EP1440224B1 - Device for controlling gas exchange valves - Google Patents

Device for controlling gas exchange valves Download PDF

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Publication number
EP1440224B1
EP1440224B1 EP02760102A EP02760102A EP1440224B1 EP 1440224 B1 EP1440224 B1 EP 1440224B1 EP 02760102 A EP02760102 A EP 02760102A EP 02760102 A EP02760102 A EP 02760102A EP 1440224 B1 EP1440224 B1 EP 1440224B1
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EP
European Patent Office
Prior art keywords
valve
gas exchange
valve actuator
outlet
working space
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Expired - Lifetime
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EP02760102A
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German (de)
French (fr)
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EP1440224A1 (en
Inventor
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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/06—Timing or lift different for valves of same cylinder

Definitions

  • the invention relates to a device for controlling gas exchange valves in combustion cylinders of an internal combustion engine according to the preamble of claim 1.
  • each valve actuator whose actuating piston is integrally connected to the valve stem of the associated gas exchange valve, with its first working space constantly connected to a high pressure source and with its second working space on the one hand to a supply line to the high pressure source alternately closing or releasing first electric control valve and on the other hand a discharge line alternately releasing or closing second control valve connected.
  • the electrical control valves are designed as 2/2-way solenoid valves with spring return. With de-energized control valves, the first working space is still under high pressure, while the second working space is disconnected from the high pressure source and connected to the relief line. The gas exchange valve is closed. To open the gas exchange valve both control valves are energized.
  • the second working space of the valve actuator is on the one hand blocked by the second control valve with respect to the discharge line and on the other hand connected by the first control valve with the supply line to the high pressure source.
  • the gas exchange valve opens, wherein the size of the opening stroke depends on the formation of the voltage applied to the first electric control valve electrical control signal and the opening speed of the pressure supplied by the high pressure source.
  • the first control valve is then de-energized, so that it shuts off the supply line to the second working space of the valve actuator. In this way, all valve opening positions of the gas exchange valve can be adjusted by means of an electrical control unit for generating control signals.
  • two electrical control valves are required in each case, which act on the associated valve actuator according to hydraulic pressure.
  • the inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by the direct hydraulic coupling of the second working spaces of two valve actuators of a valve actuator pair for the implementation of the hydraulic Energy in a linear movement of the gas exchange valves, the number of required for the control of two valve actuators control valves is reduced from four to only two. Since it also halves the number of required for controlling the control valves output stages in the electronic control unit and thus also reduces the cabling effort, the manufacturing cost of the control device can be significantly reduced overall. In addition, the required installation space is reduced by the elimination of components and wiring, reduced by the low valve number, the probability of failure of the control valves and reduced both the hydraulic and the electrical energy requirements.
  • the two operated by the first and second valve actuator gas exchange valves are arranged in the same combustion cylinder of the internal combustion engine.
  • This has the advantage that the force surplus of the second valve actuator for opening the associated gas exchange valve does not have to be designed in the same amount as that of the first valve actuator, which must open the associated gas exchange valve against the maximum occurring back pressure in the combustion cylinder, but can be designed lower because the counterforce for opening the second gas exchange valve of the same combustion cylinder partially could already break down over the open first gas exchange valve.
  • At least the first valve actuator on a mechanical stroke limitation which is designed so that it blocks the further stroke movement of the actuating piston in the valve opening direction after releasing the connected to the second working space of the second valve actuator outlet on the first valve actuator by the actuating piston.
  • the lifting speed of both gas exchange valves is pressure-dependent and is influenced by the overlap of the strokes in conjunction with the release of the outlet in the second working space of the first valve actuator to the second working space of the second valve actuator. This results in a pressure and stroke-dependent speed curve of the gas exchange valves.
  • the invention is described in more detail below with reference to an embodiment shown in the drawing.
  • the drawing shows a circuit diagram of a device for controlling two gas exchange valves in a combustion cylinder of an internal combustion engine.
  • the gas exchange valves 12, 13 may be intake valves or exhaust valves which seal a combustion chamber 11 formed in the combustion cylinder 10 gas-tight.
  • Each gas exchange valve 12, 13 has in known manner an opening cross-section 14 in the combustion cylinder enclosing the valve seat 15 and a valve member 16 with a seated on an axially displaceable valve stem 161 valve closing body 162 which cooperates with the valve seat 15 for closing and releasing the opening cross-section 14.
  • the valve closing body 162 lifts off the valve seat 15 or lies on the valve seat 15.
  • the illustrated in the drawing in the block diagram device for controlling the two gas exchange valves 12, 13 has a gas exchange valve 12 actuated first valve actuator 17 and a gas exchange valve 13 actuated second valve actuator 18.
  • the valve control device further includes a Pressure supply device 19, which promotes a preferably controllable high-pressure pump 20, the fluid, for example hydraulic oil, from a fluid reservoir 21, a check valve 22 and a pressure accumulator 23 includes.
  • a pressure supply device 191 of the pressure supply device 19 which may be preceded by a second check valve 24 facing the output 191 forward direction, is a permanent, adjustable high pressure on.
  • the two hydraulic valve actuators 17, 18 are identically designed and each designed as a double-acting cylinder with a cylinder housing 25 and an axially displaceable guided therein actuator piston 26 which divides the interior of the cylinder housing 25 in a first working space 27 and a second working space 28.
  • the two first working chambers 27 of the two valve actuators 17, 18 are permanently connected to the outlet 191 of the pressure supply device. 19 connected.
  • the second working space 28 of the first valve actuator 17 has an inlet 29 and two outlets 30, 31, wherein the second outlet 31 is arranged at such a stroke distance from the first outlet 30, which in the closed position of the actuating piston 26 shown in FIG which he has brought about a closure of the gas exchange valve 12, the second outlet 31 is closed by the actuating piston 26 and is released to open the gas exchange valve 12 to the second working space 28 only after a predetermined opening stroke of the actuating piston 26.
  • the second working chamber 28 of the second valve actuator 18 has an inlet 32 and an outlet 33.
  • the inlet 29 on the first valve actuator 17 is via a first Control valve 3.4 connected to the output 191 of the pressure supply device 19.
  • the first outlet 30 of the first valve actuator 17 is connected to the valve inlet of a second control valve 35, whose valve outlet is connected to a return line 36 to the fluid reservoir 21.
  • the inlet 32 on the second valve actuator 18 is connected to the second outlet 31 on the first valve actuator 17 and the outlet 33 on the second valve actuator 18 via a check valve 37 to the valve inlet of the second control valve 35:
  • the passage direction of the check valve 37 faces from the outlet 33 to the second control valve 35.
  • the two control valves 34, 35 are designed as 2/2-way solenoid valves with spring return.
  • valve control device The operation of the valve control device is as follows:
  • the first control valve 34 is closed and the second control valve 35 is opened, the two second working chambers 28 of the valve actuator 17, 18 depressurized, and in the first working chambers 27 of the valve actuator 17, 18 pending high pressure of the pressure supply device 19 ensures that the actuating piston 26 are in their upper Hubend ein and thereby keep the gas exchange valves 12, 13 in their closed position.
  • the actuating piston 26 in the first valve actuator 17 closes the second outlet 31 connected to the inlet 32 on the second valve actuator 18.
  • the design of the distance between the two outlets 30, 31 on the first valve actuator 17 is energy-optimal as a function of the operating map of the internal combustion engine. It is also possible to make the stroke distance of the two outlets 30, 31 controllable by, for example, the second Outlet 31 is moved into a displaceable on the cylinder housing 25 collar, which is liquid-tight with the second working space 28 in conjunction. On the collar attacks a lifting drive, which is controlled by an electronic control unit, which controls the two control valves 34 and 35.
  • the axial displaceability of the second outlet 31 relative to the first outlet 30 is symbolized in the drawing by a second arrow 31 associated with the double arrow 39.
  • a plurality of second outlets 31 in the stroke direction of the actuating piston 26 can be arranged one behind the other, which can be closed by the adjusting ring successively.
  • the lift height of the respective gas exchange valve 12 or 13 during opening depends primarily on the activation duration of the first control valve 34. With prolonged control then engages provided at least in the first valve actuator 17 mechanical stroke limitation.
  • the in the drawing only as a stop 38 schematically indicated stroke limitation is for example designed so that the actuating piston 26 is prevented in the first valve actuator 17 shortly after releasing the outlet 31 to the second working chamber 28 of the second valve actuator 18 at a further stroke in the valve opening direction.
  • Such a stroke limitation makes energy sense, since then only hydraulic energy for adjusting the control piston 26 in the second valve actuator 18 is required.
  • the prerequisite for such a stroke limitation is that the sum of the opening cross sections 14 still achievable by the stroke limitation is sufficient in both gas exchange valves 12, 13 for the full load range of the internal combustion engine.
  • the lifting speed of the two gas exchange valves 12, 13 is primarily pressure-dependent and is influenced by the overlap of the strokes and the release of the connection between the second working chambers 28 of the two valve actuators 17, 18.

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

Abstract

The invention relates to a device for controlling gas exchange valves in an internal combustion engine, said device having hydraulic valve actuators (17, 18) comprising actuating plungers (26) acting upon a gas exchange valve (12, 13) and working chambers (27, 28) defined by the actuating plunger (26). The first working chamber (27) for closing the gas exchange valve (12, 13) is permanently under fluid pressure and the second working chamber (28) for opening the gas exchange valve (10) is alternately filled with and emptied of a pressurized fluid by means of a first and a second electrical control valve (34, 35). In order to reduce the number of required control valves, the second working chamber (28) of the second valve actuator (18) in a pair of valves is filled through the second working chamber (28) of the first valve actuator (17) that is connected to the first control valve (34) once a given stroke of the actuating plunger (26) of the first valve actuator (17) is carried out so as to open the assigned gas exchange valve (12).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Vorrichtung zur Steuerung von Gaswechselventilen in Verbrennungszylindern einer Brennkraftmaschine nach dem Oberbegriff des Anspruchs 1.The invention relates to a device for controlling gas exchange valves in combustion cylinders of an internal combustion engine according to the preamble of claim 1.

Bei einer bekannten Vorrichtung dieser Art ( DE 198 26 047 A1 ) ist jeder Ventilsteller, dessen Stellkolben einstückig mit dem Ventilstößel des zugeordneten Gaswechselventils verbunden ist, mit seinem ersten Arbeitsraum ständig mit einer Hochdruckquelle verbunden und mit seinem zweiten Arbeitsraum einerseits an einem eine Zuführleitung zu der Hochdruckquelle wechselweise schließenden oder freigebenden ersten elektrischen Steuerventil und andererseits an einem eine Entlastungsleitung wechselweise freigebenden oder schließenden zweiten Steuerventil angeschlossen. Die elektrischen Steuerventile sind als 2/2-Wegemagnetventile mit Federrückstellung ausgebildet. Bei stromlosen Steuerventilen steht der erste Arbeitsraum nach wie vor unter Hochdruck, während der zweite Arbeitsraum von der Hochdruckquelle getrennt und mit der Entlastungsleitung verbunden ist. Das Gaswechselventil ist geschlossen. Zum Öffnen des Gaswechselventils werden beide Steuerventile bestromt. Durch die umschaltenden Steuerventile wird der zweite Arbeitsraum des Ventilstellers einerseits durch das zweite Steuerventil gegenüber der Entlastungsleitung gesperrt und andererseits durch das erste Steuerventil mit der Zuführleitung zur Hochdruckquelle verbunden. Das Gaswechselventil öffnet, wobei die Größe des Öffnungshubs von der Ausbildung des an das erste elektrische Steuerventil angelegten elektrischen Steuersignals und die Öffnungsgeschwindigkeit von dem von der Hochdruckquelle eingesteuerten Druck abhängt. Um das Gaswechselventil in einer bestimmten Offenstellung zu halten, wird das erste Steuerventil anschließend stromlos geschaltet, so daß es die Zuführleitung zum zweiten Arbeitsraum des Ventilstellers absperrt. Auf diese Weise lassen sich mittels eines elektrischen Steuergeräts zur Steuersignalerzeugung sämtliche Ventilöffnungspositionen des Gaswechselventils einstellen. Zur Steuerung eines Gaswechselventils sind jeweils zwei elektrische Steuerventile nötig, die den zugeordneten Ventilsteller entsprechend mit Hydraulikdruck beaufschlagen.In a known device of this type ( DE 198 26 047 A1 ) is each valve actuator, whose actuating piston is integrally connected to the valve stem of the associated gas exchange valve, with its first working space constantly connected to a high pressure source and with its second working space on the one hand to a supply line to the high pressure source alternately closing or releasing first electric control valve and on the other hand a discharge line alternately releasing or closing second control valve connected. The electrical control valves are designed as 2/2-way solenoid valves with spring return. With de-energized control valves, the first working space is still under high pressure, while the second working space is disconnected from the high pressure source and connected to the relief line. The gas exchange valve is closed. To open the gas exchange valve both control valves are energized. By switching control valves, the second working space of the valve actuator is on the one hand blocked by the second control valve with respect to the discharge line and on the other hand connected by the first control valve with the supply line to the high pressure source. The gas exchange valve opens, wherein the size of the opening stroke depends on the formation of the voltage applied to the first electric control valve electrical control signal and the opening speed of the pressure supplied by the high pressure source. In order to keep the gas exchange valve in a certain open position, the first control valve is then de-energized, so that it shuts off the supply line to the second working space of the valve actuator. In this way, all valve opening positions of the gas exchange valve can be adjusted by means of an electrical control unit for generating control signals. To control a gas exchange valve two electrical control valves are required in each case, which act on the associated valve actuator according to hydraulic pressure.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Vorrichtung zur Steuerung von Gaswechselventilen mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß durch die direkte hydraulische Kopplung der zweiten Arbeitsräume von zwei Ventilstellern eines Ventilstellerpaars für die Umsetzung der hydraulischen Energie in eine lineare Bewegung der Gaswechselventile die Zahl der für die Steuerung von zwei Ventilstellern erforderlichen Steuerventile von bisher vier auf nur zwei reduziert wird. Da damit auch die Zahl der zur Ansteuerung der Steuerventile erforderlichen Endstufen im elektronischen Steuergerät halbiert wird und damit zusätzlich auch der Verkabelungsaufwand sinkt, können die Fertigungskosten für die Steuervorrichtung insgesamt deutlich reduziert werden. Zusätzlich wird der erforderliche Einbauraum durch den Wegfall von Bauelementen und Verkabelung reduziert, durch die geringe Ventilzahl die Ausfallwahrscheinlichkeit der Steuerventile verringert und sowohl der hydraulische als auch der elektrische Energiebedarf verkleinert.The inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by the direct hydraulic coupling of the second working spaces of two valve actuators of a valve actuator pair for the implementation of the hydraulic Energy in a linear movement of the gas exchange valves, the number of required for the control of two valve actuators control valves is reduced from four to only two. Since it also halves the number of required for controlling the control valves output stages in the electronic control unit and thus also reduces the cabling effort, the manufacturing cost of the control device can be significantly reduced overall. In addition, the required installation space is reduced by the elimination of components and wiring, reduced by the low valve number, the probability of failure of the control valves and reduced both the hydraulic and the electrical energy requirements.

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

Gemäß einer bevorzugten Ausführungsform der Erfindung sind die beiden von dem ersten und zweiten Ventilsteller betätigten Gaswechselventile in demselben Verbrennungszylinder der Brennkraftmaschine angeordnet. Dies hat den Vorteil, daß der Kraftüberschuß des zweiten Ventilstellers zum Öffnen des zugeordneten Gaswechselventils nicht in der gleichen Höhe ausgelegt werden muß, wie der des ersten Ventilstellers, der das zugeordnete Gaswechselventil gegen den maximal auftretenden Gegendruck im Verbrennungszylinder öffnen muß, sondern niedriger ausgelegt werden kann, da sich die Gegenkraft zum Öffnen des zweiten Gaswechselventils des gleichen Verbrennungszylinders zum Teil bereits über das geöffnete erste Gaswechselventil abbauen konnte.According to a preferred embodiment of the invention, the two operated by the first and second valve actuator gas exchange valves are arranged in the same combustion cylinder of the internal combustion engine. This has the advantage that the force surplus of the second valve actuator for opening the associated gas exchange valve does not have to be designed in the same amount as that of the first valve actuator, which must open the associated gas exchange valve against the maximum occurring back pressure in the combustion cylinder, but can be designed lower because the counterforce for opening the second gas exchange valve of the same combustion cylinder partially could already break down over the open first gas exchange valve.

Gemäß einer vorteilhaften Ausführungsform der Erfindung weist zumindest der erste Ventilsteller eine mechanische Hubbegrenzung auf, die so ausgelegt ist, daß sie nach Freigeben des mit dem zweiten Arbeitsraum des zweiten Ventilstellers verbundenen Auslasses am ersten Ventilsteller durch den Stellkolben die weitere Hubbewegung des Stellkolbens in Ventilöffnungsrichtung blockiert. Eine solche Hubbegrenzung im ersten Ventilsteller ist energetisch vorteilhaft, wenn der maximale Öffnungsquerschnitt beider Gaswechselventile noch für den Vollastbereich ausreicht; denn mit Blockieren des Stellkolbens im ersten Ventilsteller kann der gesamte Kraftüberschuß zur Verdrängung des Stellkolbens im zweiten Ventilsteller und zum Öffnen des zweiten Gaswechselventils eingesetzt werden. Die Hubgeschwindigkeit beider Gaswechselventile ist druckabhängig und wird durch die Überschneidung der Hübe in Verbindung mit der Freigabe des Auslasses im zweiten Arbeitsraum des ersten Ventilstellers zum zweiten Arbeitsraum des zweiten Ventilstellers beeinflußt. Damit ergibt sich ein druck- und hubabhängiger Geschwindigkeitsverlauf der Gaswechselventile.According to an advantageous embodiment of the invention, at least the first valve actuator on a mechanical stroke limitation, which is designed so that it blocks the further stroke movement of the actuating piston in the valve opening direction after releasing the connected to the second working space of the second valve actuator outlet on the first valve actuator by the actuating piston. Such a stroke limitation in the first valve actuator is energetically advantageous if the maximum opening cross section of both gas exchange valves is still sufficient for the full load range; because with blocking of the actuating piston in the first valve actuator, the entire excess force can be used to displace the actuating piston in the second valve actuator and to open the second gas exchange valve. The lifting speed of both gas exchange valves is pressure-dependent and is influenced by the overlap of the strokes in conjunction with the release of the outlet in the second working space of the first valve actuator to the second working space of the second valve actuator. This results in a pressure and stroke-dependent speed curve of the gas exchange valves.

Zeichnungdrawing

Die Erfindung ist anhand eines in der Zeichnung dargestellten Ausführungsbeispiels im folgenden näher beschrieben. Dabei zeigt die Zeichnung ein Schaltbild einer Vorrichtung zur Steuerung von zwei Gaswechselventilen in einem Verbrennungszylinder einer Brennkraftmaschine.The invention is described in more detail below with reference to an embodiment shown in the drawing. The drawing shows a circuit diagram of a device for controlling two gas exchange valves in a combustion cylinder of an internal combustion engine.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Mit der in Fig. 1 im Schaltbild dargestellten Vorrichtung zur Steuerung von Gaswechselventilen wird ein Paar Gaswechselventile 12, 13, die in einem nur ausschnittweise dargestellten Verbrennungszylinder 10 einer Brennkraftmaschine angeordnet sind, in Abhängigkeit eines Betriebskennfeldes der Brennkraftmaschine energieoptimal gesteuert. Bei den Gaswechselventilen 12, 13 kann es sich um Einlaßventile oder um Auslaßventile handeln, die einen im Verbrennungszylinder 10 ausgebildeten Brennraum 11 gasdicht abschließen. Jedes Gaswechselventil 12, 13 weist in bekannter Weise einen einen Öffnungsquerschnitt 14 im Verbrennungszylinder umschließenden Ventilsitz 15 und ein Ventilglied 16 mit einem auf einem axial verschieblich geführten Ventilschaft 161 sitzenden Ventilschließkörper 162 auf, der mit dem Ventilsitz 15 zum Schließen und Freigeben des Öffnungsquerschnitts 14 zusammenwirkt. Durch Verschieben des Ventilschafts 161 in die eine oder andere Axialrichtung hebt der Ventilschließkörper 162 vom Ventilsitz 15 ab oder legt sich auf den Ventilsitz 15 auf.With the device shown in Fig. 1 in the diagram for controlling gas exchange valves, a pair of gas exchange valves 12, 13, which are arranged in a combustion cylinder 10 of an internal combustion engine only partially shown, controlled in an energy-optimal manner depending on an operating map of the internal combustion engine. The gas exchange valves 12, 13 may be intake valves or exhaust valves which seal a combustion chamber 11 formed in the combustion cylinder 10 gas-tight. Each gas exchange valve 12, 13 has in known manner an opening cross-section 14 in the combustion cylinder enclosing the valve seat 15 and a valve member 16 with a seated on an axially displaceable valve stem 161 valve closing body 162 which cooperates with the valve seat 15 for closing and releasing the opening cross-section 14. By moving the valve stem 161 in one or the other axial direction, the valve closing body 162 lifts off the valve seat 15 or lies on the valve seat 15.

Die in der Zeichnung im Blockschaltbild dargestellte Vorrichtung zur Steuerung der beiden Gaswechselventile 12, 13 weist einen das Gaswechselventil 12 betätigenden ersten Ventilsteller 17 und einen das Gaswechselventil 13 betätigenden zweiten Ventilsteller 18 auf. Die beiden hydraulischen Ventilsteller 17, 18, auch Aktuatoren oder Aktoren genannt, greifen jeweils am Ventilschaft 161 der beiden Gaswechselventile 12, 13 an. Zur Ventilsteuervorrichtung gehören ferner eine Druckversorgungseinrichtung 19, die eine vorzugsweise regelbare Hochdruckpumpe 20, die Fluid, beispielsweise Hydrauliköl, aus einem Fluidreservoir 21 fördert, ein Rückschlagventil 22 und einen Druckspeicher 23 umfaßt. An dem zwischen Rückschlagventil 22 und Druckspeicher 23 abgegriffenen Ausgang 191 der Druckversorgungseinrichtung 19, dem noch ein zweites Rückschlagventil 24 mit zum Ausgang 191 weisender Durchlaßrichtung vorgeschaltet sein kann, steht ein permanenter, regelbarer Hochdruck an.The illustrated in the drawing in the block diagram device for controlling the two gas exchange valves 12, 13 has a gas exchange valve 12 actuated first valve actuator 17 and a gas exchange valve 13 actuated second valve actuator 18. The two hydraulic valve actuators 17, 18, also called actuators or actuators, respectively engage the valve stem 161 of the two gas exchange valves 12, 13. The valve control device further includes a Pressure supply device 19, which promotes a preferably controllable high-pressure pump 20, the fluid, for example hydraulic oil, from a fluid reservoir 21, a check valve 22 and a pressure accumulator 23 includes. At the tapped between the check valve 22 and pressure accumulator 23 output 191 of the pressure supply device 19, which may be preceded by a second check valve 24 facing the output 191 forward direction, is a permanent, adjustable high pressure on.

Die beiden hydraulischen Ventilsteller 17, 18 sind identisch ausgebildet und jeweils als doppeltwirkender Arbeitszylinder mit einem Zylindergehäuse 25 und einem darin axial verschieblich geführten Stellkolben 26 ausgebildet, der den Innenraum des Zylindergehäuses 25 in einen ersten Arbeitsraum 27 und einen zweiten Arbeitsraum 28 unterteilt. Die beiden ersten Arbeitsräume 27 der beiden Ventilsteller 17, 18 sind permanent mit dem Ausgang 191 der Druckversorgungseinrichtung. 19 verbunden. Der zweite Arbeitsraum 28 des ersten Ventilstellers 17 weist einen Einlaß 29 und zwei Auslässe 30, 31 auf, wobei der zweite Auslaß 31 in einem solchen Hubabstand vom ersten Auslaß 30 angeordnet ist, das in der in Fig. 1 dargestellten Schließstellung des Stellkolbens 26, in welchem er eine Schließung des Gaswechselventils 12 herbeigeführt hat, der zweite Auslaß 31 von dem Stellkolben 26 verschlossen ist und erst nach einem vorgegeben Öffnungshub des Stellkolbens 26 zum Öffnen des Gaswechselventils 12 zum zweiten Arbeitsraum 28 hin freigegeben wird. Der zweite Arbeitsraum 28 des zweiten Ventilstellers 18 hat einen Einlaß 32 und einen Auslaß 33. Der Einlaß 29 am ersten Ventilsteller 17 ist über ein erstes Steuerventil 3.4 mit dem Ausgang 191 der Druckversorgungseinrichtung 19 verbunden. Der erste Auslaß 30 des ersten Ventilstellers 17 ist an dem Ventileingang eines zweiten Steuerventils 35 angeschlossen, dessen Ventilausgang mit einem Rücklauf 36 zum Fluidreservoir 21 verbunden ist. Der Einlaß 32 am zweiten Ventilsteller 18 ist mit dem zweiten Auslaß 31 am ersten Ventilsteller 17 und der Auslaß 33 am zweiten Ventilsteller 18 über ein Rückschlagventil 37 mit dem Ventileinlaß des zweiten Steuerventils 35 verbunden: Die Durchlaßrichtung des Rückschlagventils 37 weist vom Auslaß 33 zum zweiten Steuerventil 35. Die beiden Steuerventile 34, 35 sind als 2/2-Wegemagnetventile mit Federrückstellung ausgebildet.The two hydraulic valve actuators 17, 18 are identically designed and each designed as a double-acting cylinder with a cylinder housing 25 and an axially displaceable guided therein actuator piston 26 which divides the interior of the cylinder housing 25 in a first working space 27 and a second working space 28. The two first working chambers 27 of the two valve actuators 17, 18 are permanently connected to the outlet 191 of the pressure supply device. 19 connected. The second working space 28 of the first valve actuator 17 has an inlet 29 and two outlets 30, 31, wherein the second outlet 31 is arranged at such a stroke distance from the first outlet 30, which in the closed position of the actuating piston 26 shown in FIG which he has brought about a closure of the gas exchange valve 12, the second outlet 31 is closed by the actuating piston 26 and is released to open the gas exchange valve 12 to the second working space 28 only after a predetermined opening stroke of the actuating piston 26. The second working chamber 28 of the second valve actuator 18 has an inlet 32 and an outlet 33. The inlet 29 on the first valve actuator 17 is via a first Control valve 3.4 connected to the output 191 of the pressure supply device 19. The first outlet 30 of the first valve actuator 17 is connected to the valve inlet of a second control valve 35, whose valve outlet is connected to a return line 36 to the fluid reservoir 21. The inlet 32 on the second valve actuator 18 is connected to the second outlet 31 on the first valve actuator 17 and the outlet 33 on the second valve actuator 18 via a check valve 37 to the valve inlet of the second control valve 35: The passage direction of the check valve 37 faces from the outlet 33 to the second control valve 35. The two control valves 34, 35 are designed as 2/2-way solenoid valves with spring return.

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

Ist, wie in der Zeichnung dargestellt, das erste Steuerventil 34 geschlossen und das zweite Steuerventil 35 geöffnet, so sind die beiden zweiten Arbeitsräume 28 der Ventilsteller 17, 18 drucklos, und der in den ersten Arbeitsräumen 27 der Ventilsteller 17, 18 anstehende Hochdruck der Druckversorgungseinrichtung 19 sorgt dafür, daß die Stellkolben 26 sich in ihren oberen Hubendstellung befinden und dadurch die Gaswechselventile 12, 13 in ihrer Schließstellung halten. In dieser oberen Hubendstellung oder Schließstellung verschließt der Stellkolben 26 im ersten Ventilsteller 17 den mit den Einlaß 32 am zweiten Ventilsteller 18 verbundenen zweiten Auslaß 31.Is, as shown in the drawing, the first control valve 34 is closed and the second control valve 35 is opened, the two second working chambers 28 of the valve actuator 17, 18 depressurized, and in the first working chambers 27 of the valve actuator 17, 18 pending high pressure of the pressure supply device 19 ensures that the actuating piston 26 are in their upper Hubendstellung and thereby keep the gas exchange valves 12, 13 in their closed position. In this upper stroke end position or closed position, the actuating piston 26 in the first valve actuator 17 closes the second outlet 31 connected to the inlet 32 on the second valve actuator 18.

Werden die Steuerventile 34, 35 umgeschaltet, so werden die zweiten Arbeitsräume 28 der beiden Ventilsteller 17, 18 von dem Rücklauf 36 abgesperrt und der zweite Arbeitsraum 28 des ersten Ventilstellers 17 mit dem Ausgang 191 der Druckversorgungseinrichtung 19 verbunden. Da die den zweiten Arbeitsraum 28 begrenzende Fläche des Stellkolbens 26 größer ist als die Wirkfläche des Stellkolbens 26 im ersten Arbeitsraum 27, bewirkt der im zweiten Arbeitsraum 28 anstehende Hochdruck, daß sich der Stellkolben 26 nach unten bewegt und über den Ventilschaft 161 den Ventilschließkörper 162 vom Ventilsitz 15 abhebt, so daß das Gaswechselventil 12 öffnet.If the control valves 34, 35 switched, the second working chambers 28 of the two valve actuators 17, 18 of shut off the return 36 and the second working space 28 of the first valve actuator 17 connected to the output 191 of the pressure supply device 19. Since the second working space 28 limiting surface of the actuating piston 26 is greater than the active surface of the actuating piston 26 in the first working space 27 causes the pending in the second working chamber 28 high pressure that the actuator piston 26 moves down and the valve stem 161 the valve closing body 162 from Valve seat 15 lifts so that the gas exchange valve 12 opens.

Je nach Betriebspunkt der Brennkraftmaschine müssen unterschiedliche Öffnungsquerschnitte 14 im Verbrennungszylinder 10 bereitgestellte werden, d. h. es muß nur ein Gaswechselventil 12 oder es müssen beide Gaswechselventile 12, 13 mit kleinerem oder größerem Hub angesteuert werden. Wird nun ein größerer Öffnungsquerschnitt gefordert, so wird nach einem definierten Hub des Stellkolbens 26 im ersten Ventilsteller 17 der Auslaß 31 vom Stellkolben 28 freigegeben so daß nunmehr sich auch Hochdruck im zweiten Arbeitsraum 28 des zweiten Ventilsteller 18 aufbaut. Der dadurch auf den Stellkolben 26 im zweiten Ventilsteller 18 wirkende Kraftüberschuß im zweiten Arbeitsraum 28 verschiebt nunmehr den Stellkolben 26, so daß auch das Ventilglied 13 öffnet.Depending on the operating point of the internal combustion engine different opening cross-sections 14 must be provided in the combustion cylinder 10, d. H. it only needs a gas exchange valve 12 or both gas exchange valves 12, 13 must be controlled with a smaller or larger stroke. Now, if a larger opening cross-section is required, then the outlet 31 is released by the actuating piston 28 after a defined stroke of the actuating piston 26 in the first valve plate 17 so that now also high pressure in the second working chamber 28 of the second valve actuator 18 builds up. The thus acting on the actuator piston 26 in the second valve actuator 18 excess force in the second working chamber 28 now shifts the actuator piston 26, so that the valve member 13 opens.

Die Auslegung des Abstands der beiden Auslässe 30, 31 am ersten Ventilsteller 17 erfolgt energieoptimal in Abhängigkeit von dem Betriebskennfeld der Brennkraftmaschine. Es ist auch möglich, den Hubabstand der beiden Auslässe 30, 31 steuerbar zu machen, indem beispielsweise der zweite Auslaß 31 in einen am Zylindergehäuse 25 verschiebbaren Stellring verlegt wird, der mit dem zweiten Arbeitsraum 28 flüssigkeitsdicht in Verbindung steht. Am Stellring greift ein Hubantrieb an, der von einem elektronischen Steuergerät gesteuert wird, das auch die beiden Steuerventile 34 und 35 steuert. Die axiale Verschieblichkeit des zweiten Auslasses 31 relativ zum ersten Auslaß 30 ist in der Zeichnung durch einen dem zweiten Auslaß 31 zugeordneten Doppelpfeil 39 symbolisiert. Alternativ können mehrere zweite Auslässe 31 in Hubrichtung des Stellkolbens 26 hintereinander angeordnet werden, die von dem Stellring nacheinander verschließbar sind.The design of the distance between the two outlets 30, 31 on the first valve actuator 17 is energy-optimal as a function of the operating map of the internal combustion engine. It is also possible to make the stroke distance of the two outlets 30, 31 controllable by, for example, the second Outlet 31 is moved into a displaceable on the cylinder housing 25 collar, which is liquid-tight with the second working space 28 in conjunction. On the collar attacks a lifting drive, which is controlled by an electronic control unit, which controls the two control valves 34 and 35. The axial displaceability of the second outlet 31 relative to the first outlet 30 is symbolized in the drawing by a second arrow 31 associated with the double arrow 39. Alternatively, a plurality of second outlets 31 in the stroke direction of the actuating piston 26 can be arranged one behind the other, which can be closed by the adjusting ring successively.

Die Hubhöhe des jeweiligen Gaswechselventils 12 bzw. 13 beim Öffnen hängt in erster Linie von der Ansteuerdauer des ersten Steuerventils 34 ab. Bei längerer Ansteuerung greift dann eine zumindest im ersten Ventilsteller 17 vorgesehene mechanische Hubbegrenzung. Die in der Zeichnung nur als Anschlag 38 schematisch angedeutete Hubbegrenzung ist beispielsweise so ausgelegt, daß der Stellkolben 26 im ersten Ventilsteller 17 kurz nach Freigeben des Auslasses 31 zum zweiten Arbeitsraum 28 des zweiten Ventilstellers 18 an einer weiteren Hubbewegung in Ventilöffnungsrichtung gehindert wird. Eine solche Hubbegrenzung ist energetisch sinnvoll, da dann nur noch hydraulische Energie zur Verstellung des Stellkolbens 26 im zweiten Ventilsteller 18 benötigt wird. Voraussetzung für eine solche Hubbegrenzung ist, daß die durch die Hubbegrenzung noch erreichbare Summe der Öffnungsquerschnitte 14 in beiden Gaswechselventilen 12, 13 für den Vollastbereich der Brennkraftmaschine ausreichend ist.The lift height of the respective gas exchange valve 12 or 13 during opening depends primarily on the activation duration of the first control valve 34. With prolonged control then engages provided at least in the first valve actuator 17 mechanical stroke limitation. The in the drawing only as a stop 38 schematically indicated stroke limitation is for example designed so that the actuating piston 26 is prevented in the first valve actuator 17 shortly after releasing the outlet 31 to the second working chamber 28 of the second valve actuator 18 at a further stroke in the valve opening direction. Such a stroke limitation makes energy sense, since then only hydraulic energy for adjusting the control piston 26 in the second valve actuator 18 is required. The prerequisite for such a stroke limitation is that the sum of the opening cross sections 14 still achievable by the stroke limitation is sufficient in both gas exchange valves 12, 13 for the full load range of the internal combustion engine.

Die Hubgeschwindigkeit der beiden Gaswechselventile 12, 13 ist in erster Linie druckabhängig und wird durch die Überschneidung der Hübe und die Freigabe der Verbindung zwischen den zweiten Arbeitsräumen 28 der beiden Ventilstellern 17, 18 beeinflußt.The lifting speed of the two gas exchange valves 12, 13 is primarily pressure-dependent and is influenced by the overlap of the strokes and the release of the connection between the second working chambers 28 of the two valve actuators 17, 18.

Claims (7)

  1. Device for the control of gas exchange valves (12, 13) in combustion cylinders (10) of an internal combustion engine, with hydraulic valve actuators (17, 18) which are assigned in each case to a gas exchange valve (12, 13) and which have in each case an actuating piston (26) acting on the gas exchange valve (12, 13) and two hydraulic working spaces (27, 28) which are delimited by the actuating piston (26) and of which the first working space (27) acting upon the gas exchange valve (12, 13) in a closing direction is filled constantly with a pressurized fluid and the second working space (28) acting upon the gas exchange valve (12, 13) in the opening direction can be alternately filled with a pressurized fluid and relieved via a first and a second electrical control valve (34, 35), characterized in that the filling of the second working space (28) of the second valve actuator (18) of a pair of valve actuators is carried out, via the second working space (28), connected to the first control valve (34), of the first valve actuator (17), after a predetermined stroke of the actuating piston (26) of the first valve actuator (17) in the opening direction of the assigned gas exchange valve (12).
  2. Device according to Claim 1, characterized in that the second working space (28) of the first valve actuator (17) has an inlet (29) connected to the first control valve (34) and two outlets (30, 31), of which a first outlet (30) is connected to the second control valve (35) and a second outlet (31) is connected to the second working space (28) of the second valve actuator (18), which second working space is connected, in turn, to the second control valve (35) via a non-return valve (37) having a shut-off direction pointing towards the second working space (28), and in that the second outlet (31) is arranged in the second working space (28) of the first valve actuator (17) at a stroke distance from the first outlet (30) such that the said second outlet is closed by the actuating piston (26) of the first valve actuator (17), in its closing position causing the closing of the assigned gas exchange valve (12), and, after a predetermined stroke of the actuating piston (26), is released in an opening direction causing the opening of the assigned gas exchange valve (12).
  3. Device according to Claim 2, characterized in that the mutual stroke distance between the two outlets (30, 31) on the first valve actuator (17) can be varied in a controlled way.
  4. Device according to Claim 2 or 3, characterized in that the second working space (28) of the second valve actuator (18) has an inlet (32) connected to the second outlet (31) on the first valve actuator (17) and an outlet (33) connected to the non-return valve (37).
  5. Device according to one of Claims 2-4, characterized in that the first valve actuator (17) has a mechanical stroke limitation (38) which is designed such that it blocks a further stroke movement of the actuating piston (26) in the opening direction of the assigned gas exchange valve (12) after the release of the second outlet (31) by the actuating piston (26).
  6. Device according to one of Claims 1-5, characterized in that the two gas exchange valves (12, 13) actuated by the first and the second valve actuator (17, 18) are arranged in the same combustion cylinder (10).
  7. Device according to one of Claims 1-8, characterized in that the gas exchange valves (12, 13) assigned to the first and the second valve actuator (17, 18) are used as inlet or outlet valves.
EP02760102A 2001-10-24 2002-07-18 Device for controlling gas exchange valves Expired - Lifetime EP1440224B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10152503A DE10152503A1 (en) 2001-10-24 2001-10-24 Device for controlling gas exchange valves
DE10152503 2001-10-24
PCT/DE2002/002630 WO2003038245A1 (en) 2001-10-24 2002-07-18 Device for controlling gas exchange valves

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EP1440224A1 EP1440224A1 (en) 2004-07-28
EP1440224B1 true EP1440224B1 (en) 2007-09-26

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US (1) US7089896B2 (en)
EP (1) EP1440224B1 (en)
JP (1) JP2005507045A (en)
KR (1) KR20040048980A (en)
DE (2) DE10152503A1 (en)
WO (1) WO2003038245A1 (en)

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DE102007021109A1 (en) * 2007-05-03 2008-11-13 Jan Mendzigall Valve for internal combustion engine, is ideally brought, clocked by drive, into one position for closing or opening combustion chamber
US10338672B2 (en) 2011-02-18 2019-07-02 Business Objects Software Ltd. System and method for manipulating objects in a graphical user interface
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
EP3406866A1 (en) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Hydraulic drive for accelerating and braking components to be dynamically moved

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US5497736A (en) * 1995-01-06 1996-03-12 Ford Motor Company Electric actuator for rotary valve control of electrohydraulic valvetrain
US5572961A (en) * 1995-04-05 1996-11-12 Ford Motor Company Balancing valve motion in an electrohydraulic camless valvetrain
US5636602A (en) * 1996-04-23 1997-06-10 Caterpillar Inc. Push-pull valve assembly for an engine cylinder
DE19826047A1 (en) 1998-06-12 1999-12-16 Bosch Gmbh Robert Device for controlling a gas exchange valve for internal combustion engines

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EP1440224A1 (en) 2004-07-28
DE10152503A1 (en) 2003-05-08
JP2005507045A (en) 2005-03-10
DE50210991D1 (en) 2007-11-08
US20040079308A1 (en) 2004-04-29
KR20040048980A (en) 2004-06-10
WO2003038245A1 (en) 2003-05-08
US7089896B2 (en) 2006-08-15

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