EP1485585B1 - Device for controlling a gas exchange valve - Google Patents

Device for controlling a gas exchange valve Download PDF

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Publication number
EP1485585B1
EP1485585B1 EP03704223A EP03704223A EP1485585B1 EP 1485585 B1 EP1485585 B1 EP 1485585B1 EP 03704223 A EP03704223 A EP 03704223A EP 03704223 A EP03704223 A EP 03704223A EP 1485585 B1 EP1485585 B1 EP 1485585B1
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EP
European Patent Office
Prior art keywords
valve
pressure
gas exchange
lower pressure
pressure space
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EP03704223A
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German (de)
French (fr)
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EP1485585A1 (en
Inventor
Thomas Ludwig
Udo Diehl
Bernd Rosenau
Simon Kieser
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a device for controlling a gas exchange valve in internal combustion engines according to the preamble of claim 1.
  • the upper Working chamber is additionally connected via a likewise designed as a 2/2-way solenoid valve with spring return second control valve to a receding in a fluid reservoir return line.
  • a likewise designed as a 2/2-way solenoid valve with spring return second control valve to a receding in a fluid reservoir return line.
  • the second control valve is closed and the first control valve is opened.
  • the speed of the valve lift depends on the level of fluid or hydraulic pressure delivered by the pressure supply unit.
  • To close the gas exchange valve both control valves are switched so that the upper working chamber is closed off on the one hand by the pressure supply device and on the other hand connected to the return line.
  • the actuator piston is displaced upwards by the pressure prevailing in the lower working chamber and closes the gas exchange valve.
  • a Notschegafeder is provided, which is used as a compression spring in the lower working space and on the Actuator piston supported.
  • the Notschegafeder is dimensioned so that it overcomes the friction moments in the gas exchange valve and the valve actuator under all conditions and the actuator piston from each of his Move displacement positions out into the closed position is able to move.
  • the device according to the invention for controlling a gas exchange valve with the features of claim 1 has the advantage that with similar functionality, the device per gas exchange valve requires only a single electrical control valve. With the saving of one control valve per gas exchange valve not only reduces the number of control valves by half, but also halves the number of output stages required in the control unit for controlling the control valves. This results in a considerable savings potential in the production costs, which is e.g. in a four-cylinder engine with sixteen valves, eight control valves and eight output stages makes. In addition, the electrical energy requirement and the electrical wiring costs are reduced. The smaller number of control valves reduces the installation volume and reduces the probability of failure of the device. Overall, the device is less complex than the known one.
  • the control valve is designed as an electrically operated directional control valve.
  • the directional control valve is a 2/2-way solenoid valve.
  • a variable stroke of the gas exchange valve can be achieved only by short opening times by aborting the valve lift.
  • only the opening time and the closing time of the gas exchange valve can be specified.
  • the 2/2-way solenoid valve is clocked switched according to a preferred embodiment of the invention, wherein preferably the clock frequency is selected in response to the desired valve lift so that at a desired valve travel adjustment of the Control piston on the one hand and on the other hand via the 2/2-way solenoid valve on the other hand flowing fluid flows are the same size.
  • the proportional valve is controlled so that at a desired valve lift corresponding adjustment of the actuating piston via the throttle on the one hand and the proportional valve on the other hand flowing fluid flows are equal and thus sets a balance of power between the upper pressure chamber and the lower pressure chamber.
  • the device shown in block diagram in Fig. 1 is used to control gas exchange valves 10 in internal combustion engines.
  • the internal combustion engine or the internal combustion engine for a motor vehicle usually has four or more combustion cylinders, of which in Fig. 1 a detail of a cylinder head 11 of a combustion cylinder is shown.
  • combustion chamber 12 In the combustion cylinder a closed by the cylinder head 11 combustion chamber 12 is formed, which has at least one inlet cross section and an outlet cross section, which are each controlled by a gas exchange valve 10.
  • Each gas exchange valve 10 has, in a known manner, a valve member 13 with an axially displaceable on one guided valve stem 131 seated valve closing body 132, which cooperates with a inlet or outlet cross-section in the cylinder head 11 enclosing the valve seat 14.
  • the valve closing body 132 lifts off from the valve seat 14 or settles sealingly thereon.
  • each gas exchange valve 10 is assigned a hydraulic valve actuator 16, also called an actuator.
  • the hydraulic valve actuator 16 and a hydraulic output 162 having a hydraulic valve actuator 16 comprises a double-acting cylinder 17, a throttle 18 and a control valve 19.
  • the cylinder 17 has in a known manner a cylinder housing 20 and an axially displaceable guided therein and with the valve stem 131 of the associated gas exchange valve 10 coupled actuating piston 21, which divides the interior of the cylinder housing 20 in an upper pressure chamber 22 and a lower pressure chamber 23.
  • the upper pressure chamber 22 is connected directly and the lower pressure chamber 23 via the throttle 18 to the hydraulic input 161.
  • the control valve which is formed in FIG. 1 as a 2/2-way solenoid valve 24, is connected on the one hand to the lower pressure chamber 23 and on the other hand to the hydraulic output 162.
  • a relief line is connected, which is designed here as a fluid return line 25.
  • All valve actuators 16 are provided by a pressure supply device 25 with high-pressure fluid, preferably hydraulic oil, for which the hydraulic input 161 of each valve actuator 16 is connected to a fluid outlet 251 of the pressure supply device 25.
  • the pressure supply device 25 comprises a fluid reservoir 26, in which the fluid return line 27 opens, a high-pressure pump 28, the fluid from the fluid reservoir 26 sucks and promotes high pressure to the fluid outlet 251 of the pressure supply means 25, and connected to the fluid outlet 251 high-pressure accumulator 29, as Energy storage and pulsation damper is used. Between the output of the high-pressure pump 28 and the fluid outlet 251 of the pressure supply device 25 is still a check valve 30 is arranged with the pump outlet facing blocking direction.
  • valve control device The operation of the valve control device is as follows:
  • the pressure supply device 25 supplies the double-acting cylinder 17 with pressurized fluid.
  • the pressure in the upper pressure chamber 22 and in the lower pressure chamber 23 is equal. Since the coupling of the valve stem 131 the upper pressure chamber 22 limiting Druckbeaufschlagungs- or effective area of the actuating piston 21 is greater than the lower pressure chamber 23 limiting Druckbeaufschlagungs- or effective area, in the lower pressure chamber 23 acting as a return spring compression spring 31 is arranged, on the one hand on the cylinder housing 20 and on the other hand on the actuating piston 21 is supported.
  • the compression spring 31 is dimensioned so that it holds the adjusting piston 21 in its in Fig.
  • the pressure spring 31 also fulfills the requirement for resetting the gas exchange valve 10 in its closed state during prolonged standstill of the internal combustion engine or in the event of failure of the pressure supply device 25 as an emergency closing spring.
  • the 2/2-way solenoid valve 24 is switched from its switching position shown in FIG. 1, so that the lower pressure chamber 23 is relieved by its connection to the fluid return line 27.
  • the control piston 21 moves down and opens the gas exchange valve 10.
  • the 2/2-way solenoid valve 24 is reset and thus the lower pressure chamber 23 separated from the fluid return line 27. Via the throttle 18 high-pressure fluid flows into the lower pressure chamber 23, and the actuating piston 21 is returned with support by the compression spring 31 in its the gas exchange valve 10 closing top dead center.
  • the solenoid valve 24 is controlled clocked.
  • the clock frequency is selected as a function of the desired valve lift, in such a way that at a desired valve travel adjustment of the actuating piston 21 via the throttle 18 on the one hand and the 2/2-way solenoid valve 24 on the other flowing fluid flows are the same size and thus adjusts an equilibrium of forces on the actuating piston 21 between the upper pressure chamber 22 and the lower pressure chamber 23.
  • the double-acting working cylinder 17 'shown schematically in FIG. 2 can be inserted into the valve control device 15 instead of the working cylinder 17 shown in FIG.
  • the working cylinder 17 ' is modified insofar as the compression spring 31 is omitted and the actuating piston 21 is formed as a stepped piston 32 with the upper pressure chamber 22 limiting active surface 321 and the lower pressure chamber 23 limiting effective surface 322.
  • With equal pressure in the upper pressure chamber 22 and the lower pressure chamber 23 of the stepped piston 32 is due to the lower pressure chamber 23 limiting larger effective area 322 safely moved to its top dead center and reliable in this held, so that the gas exchange valve 10 is reliably held in its closed position.
  • a same compression spring as the compression spring 31 can be provided in Fig. 1, but which can be dimensioned much weaker and only the holding of the stepped piston 32 must ensure in its top dead center.

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

Abstract

Disclosed is a device for controlling gas exchange valves comprising at least one valve actuator (16) and a pressure supply device (25) which provides the valve actuator (16) with high-pressure fluid. The valve actuator (16) comprises a working cylinder (17) with an actuating piston (21) which is coupled to the gas exchange valve (10) and which defines an upper pressure chamber (22) for closing the valve and a lower chamber (23) for opening the valve, in addition to a control valve (19) which controls the hydraulic pressure in the pressure chambers (22, 23). In order to reduce the production costs and electrical power requirements of said device, the upper pressure chamber (22) is connected directly and the lower pressure chamber (23) is connected by means of a throttle (18) to the pressure supply device (25) and the control valve (19) is connected to the lower pressure chamber (23) and a discharge line (27). According to the switching position, the control device (19) also connects the lower pressure chamber (23) to the discharge line (27) or blocks it off from said discharge line.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Vorrichtung zur Steuerung eines Gaswechselventils in Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1.The invention relates to a device for controlling a gas exchange valve in internal combustion engines according to the preamble of claim 1.

Bei einer bekannten Vorrichtung dieser Art ( DE 198 26 047 A1 ) ist der untere Druck- oder Arbeitsraum des doppeltwirkenden Arbeitszylinders und der obere Druck- oder Arbeitsraum des Arbeitszylinders über das als 2/2-Wegemagnetventil mit Federrückstellung ausgebildete Steuerventil an die hydraulische Druckversorgungseinrichtung gelegt. Die den oberen Arbeitsraum begrenzende Druckbeaufschlagungs- oder Wirkfläche des Stellkolbens ist größer ausgebildet als die den unteren Arbeitsraum begrenzende Druckbeaufschlagungs- oder Wirkfläche des Stellkolbens, so daß mit Öffnen des Steuerventils auf den Stellkolben eine diesen gegen den Druck im unteren Arbeitsraum verschiebende Druckkraft wirkt und der Stellkolben das Gaswechselventil öffnet. Der obere Arbeitsraum ist zusätzlich über ein ebenfalls als 2/2-Wegemagnetventil mit Federrückstellung ausgebildetes zweites Steuerventil an einer in einem Fluidreservoir mündenden Rückführleitung angeschlossen. Zum Verschieben des Stellkolbens in Ventilöffnungsrichtung wird das zweite Steuerventil geschlossen und das erste Steuerventil geöffnet. Infolge der unterschiedlichen Wirkflächen des Stellkolbens wird der Stellkolben nach unten verschoben und öffnet das Gaswechselventil um einen von der Dauer der Steuerventilansteuerung abhängigen Ventilhub. Die Geschwindigkeit des Ventilhubs hängt von der Höhe des von der Druckversorgungseinheit eingesteuerten Fluid- oder Hydraulikdrucks ab. Zum Schließen des Gaswechselventils werden beide Steuerventile umgeschaltet, so daß der obere Arbeitsraum einerseits von der Druckversorgungseinrichtung abgesperrt und andererseits mit der Rückführleitung verbunden wird. Der Stellkolben wird von dem im unteren Arbeitsraum herrschenden Druck nach oben verschoben und schließt das Gaswechselventil.In a known device of this type ( DE 198 26 047 A1 ), the lower pressure or working space of the double-acting cylinder and the upper pressure or working space of the working cylinder is placed on the designed as a 2/2-way solenoid valve with spring return control valve to the hydraulic pressure supply device. The upper working space limiting Druckbeaufschlagungs- or effective area of the actuating piston is designed to be greater than the lower working space limiting Druckbeaufschlagungs- or effective area of the actuating piston, so that with opening of the control valve on the actuating piston this acts against the pressure in the lower working space pressure force and the actuating piston the gas exchange valve opens. The upper Working chamber is additionally connected via a likewise designed as a 2/2-way solenoid valve with spring return second control valve to a receding in a fluid reservoir return line. To displace the actuating piston in the valve opening direction, the second control valve is closed and the first control valve is opened. As a result of the different effective surfaces of the actuating piston of the adjusting piston is moved downward and opens the gas exchange valve by a dependent of the duration of the control valve control valve. The speed of the valve lift depends on the level of fluid or hydraulic pressure delivered by the pressure supply unit. To close the gas exchange valve both control valves are switched so that the upper working chamber is closed off on the one hand by the pressure supply device and on the other hand connected to the return line. The actuator piston is displaced upwards by the pressure prevailing in the lower working chamber and closes the gas exchange valve.

Um das Gaswechselventil nach einer vollständigen Druckentlastung des Drucksystems durch eine geringe Leckage, z.B. bei längerem Abstellen der Brennkraftmaschine oder bei Ausfall der Druckversorgungseinrichtung, in der Schließposition zu halten, ist eine Notschließfeder vorgesehen, die als Druckfeder in den unteren Arbeitsraum eingesetzt ist und sich an dem Stellkolben abstützt. Die Notschließfeder ist so dimensioniert, daß sie unter allen Bedingungen die Reibmomente im Gaswechselventil und im Ventilsteller überwindet und den Stellkolben aus jeder seiner Verschiebepositionen heraus in die Schließlage zu bewegen vermag.To keep the gas exchange valve after a complete pressure relief of the pressure system by a slight leakage, eg prolonged shutdown of the engine or failure of the pressure supply device in the closed position, a Notschließfeder is provided, which is used as a compression spring in the lower working space and on the Actuator piston supported. The Notschließfeder is dimensioned so that it overcomes the friction moments in the gas exchange valve and the valve actuator under all conditions and the actuator piston from each of his Move displacement positions out into the closed position is able to move.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Vorrichtung zur Steuerung eines Gaswechselventils mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß bei ähnlicher Funktionalität die Vorrichtung pro Gaswechselventil nur ein einziges elektrisches Steuerventil benötigt. Mit der Einsparung eines Steuerventils pro Gaswechselventil verringert sich nicht nur die Zahl der Steuerventile um die Hälfte, sondern halbiert sich auch die Zahl der im Steuergerät zur Ansteuerung der Steuerventile erforderlichen Leistungsendstufen. Damit wird ein erhebliches Einsparungspotential bei den Herstellungskosten erzielt, was z.B. bei einer vierzylindrigen Brennkraftmaschine mit sechzehn Ventilen, acht Steuerventile und acht Leistungsendstufen ausmacht. Darüber hinaus verringert sich der elektrische Energiebedarf und der elektrische Verkabelungaufwand. Durch die geringere Zahl der Steuerventile reduziert sich das Einbauvolumen und sinkt die Ausfallwahrscheinlichkeit der Vorrichtung. Insgesamt ist die Vorrichtung weniger komplex als die bekannte.The device according to the invention for controlling a gas exchange valve with the features of claim 1 has the advantage that with similar functionality, the device per gas exchange valve requires only a single electrical control valve. With the saving of one control valve per gas exchange valve not only reduces the number of control valves by half, but also halves the number of output stages required in the control unit for controlling the control valves. This results in a considerable savings potential in the production costs, which is e.g. in a four-cylinder engine with sixteen valves, eight control valves and eight output stages makes. In addition, the electrical energy requirement and the electrical wiring costs are reduced. The smaller number of control valves reduces the installation volume and reduces the probability of failure of the device. Overall, the device is less complex than the known one.

Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Vorrichtung möglich.The measures listed in the further claims advantageous refinements and improvements of claim 1 device are possible.

Gemäß einer vorteilhaften Ausführungsform der Erfindung ist das Steuerventil als ein elektrisch betätigtes Wegeventil ausgebildet. Vorzugsweise ist das Wegeventil ein 2/2-Wegemagnetventil. Bei dieser einfachsten Form der Realisierung des Steuerventils kann ein variabler Hub des Gaswechselventils nur bei kurzen Öffnungszeiten durch Abbruch des Ventilhubs erreicht werden. Im übrigen können nur die Öffnungszeit und die Schließzeit des Gaswechselventils vorgegeben werden.According to an advantageous embodiment of the invention, the control valve is designed as an electrically operated directional control valve. Preferably, the directional control valve is a 2/2-way solenoid valve. In this simplest form of implementation of the control valve, a variable stroke of the gas exchange valve can be achieved only by short opening times by aborting the valve lift. Moreover, only the opening time and the closing time of the gas exchange valve can be specified.

Soll der Ventilhub auch bei längeren Öffnungszeiten beeinflußbar sein, so wird gemäß einer bevorzugten Ausführungsform der Erfindung das 2/2-Wegemagnetventil getaktet umgeschaltet, wobei vorzugsweise die Taktfrequenz in Abhängigkeit von dem gewünschten Ventilhub so gewählt wird, daß bei einem dem gewünschten Ventilhub entsprechenden Verstellweg des Stellkolbens die über die Drossel einerseits und über das 2/2-Wegemagnetventil andererseits fließenden Fluidströme gleich groß sind.If the valve lift can be influenced even with longer opening times, the 2/2-way solenoid valve is clocked switched according to a preferred embodiment of the invention, wherein preferably the clock frequency is selected in response to the desired valve lift so that at a desired valve travel adjustment of the Control piston on the one hand and on the other hand via the 2/2-way solenoid valve on the other hand flowing fluid flows are the same size.

Gemäß einer alternativen Ausführungsform der Erfindung kann anstelle eines getakteten 2/2-Wegemagnetventils auch ein elektrisch betätigtes Proportionalventil verwendet werden. Zur Erzielung des variablen Ventilhubs wird das Proportionalventil so angesteuert, daß bei einem dem gewünschten Ventilhub entsprechenden Verstellweg des Stellkolbens die über die Drossel einerseits und das Proportionalventil anderseits fließenden Fluidströme gleich groß sind und sich damit ein Kräftegleichgewicht zwischen dem oberen Druckraum und dem unteren Druckraum einstellt.According to an alternative embodiment of the invention, instead of a clocked 2/2-way solenoid valve and an electrically operated proportional valve can be used. To achieve the variable valve lift, the proportional valve is controlled so that at a desired valve lift corresponding adjustment of the actuating piston via the throttle on the one hand and the proportional valve on the other hand flowing fluid flows are equal and thus sets a balance of power between the upper pressure chamber and the lower pressure chamber.

Zeichnungdrawing

Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels im folgenden näher beschrieben. Es zeigen:

Fig. 1
ein Schaltbild einer Vorrichtung zur Steuerung eines Gaswechselventils in einer Brennkraftmaschine,
Fig. 2
ein alternatives Ausführungsbeispiels eines Ventilstellers in Fig. 1,
Fig. 3
zwei Diagramme zur Erläuterung der Funktionsweise des Ventilstellers in Fig. 1.
The invention is described in more detail below with reference to an embodiment shown in the drawing. Show it:
Fig. 1
a circuit diagram of an apparatus for controlling a gas exchange valve in an internal combustion engine,
Fig. 2
an alternative embodiment of a valve actuator in Fig. 1,
Fig. 3
two diagrams for explaining the operation of the valve actuator in Fig. 1st

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die in Fig. 1 im Blockschaltbild dargestellte Vorrichtung dient zur Steuerung von Gaswechselventilen 10 in Brennkraftmaschinen. Die Brennkraftmaschine oder der Verbrennungsmotor für ein Kraftfahrzeug weist üblicherweise vier oder mehr Verbrennungszylinder auf, von denen in Fig. 1 ausschnittweise ein Zylinderkopf 11 eines Verbrennungszylinders dargestellt ist. Im Verbrennungszylinder ist ein von dem Zylinderkopf 11 abgeschlossener Brennraum 12 ausgebildet, der mindestens einen Einlaßquerschnitt und einen Auslaßquerschnitt aufweist, die jeweils von einem Gaswechselventil 10 gesteuert sind. Jedes Gaswechselventil 10 weist in bekannter Weise ein Ventilglied 13 mit einem auf einem axial verschieblich geführten Ventilschaft 131 sitzenden Ventilschließkörper 132 auf, der mit einem den Einlaß- oder Auslaßquerschnitt im Zylinderkopf 11 umschließenden Ventilsitz 14 zusammenwirkt. Durch Verschieben des Ventilschafts 131 in die eine oder andere Axialrichtung hebt der Ventilschließkörper 132 vom Ventilsitz 14 ab öder legt sich dichtend auf diesen auf.The device shown in block diagram in Fig. 1 is used to control gas exchange valves 10 in internal combustion engines. The internal combustion engine or the internal combustion engine for a motor vehicle usually has four or more combustion cylinders, of which in Fig. 1 a detail of a cylinder head 11 of a combustion cylinder is shown. In the combustion cylinder a closed by the cylinder head 11 combustion chamber 12 is formed, which has at least one inlet cross section and an outlet cross section, which are each controlled by a gas exchange valve 10. Each gas exchange valve 10 has, in a known manner, a valve member 13 with an axially displaceable on one guided valve stem 131 seated valve closing body 132, which cooperates with a inlet or outlet cross-section in the cylinder head 11 enclosing the valve seat 14. By moving the valve stem 131 in one or the other axial direction, the valve closing body 132 lifts off from the valve seat 14 or settles sealingly thereon.

Die Betätigung der Gaswechselventile 10 erfolgt durch eine elektrohydraulische Ventilsteuervorrichtung, die in Fig. 1 im Schaltbild dargestellt ist. In der Ventilsteuervorrichtung ist jedem Gaswechselventil 10 ein hydraulischer Ventilsteller 16, auch Aktor genannt, zugeordnet. Der einen Hydraulikeingang 161 und einen Hydraulikausgang 162 aufweisende hydraulischer Ventilsteller 16 umfaßt einen doppeltwirkenden Arbeitszylinder 17, eine Drossel 18 und ein Steuerventil 19. Der Arbeitszylinder 17 weist in bekannter Weise ein Zylindergehäuse 20 und einen darin axial verschieblich geführten und mit dem Ventilschaft 131 des zugeordneten Gaswechselventils 10 gekoppelten Stellkolben 21 auf, der den Innenraum des Zylindergehäuses 20 in einen oberen Druckraum 22 und einen unteren Druckraum 23 unterteilt. Der obere Druckraum 22 ist unmittelbar und der untere Druckraum 23 über die Drossel 18 an dem Hydraulikeingang 161 angeschlossen. Das Steuerventil, das in Fig. 1 als ein 2/2-Wegemagnetventil 24 ausgebildet ist, ist einerseits mit dem unteren Druckraum 23 und andererseits mit dem Hydraulikausgang 162 verbunden. An dem Hydraulikausgang 162 ist eine Entlastungsleitung angeschlossen, die hier als Fluidrücklaufleitung 25 ausgebildet ist. Alle Ventilsteller 16 werden von einer Druckversorgungseinrichtung 25 mit unter Hochdruck stehendem Fluid, vorzugsweise Hydrauliköl, gespeist, wozu der Hydraulikeingang 161 eines jeden Ventilstellers 16 an einem Fluidausgang 251 der Druckversorgungseinrichtung 25 angeschlossen ist. Die Druckversorgungseinrichtung 25 umfaßt ein Fluidreservoir 26, in dem die Fluidrückführleitung 27 mündet, eine Hochdruckpumpe 28, die Fluid aus dem Fluidreservoir 26 ansaugt und mit Hochdruck zu dem Fluidausgang 251 der Druckversorgungseinrichtung 25 fördert, sowie einen an dem Fluidausgang 251 angeschlossenen Hochdruckspeicher 29, der als Energiespeicher und Pulsationsdämpfer dient. Zwischen Ausgang der Hochdruckpumpe 28 und dem Fluidausgang 251 der Druckversorgungseinrichtung 25 ist noch ein Rückschlagventil 30 mit zum Pumpenausgang weisender Sperrichtung angeordnet.The actuation of the gas exchange valves 10 is effected by an electro-hydraulic valve control device, which is shown in Fig. 1 in the diagram. In the valve control device, each gas exchange valve 10 is assigned a hydraulic valve actuator 16, also called an actuator. The hydraulic valve actuator 16 and a hydraulic output 162 having a hydraulic valve actuator 16 comprises a double-acting cylinder 17, a throttle 18 and a control valve 19. The cylinder 17 has in a known manner a cylinder housing 20 and an axially displaceable guided therein and with the valve stem 131 of the associated gas exchange valve 10 coupled actuating piston 21, which divides the interior of the cylinder housing 20 in an upper pressure chamber 22 and a lower pressure chamber 23. The upper pressure chamber 22 is connected directly and the lower pressure chamber 23 via the throttle 18 to the hydraulic input 161. The control valve, which is formed in FIG. 1 as a 2/2-way solenoid valve 24, is connected on the one hand to the lower pressure chamber 23 and on the other hand to the hydraulic output 162. At the hydraulic outlet 162, a relief line is connected, which is designed here as a fluid return line 25. All valve actuators 16 are provided by a pressure supply device 25 with high-pressure fluid, preferably hydraulic oil, for which the hydraulic input 161 of each valve actuator 16 is connected to a fluid outlet 251 of the pressure supply device 25. The pressure supply device 25 comprises a fluid reservoir 26, in which the fluid return line 27 opens, a high-pressure pump 28, the fluid from the fluid reservoir 26 sucks and promotes high pressure to the fluid outlet 251 of the pressure supply means 25, and connected to the fluid outlet 251 high-pressure accumulator 29, as Energy storage and pulsation damper is used. Between the output of the high-pressure pump 28 and the fluid outlet 251 of the pressure supply device 25 is still a check valve 30 is arranged with the pump outlet facing blocking direction.

Die Wirkungsweise der Ventilsteuervorrichtung ist wie folgt:The operation of the valve control device is as follows:

Die Druckversorgungseinrichtung 25 versorgt den doppeltwirkenden Arbeitszylinder 17 mit unter Druck stehendem Fluid. In dem in Fig. 1 dargestellten statischen Fall ist der Druck in dem oberen Druckraum 22 und in dem unteren Druckraum 23 gleich groß. Da durch die Ankopplung des Ventilschafts 131 die den oberen Druckraum 22 begrenzende Druckbeaufschlagungs- oder Wirkfläche des Stellkolbens 21 größer ist als die den unteren Druckraum 23 begrenzende Druckbeaufschlagungs- oder Wirkfläche, ist im unteren Druckraum 23 eine als Rückstellfeder fungierende Druckfeder 31 angeordnet, die sich einerseits am Zylindergehäuse 20 und andererseits am Stellkolben 21 abstützt. Die Druckfeder 31 ist so dimensioniert, daß sie bei Druckgleichheit in den beiden Druckräumen 22, 23 den Stellkolben 21 in seiner in Fig. 1 dargestellten, oberen Totpunktlage hält, in der das Gaswechselventil 10 geschlossen ist, der Ventilschließkörper 132 des Ventilglieds 13 also dichtend auf dem Ventilsitz 14 am Zylinderkopf 11 aufsitzt. Die Druckfeder 31 erfüllt zugleich auch als Notschließfeder die Forderung nach Rückstellen des Gaswechselventils 10 in seinen Schließzustand bei längerem Stillstand der Brennkraftmaschine oder bei Ausfall der Druckversorgungseinrichtung 25.The pressure supply device 25 supplies the double-acting cylinder 17 with pressurized fluid. In the static case shown in Fig. 1, the pressure in the upper pressure chamber 22 and in the lower pressure chamber 23 is equal. Since the coupling of the valve stem 131 the upper pressure chamber 22 limiting Druckbeaufschlagungs- or effective area of the actuating piston 21 is greater than the lower pressure chamber 23 limiting Druckbeaufschlagungs- or effective area, in the lower pressure chamber 23 acting as a return spring compression spring 31 is arranged, on the one hand on the cylinder housing 20 and on the other hand on the actuating piston 21 is supported. The compression spring 31 is dimensioned so that it holds the adjusting piston 21 in its in Fig. 1 shown, top dead center position in pressure equality in the two pressure chambers 22, 23, in the Gas exchange valve 10 is closed, the valve closing body 132 of the valve member 13 so sealingly seated on the valve seat 14 on the cylinder head 11. At the same time, the pressure spring 31 also fulfills the requirement for resetting the gas exchange valve 10 in its closed state during prolonged standstill of the internal combustion engine or in the event of failure of the pressure supply device 25 as an emergency closing spring.

Zum Öffnen des Gaswechselventils 10 wird das 2/2-Wegemagnetventil 24 aus seiner in Fig. 1 dargestellten Schaltstellung umgeschaltet, so daß der untere Druckraum 23 durch seinen Anschluß an die Fluidrückführleitung 27 entlastet wird. Durch den zusammenbrechenden Druck im untere Druckraum 23 bewegt sich der Stellkolben 21 nach unten und öffnet das Gaswechselventil 10. Zum Schließen des Gaswechselventils 10 wird das 2/2-Wegemagnetventil 24 wieder zurückgesetzt und damit der untere Druckraum 23 von der Fluidrückführleitung 27 getrennt. Über die Drossel 18 strömt unter Hochdruck stehendes Fluid in die untere Druckkammer 23, und der Stellkolben 21 wird mit Unterstützung durch die Druckfeder 31 in seine das Gaswechselventil 10 schließende obere Totpunktlage zurückgeführt.To open the gas exchange valve 10, the 2/2-way solenoid valve 24 is switched from its switching position shown in FIG. 1, so that the lower pressure chamber 23 is relieved by its connection to the fluid return line 27. By the collapsing pressure in the lower pressure chamber 23, the control piston 21 moves down and opens the gas exchange valve 10. To close the gas exchange valve 10, the 2/2-way solenoid valve 24 is reset and thus the lower pressure chamber 23 separated from the fluid return line 27. Via the throttle 18 high-pressure fluid flows into the lower pressure chamber 23, and the actuating piston 21 is returned with support by the compression spring 31 in its the gas exchange valve 10 closing top dead center.

In den Diagrammen der Fig. 3 ist einerseits der Hubweg h des Ventilglieds 13 des Gaswechselventils 10 in Abhängigkeit von der Zeit t (oberes Diagramm) und andererseits die Magnetventilansteuerung in Abhängigkeit von der Zeit t (unteres Diagramm) dargestellt. Im Zeitpunkt t0 wird das Magnetventil 24 bestromt und schaltet damit aus seiner Sperrstellung um, so daß der untere Druckraum 23 mit der Fluidrückführleitung 27 verbunden ist. Der Stellkolben 21 bewegt sich durch den Druckabbau in dem unteren Druckraum 23 in Richtung Öffnen des Gaswechselventils 10. Wird zum Zeitpunkt t1 die Ansteuerung des Magnetventils 24 beendet und dieses in seine Sperrstellung zurückgesetzt, so haben der Stellkolben 21 und das Ventilglied 13 den Hub h1 ausgeführt. Infolge des in dem unteren Druckraum 23 ansteigenden Drucks beginnen nunmehr Stellkolben 21 und Ventilglied 13 sich in Schließrichtung des Gaswechselventils 10 zu bewegen. Wird dagegen erst zum Zeitpunkt t2 das Magnetventil 24 zurückgesetzt, so wird der Hubweg h2 erreicht und das Gaswechselventil 10 weiter geöffnet. Bei der etwas größerer Öffnungszeit t3 erreicht das Ventilglied 13 seinen maximalen Hub hmax. Wie daraus ersichtlich ist, kann der angestrebte variable Hub des Gaswechselventils 10 nur bei kleinen Ventilöffnungszeiten (kleiner t3) erreicht werden. Bei den meisten Anforderungen an einen variablen Ventiltrieb genügt dies aber.In the diagrams of Fig. 3, on the one hand, the stroke h of the valve member 13 of the gas exchange valve 10 as a function of the time t (upper diagram) and on the other hand, the solenoid valve control in dependence on the time t (lower diagram) shown. At time t 0 , the solenoid valve 24 is energized and thus switches from its blocking position, so that the lower pressure chamber 23 is connected to the fluid return line 27. The adjusting piston 21 moves through the pressure reduction in the lower pressure chamber 23 in the direction of opening the gas exchange valve 10. If, at time t 1, the control of the solenoid valve 24 ends and this reset to its blocking position, the actuating piston 21 and the valve member 13 have the stroke h 1 executed. As a result of the rising in the lower pressure chamber 23 pressure now actuating piston 21 and valve member 13 begin to move in the closing direction of the gas exchange valve 10. If, however, only at time t 2, the solenoid valve 24 is reset, the stroke h 2 is reached and the gas exchange valve 10 is opened further. At the somewhat larger opening time t 3 , the valve member 13 reaches its maximum stroke h max . As can be seen, the desired variable lift of the gas exchange valve 10 can only be achieved with small valve opening times (smaller t 3 ). But this is sufficient for most requirements of a variable valve train.

Soll der Hub des Ventilglieds 13 des Gaswechselventils 10 auch bei längeren Öffnungszeiten beeinflußt werden können, also bei Öffnungszeiten, die größer als t3 in Fig. 3 sind, so wird das Magnetventil 24 getaktet angesteuert. Dabei wird die Taktfrequenz in Abhängigkeit von dem gewünschten Ventilhub gewählt, und zwar so, daß bei einem dem gewünschten Ventilhub entsprechenden Verstellweg des Stellkolbens 21 die über die Drossel 18 einerseits und das 2/2-Wegemagnetventil 24 andererseits fließenden Fluidströme gleich groß sind und sich somit ein Kräftegleichgewicht am Stellkolben 21 zwischen dem oberen Druckraum 22 und dem unteren Druckraum 23 einstellt.If the stroke of the valve member 13 of the gas exchange valve 10 can be influenced even at longer opening times, ie at opening times that are greater than t 3 in Fig. 3, the solenoid valve 24 is controlled clocked. The clock frequency is selected as a function of the desired valve lift, in such a way that at a desired valve travel adjustment of the actuating piston 21 via the throttle 18 on the one hand and the 2/2-way solenoid valve 24 on the other flowing fluid flows are the same size and thus adjusts an equilibrium of forces on the actuating piston 21 between the upper pressure chamber 22 and the lower pressure chamber 23.

Statt des getakteten 2/2-Wegemagnetventils 24 kann auch ein elektrisch betätigtes Proportionalventil verwendet werden. Dieses Proportionalventil wird so angesteuert; daß bei einem dem gewünschten Ventilhub entsprechenden Verstellweg des Stellkolbens 21 die über die Drossel 18 einerseits und das Proportionalventil andererseits fließenden Fluidströme ein Kräftegleichgewicht zwischen dem oberen Druckraum und dem unteren Druckraum 23 ergeben. Dies ist der Fall, wenn der über die Drossel 18 fließende Fluidstrom gleich dem über das Proportionalventil fließende Fluidstrom ist. Mit dem entsprechend aufgesteuerten Proportionalventil kann jeder beliebige Hub des Ventilglieds 13 eingestellt und über eine beliebige Öffnungsdauer gehalten werden.Instead of the clocked 2/2-way solenoid valve 24 and an electrically operated proportional valve can be used. This proportional valve is activated in this way; that at a corresponding to the desired valve travel adjustment of the actuating piston 21 via the throttle 18 on the one hand and the proportional valve on the other hand flowing fluid flows result in a balance of power between the upper pressure chamber and the lower pressure chamber 23. This is the case when the fluid flow flowing via the throttle 18 is equal to the fluid flow flowing through the proportional valve. With the appropriately open proportional valve any stroke of the valve member 13 can be adjusted and maintained over any opening period.

Der in Fig. 2 schematische dargestellte, doppeltwirkende Arbeitszylinder 17' kann anstelle des in Fig. 1 dargestellten Arbeitszylinders 17 in die Ventilsteuervorrichtung 15 eingesetzt werden. Der Arbeitszylinder 17' ist insofern modifiziert, als die Druckfeder 31 entfallen ist und der Stellkolben 21 als Stufenkolben 32 mit einer den oberen Druckraum 22 begrenzenden Wirkfläche 321 und einer den unteren Druckraum 23 begrenzende Wirkfläche 322 ausgebildet ist. Die untere Wirkfläche 322 ist wesentlich größer ausgebildet als die obere Wirkfläche 321. Bei Druckgleichheit in dem oberen Druckraum 22 und dem unteren Druckraum 23 wird der Stufenkolben 32 infolge der den unteren Druckraum 23 begrenzenden größeren Wirkfläche 322 sicher in seine obere Totpunktlage verschoben und in dieser zuverlässig gehalten, so daß auch das Gaswechselventil 10 zuverlässig in seiner Schließstellung gehalten wird. Um eine wie vorstehend erwähnte Notfunktion bei Systemausfall oder längerem Stillstand der Brennkraftmaschine zu gewährleisten, kann eine gleiche Druckfeder wie die Druckfeder 31 in Fig. 1 vorgesehen werden, die aber wesentlich schwächer dimensioniert werden kann und nur noch das Halten des Stufenkolbens 32 in seiner oberen Totpunktlage gewährleisten muß.The double-acting working cylinder 17 'shown schematically in FIG. 2 can be inserted into the valve control device 15 instead of the working cylinder 17 shown in FIG. The working cylinder 17 'is modified insofar as the compression spring 31 is omitted and the actuating piston 21 is formed as a stepped piston 32 with the upper pressure chamber 22 limiting active surface 321 and the lower pressure chamber 23 limiting effective surface 322. With equal pressure in the upper pressure chamber 22 and the lower pressure chamber 23 of the stepped piston 32 is due to the lower pressure chamber 23 limiting larger effective area 322 safely moved to its top dead center and reliable in this held, so that the gas exchange valve 10 is reliably held in its closed position. To an emergency as mentioned above in case of system failure or longer To ensure standstill of the internal combustion engine, a same compression spring as the compression spring 31 can be provided in Fig. 1, but which can be dimensioned much weaker and only the holding of the stepped piston 32 must ensure in its top dead center.

Claims (11)

  1. Device for controlling gas exchange valves in internal combustion engines, having at least one valve adjuster (16) which is assigned to a gas exchange valve (10), which valve adjuster (16) comprises a double-acting hydraulic working cylinder (17) with an adjusting piston (21), which is coupled to the gas exchange valve (10) and delimits an upper pressure space (22) for actuating the gas exchange valve (10) in the opening direction and a lower pressure space (23) for actuating the gas exchange valve (10) in the closing direction, and a control valve (19) which controls the hydraulic pressure in the pressure spaces (22, 23), and having a pressure supply device (25) which feeds the pressure spaces (22, 23) of the working cylinder (17) with a highly pressurized fluid, characterized in that the upper pressure space (22) is connected directly, and the lower pressure space (23) is connected by means of a throttle (18), to the pressure supply device (25), and in that the control valve (19) is connected at one side to the lower pressure space (23) and at the other side to a relief line (27) and, depending on the switching position, produces or blocks the connection between the lower pressure space (23) and relief line (27).
  2. Device according to Claim 1, characterized in that the control valve (19) is embodied as an electrically actuated directional control valve.
  3. Device according to Claim 1, characterized in that the directional control valve is a 2/2 directional control solenoid valve (24).
  4. Device according to Claim 3, characterized in that the 2/2 directional control solenoid valve (24) is switched in a clocked fashion in order to obtain a variable valve stroke.
  5. Device according to Claim 4, characterized in that the clock frequency is set as a function of the desired valve stroke, in such a way that, at an adjustment travel of the adjusting piston (21) which corresponds to the desired valve stroke, the fluid flows which flow via the throttle (18) on the one hand and via the 2/2 directional control solenoid valve (24) on the other hand are equally large.
  6. Device according to Claim 2, characterized in that the electrically actuated directional control valve is a proportional valve which is activated, in order to obtain a variable valve stroke, in such a way that, at an adjustment travel of the adjusting piston (21) which corresponds to the desired valve stroke, the fluid flows which flow via the throttle (18) on the one hand and via the proportional valve on the other hand are equally large.
  7. Device according to one of Claims 1 - 6, characterized in that a restoring spring (31) which loads the adjusting piston (21) counter to the pressure in the upper pressure space (22) is arranged in the working cylinder (17).
  8. Device according to Claim 7, characterized in that the restoring spring is a pressure spring (31) which is arranged in the lower pressure space (23), which restoring spring is supported at one side in the lower pressure space (23) and at the other side on the adjusting piston (21).
  9. Device according to one of Claims 1 - 8, characterized in that the adjusting piston (21) has a pressure-loading face (321) which delimits the upper pressure space (22) and a pressure-loading face (322) which delimits the lower pressure space (23), and in that the lower pressure-loading face (322) is larger than the upper pressure-loading face (321).
  10. Device according to Claim 9, characterized in that the adjusting piston (21) is embodied as a stepped piston (32).
  11. Device according to one of Claims 1 - 10, characterized in that the relief line is a fluid return line (27) which opens out in a fluid reservoir (26) of the pressure supply device (25).
EP03704223A 2002-03-08 2003-01-17 Device for controlling a gas exchange valve Expired - Lifetime EP1485585B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10210334A DE10210334A1 (en) 2002-03-08 2002-03-08 Device for controlling a gas exchange valve
DE10210334 2002-03-08
PCT/DE2003/000121 WO2003076772A1 (en) 2002-03-08 2003-01-17 Device for controlling a gas exchange valve

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EP1485585A1 EP1485585A1 (en) 2004-12-15
EP1485585B1 true EP1485585B1 (en) 2008-01-30

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EP (1) EP1485585B1 (en)
JP (1) JP4290563B2 (en)
DE (2) DE10210334A1 (en)
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CN101509404B (en) * 2008-02-15 2011-05-18 蔡学功 Variable valve system
DE102010024723B4 (en) * 2010-06-23 2014-02-13 Samson Aktiengesellschaft Pneumatic actuator and method of operating the pneumatic actuator
KR101737373B1 (en) * 2012-05-31 2017-05-18 가부시키가이샤 후지킨 Flow volume control device equipped with build-down system flow volume monitor
US10202968B2 (en) * 2012-08-30 2019-02-12 Illinois Tool Works Inc. Proportional air flow delivery control for a compressor
JP6187434B2 (en) 2014-11-14 2017-08-30 トヨタ自動車株式会社 FUEL CELL SYSTEM, MOBILE BODY, AND CONTROL METHOD
EP3406866A1 (en) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Hydraulic drive for accelerating and braking components to be dynamically moved
TWI684719B (en) * 2019-02-27 2020-02-11 陳文彬 Fluid control device

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JPS6040711A (en) * 1983-08-12 1985-03-04 Yanmar Diesel Engine Co Ltd Valve mechanism
JPS63176610A (en) * 1987-01-19 1988-07-20 Honda Motor Co Ltd Control device for suction and exhaust valves
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US20040089829A1 (en) 2004-05-13
JP2005519225A (en) 2005-06-30
DE50309104D1 (en) 2008-03-20
US6857618B2 (en) 2005-02-22
DE10210334A1 (en) 2003-09-18
WO2003076772A1 (en) 2003-09-18
JP4290563B2 (en) 2009-07-08

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