closed version and / or instead of selecting electrical control of a hydraulic, pneumatic or mechanical control.

Außerdem soll das Hydraulikventil deutlich schneller schaltend als das weitere Hydraulikventil ausgebildet sein. Da während des zeitlich begrenzten Notlaufbetriebs auf die normale Funktionalität der Ventilsteuerung verzichtet werden kann, kann das weitere Hydraulikventil permanent geschlossen bleiben und folglich als vergleichsweise langsam schaltendes und kostengünstiges Ventil ausgebildet sein.In addition, the hydraulic valve should be designed much faster switching than the other hydraulic valve. Since can be dispensed with the normal functionality of the valve control during the limited-time emergency operation, the other hydraulic valve can remain permanently closed and thus be designed as a comparatively slow-switching and cost-effective valve.

Kurze Beschreibung der ZeichnungShort description of the drawing

Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus der Zeichnung, in der ein Ausführungsbeispiel der Erfindung vereinfacht dargestellt ist. Die einzige Figur zeigt einen hydraulischen Schaltplan einer erfindungsgemäßen elektrohydraulischen Ventilsteuerung.Further features of the invention will become apparent from the following description and from the drawing, in which an embodiment of the invention is shown in simplified form. The single FIGURE shows a hydraulic circuit diagram of an electrohydraulic valve control according to the invention.

Detaillierte Beschreibung der ZeichnungDetailed description of the drawing

In der Figur sind die wesentlichen Komponenten einer erfindungsgemäßen elektrohydraulischen Ventilsteuerung 1 zur variablen Betätigung eines Gaswechselventils 2 einer Brennkraftmaschine anhand eines hydraulischen Schaltplans offenbart. Dargestellt sind ein Geberkolben 3, der mittels eines hebelartigen Nockenfolgers 4 von einem Nocken 5 einer Nockenwelle 6 angetrieben ist, und ein Nehmerkolben 7, der mittels einer Ventilbrücke 8 ein Paar gleichwirkender Gaswechselventile 2, d.h. Einlass- oder Auslassventile, entgegen der Kraft in Schließrichtung wirkender Ventilfedern 9 antreibt. Der Geberkolben 3 und der Nehmerkolben 7 begrenzen einen hydraulischen Druckraum 10, der über eine Steuerleitung 11 mit einem hydraulischen Druckentlastungsraum 12 verbunden ist. Ein in der Steuerleitung 11 angeordnetes Hydraulikventil 13, das gemäß dem eingezeichneten Schaltsymbol elektrisch ansteuerbar und in stromlos offener Bauweise ausgebildet ist, sorgt dafür, dass ein Hydraulikmittelfluss durch die Steuerleitung 11 hindurch freigegeben oder gesperrt wird und dementsprechend der Druckraum 10 ein veränderliches Volumen während der Betätigung des Geberkolbens 3 aufweist. Die hierdurch erzeugte stufenlose Variabilität der Ventilbetätigung erstreckt sich innerhalb der Grenzen maximalen Öffnungshubs der Gaswechselventile 2 einerseits, wenn sich das Hydraulikventil 13 während der gesamten Hubphase des Geberkolbens 3 in Schließstellung befindet, und vollständiger Abschaltung der Gaswechselventile 2 andererseits, wenn sich das Hydraulikventil 13 zumindest bis zur Maximalerhebung des Geberkolbens 3 in Offenstellung befindet.In the figure, 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 are disclosed by means of a hydraulic circuit diagram. Shown are a master piston 3, which is driven by a cam-like cam follower 4 by a cam 5 of a camshaft 6, and a slave piston 7, by means of a valve bridge 8, a pair of identical gas exchange valves 2, i. Inlet or exhaust valves, against the force acting in the closing direction of the valve springs 9 drives. The master piston 3 and the slave piston 7 define a hydraulic pressure chamber 10, which is connected via a control line 11 with a hydraulic pressure relief chamber 12. An arranged in the control line 11 hydraulic valve 13 which is formed according to the drawn circuit symbol electrically controllable and normally open design ensures that a hydraulic fluid flow through the control line 11 through is released or blocked and accordingly the pressure chamber 10 a variable volume during actuation the master piston 3 has. The continuously variable variability of the valve actuation produced thereby extends within the limits of the maximum opening stroke of the gas exchange valves 2 on the one hand, when the hydraulic valve 13 is in the closed position during the entire stroke phase of the master piston 3, and complete shutdown of the gas exchange valves 2, if the hydraulic valve 13 at least until to the maximum elevation of the master piston 3 is in the open position.

Der an eine Hydraulikmittelversorgung 14 der Brennkraftmaschine und vorliegend an deren Schmiermittelversorgung mittels eines Rückschlagventils 15 angeschlossene Druckentlastungsraum 12 weist einen federbelasteten Druckspeicher 16 bekannter Bauweise auf und ist zwecks Ausgleich leckagebedingter Hydraulikmittelverluste aus dem Druckraum 10 über eine Bypassleitung 17 mit dem Druckraum 10 verbunden. Dabei bewirkt ein in der Bypassleitung 17 angeordnetes Rückschlagventil 18, dass ein Hydraulikmittelfluss durch die Bypassleitung 17 hindurch in den Druckraum 10 freigegeben und in den Druckentlastungsraum 12 gesperrt wird.The connected to a hydraulic fluid supply 14 of the internal combustion engine and in the present case at the lubricant supply by means of a check valve 15 pressure relief chamber 12 has a spring-loaded pressure accumulator 16 known construction and is for the purpose of balancing leak-induced hydraulic fluid losses from the pressure chamber 10 via a bypass line 17 to the pressure chamber 10 is connected. In this case, a non-return valve 18 arranged in the bypass line 17 causes a hydraulic fluid flow to be released through the bypass line 17 into the pressure chamber 10 and blocked in the pressure relief chamber 12.

Für den Fall, dass das Hydraulikventil 13 während des Betriebs der Brennkraftmaschine fehlerhaft offen stehen bleibt - wie oben erwähnt, kommt als Ursache hierfür insbesondere eine unterbrochene Stromversorgung des Hydraulikventils 13 in Betracht - und dies zur vollständigen Stilllegung der Gaswechselventile 2 bei entsprechend inakzeptablem Betriebsverhalten der Brennkraftmaschine führen würde, umfasst die Ventilsteuerung 1 erfindungsgemäß ein weiteres Hydraulikventil 19, das in der Steuerleitung 11 zwischen Hydraulikventil 13 und Druckentlastungsraum 12 angeordnet und während des normalen, d.h. fehlerfreien Betriebs der Ventilsteuerung 1 geöffnet ist. Das weitere Hydraulikventil 19 ermöglicht jedoch einen Notlaufbetrieb der Brennkraftmaschine. Dieser wird dadurch eingeleitet, dass das weitere Hydraulikventil 19 nach Detektion des fehlerhaft offen stehenden Hydraulikventils 13 schließt, so dass sich der im Druckraum 10 ausbildende Hydraulikmitteldruck nicht mehr in den Druckentlastungsraum 12 entlasten kann und die Gaswechselventile 2 ausreichend weit öffnen. Im theoretischen Falle eines vollständig inkompressiblen und leckagedichten Druckraums 10 würde so der vom Geberkolben 3 vorgegebene Hub vollständig auf die Gaswechselventile 2 übertragen werden und dem oben genannten maximalen Öffnungshub entsprechen.In the event that the hydraulic valve 13 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 hydraulic valve 13 into consideration - and this to complete decommissioning of the gas exchange valves 2 in accordance with unacceptable performance of the internal combustion engine would lead, the valve control 1 according to the invention comprises a further hydraulic valve 19 which is arranged in the control line 11 between the hydraulic valve 13 and the pressure relief chamber 12 and during normal, ie error-free operation of the valve control 1 is open. The further hydraulic valve 19, however, allows emergency operation of the internal combustion engine. This is initiated by the fact that the further hydraulic valve 19 closes after detection of the incorrectly open hydraulic valve 13, so that the forming in the pressure chamber 10 hydraulic fluid pressure can no longer relieve in the pressure relief chamber 12 and the gas exchange valves 2 open wide enough. In the theoretical case of a completely incompressible and leak-tight pressure chamber 10, the stroke predetermined by the master piston 3 would thus be completely transferred to the gas exchange valves 2 and correspond to the abovementioned maximum opening stroke.

An die Umschaltgeschwindigkeit des weiteren Hydraulikventils 19, das gemäß seinem Schaltsymbol ebenfalls elektrisch ansteuerbar und stromlos offen ist, können deutlich geringere Anforderungen als an das Hydraulikventil 13 gestellt werden. Dies liegt darin begründet, dass das weitere Hydraulikventil 19 lediglich einmal zu Beginn des Notlaufbetriebs von der Offenstellung in die Schließstellung umschalten muss. Dementsprechend kann das weitere Hydraulikventil 19 wesentlich kostengünstiger als das deutlich schneller schaltende Hydraulikventil 13 ausgeführt sein.At the switching speed of the further hydraulic valve 19, which is also electrically controlled and normally open according to its switching symbol, significantly lower requirements than the hydraulic valve 13 can be made. This is due to the fact that the further hydraulic valve 19 only has to switch from the open position to the closed position once at the beginning of the emergency operation. Accordingly, the further hydraulic valve 19 be executed much cheaper than the much faster switching hydraulic valve 13.

Bezugszahlenreference numerals

11
Ventilsteuerungvalve control
22
GaswechselventilGas exchange valve
33
Geberkolbenmaster piston
44
Nockenfolgercam follower
55
Nockencam
66
Nockenwellecamshaft
77
Nehmerkolbenslave piston
88th
Ventilbrückevalve bridge
99
Ventilfedervalve spring
1010
Druckraumpressure chamber
1111
Steuerleitungcontrol line
1212
DruckentlastungsraumPressure relief chamber
1313
Hydraulikventilhydraulic valve
1414
HydraulikmittelversorgungHydraulic medium supply
1515
Rückschlagventilcheck valve
1616
Druckspeicheraccumulator
1717
Bypassleitungbypass line
1818
Rückschlagventilcheck valve
1919
weiteres Hydraulikventilanother hydraulic valve

Claims (4)

  1. Electrohydraulic valve controller (1) for the variable actuation of a gas exchange valve (2) of an internal combustion engine, comprising
    ▪ a master piston (3) driven by a camshaft (6),
    ▪ a slave piston (7) which drives the gas exchange valve (2),
    ▪ a pressure chamber (10) which is delimited by the master piston (3) and the slave piston (7) and which has a variable volume,
    ▪ a pressure relief chamber (12) which is connected to a hydraulic medium supply (14) of the internal combustion engine,
    ▪ a control line (11) which connects the pressure chamber (10) to the pressure relief chamber (12), and an electrically actuable hydraulic valve (13) which is arranged in said control line and which enables or blocks a hydraulic medium flow through the control line (11),
    ▪ a bypass line (17) which connects the pressure chamber (10) to the pressure relief chamber (12), and a check valve (18) which is arranged in said bypass line and which enables a hydraulic medium flow through the bypass line (17) into the pressure chamber (10) and blocks a hydraulic medium flow through the bypass line (17) into the pressure relief chamber (12),
    ▪ characterized in that the valve controlled (1) comprises a further hydraulic valve (19) which is arranged in the control line (11) between the hydraulic valve (13) and the pressure relief chamber (12) and which, if the hydraulic valve (13) is erroneously open, blocks the hydraulic medium flow through the control line (11) into the pressure relief chamber (12).
  2. Electrohydraulic valve controller (1) according to Claim 1, characterized in that the hydraulic valve (13) is designed to be open when deenergized.
  3. Electrohydraulic valve controller (1) according to Claim 2, characterized in that the further hydraulic valve (19) is likewise designed to be electrically actuable and open when deenergized.
  4. Electrohydraulic valve controller (1) according to Claim 1, characterized in that the hydraulic valve (13) is designed with significantly faster switching capability than the further hydraulic valve (19).
EP09782988.1A 2008-09-26 2009-09-15 Electrohydraulic valve controller Not-in-force EP2329116B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008049181A DE102008049181A1 (en) 2008-09-26 2008-09-26 Electrohydraulic valve control
PCT/EP2009/061895 WO2010034643A1 (en) 2008-09-26 2009-09-15 Electrohydraulic valve controller

Publications (2)

Publication Number Publication Date
EP2329116A1 EP2329116A1 (en) 2011-06-08
EP2329116B1 true EP2329116B1 (en) 2014-12-17

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Application Number Title Priority Date Filing Date
EP09782988.1A Not-in-force EP2329116B1 (en) 2008-09-26 2009-09-15 Electrohydraulic valve controller

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US (1) US20110277712A1 (en)
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US20110277712A1 (en) 2011-11-17
WO2010034643A1 (en) 2010-04-01
EP2329116A1 (en) 2011-06-08
DE102008049181A1 (en) 2010-04-01
KR101581068B1 (en) 2015-12-29
CN102165148B (en) 2013-07-17
KR20110059627A (en) 2011-06-02

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