EP1440224A1 - Device for controlling gas exchange valves - Google Patents

Device for controlling gas exchange valves

Info

Publication number
EP1440224A1
EP1440224A1 EP02760102A EP02760102A EP1440224A1 EP 1440224 A1 EP1440224 A1 EP 1440224A1 EP 02760102 A EP02760102 A EP 02760102A EP 02760102 A EP02760102 A EP 02760102A EP 1440224 A1 EP1440224 A1 EP 1440224A1
Authority
EP
European Patent Office
Prior art keywords
valve
gas exchange
outlet
valve actuator
valves
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP02760102A
Other languages
German (de)
French (fr)
Other versions
EP1440224B1 (en
Inventor
Udo Diehl
Bernd Rosenau
Simon Kieser
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1440224A1 publication Critical patent/EP1440224A1/en
Application granted granted Critical
Publication of EP1440224B1 publication Critical patent/EP1440224B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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 the actuating piston of which is connected in one piece to the valve tappet of the associated gas exchange valve, is constantly connected to a high-pressure source with its first working chamber and, on the one hand, to a supply line to the one with its second working chamber High-pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a second control valve alternately releasing or closing a relief line.
  • the electrical control valves are designed as 2/2-way solenoid valves with spring return. With de-energized control valves, the first work area is still under high pressure, while the second work space is separated from the high pressure source and connected to the relief line. The gas exchange valve is closed.
  • Both control valves are energized to open the gas exchange valve. Due to the switching control valves, the second working space of the valve actuator is blocked on the one hand by the second control valve with respect to the relief line and on the other hand connected to the supply line to the high pressure source by the first control valve.
  • the gas exchange valve opens, the size of the opening stroke depending on the formation of the electrical control signal applied to the first electrical control valve and the opening speed on the pressure applied by the high pressure source.
  • the first control valve is then switched off so that it shuts off the supply line to the second working area of the valve actuator. In this way, all valve opening positions of the gas exchange valve can be set by means of an electrical control device for generating control signals.
  • two electrical control valves are required, which act accordingly on the assigned valve actuator with hydraulic pressure.
  • the inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that one by the direct hydraulic coupling of the second working spaces of two valve actuators
  • Valve actuator pairs for the implementation of the hydraulic Energy in a linear movement of the gas exchange valves the number of control valves required for the control of two valve actuators is reduced from four to just two. Since this also halves the number of output stages required to control the control valves in the electronic control unit and thus also reduces the wiring effort, the overall manufacturing costs for the control device can be significantly reduced. In addition, the installation space required is reduced due to the elimination of components and cabling, the low number of valves reduces the probability of failure of the control valves, and both the hydraulic and electrical energy requirements are reduced.
  • the two gas exchange valves actuated by the first and second valve actuators are in the same
  • Gas exchange valve of the same combustion cylinder in part could already dismantle via the opened first gas exchange valve.
  • At least the first valve actuator has a mechanical stroke limitation, which is designed such that it blocks the further stroke movement of the actuating piston in the valve opening direction after the outlet on the first valve actuator connected to the second working space of the second valve actuator is released.
  • 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; By blocking the control piston in the first valve actuator, the entire excess force can be used to displace the control piston in the second valve actuator and to open the second gas exchange valve.
  • the stroke speed of both gas exchange valves is pressure-dependent and is influenced by the overlap of the strokes in connection 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 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. Description of the embodiment
  • the gas exchange valves 12, 13 can be intake valves or exhaust valves which close a combustion chamber 11 formed in the combustion cylinder 10 in a gas-tight manner.
  • Each gas exchange valve 12, 13 has, in a known manner, a valve seat 15 enclosing an opening cross section 14 in the combustion cylinder and a valve member 16 with a valve closing body 162 seated on an axially displaceably guided valve stem 161, 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 device for controlling the two gas exchange valves 12, 13 shown in the drawing in the block diagram has a first valve actuator 17 actuating the gas exchange valve 12 and a second valve actuator 18 actuating the gas exchange valve 13.
  • Valve control devices also include one Pressure supply device 19, which comprises a preferably controllable high-pressure pump 20, which conveys fluid, for example hydraulic oil, from a fluid reservoir 21, a check valve 22 and a pressure accumulator 23.
  • a permanent, controllable high pressure is present at the outlet 191 of the pressure supply device 19 tapped between the nonreturn valve 22 and the pressure accumulator 23, which can also be preceded by a second nonreturn valve 24 with the passage direction pointing towards the outlet 191.
  • the two hydraulic valve actuators 17, 18 are of identical design and each are designed as double-acting working cylinders with a cylinder housing 25 and an actuating piston 26 which is axially displaceable therein and divides the interior of the cylinder housing 25 into a first working chamber 27 and a second working chamber 28.
  • the first two working spaces 27 of the two valve actuators 17, 18 are permanently connected to the outlet 191 of the pressure supply device 19.
  • the second working chamber 28 of the first valve actuator 17 has an inlet 29 and two outlets 30, 31, the second outlet 31 being arranged at such a stroke distance from the first outlet 30 that 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 only released after a predetermined opening stroke of the actuating piston 26 to open the gas exchange valve 12 to the second working space 28.
  • the second working space 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 with the outlet 191 of the
  • Pressure supply device 19 connected.
  • the first outlet 30 of the first valve actuator 17 is connected to the valve inlet of a second control valve 35, the valve outlet of which is connected to a return 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 is connected via a check valve 37 to the valve inlet of the second control valve 35.
  • the direction of passage of the check valve 37 points 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 mode of action of. Valve control device is as follows:
  • the two second working spaces 28 of the valve actuators 17, 18 are depressurized, and the high pressure of the pressure supply device present in the first working spaces 27 of the valve actuators 17, 18 19 ensures that the actuating pistons 26 are in their upper stroke end position and thereby hold 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 second working spaces 28 of the two valve actuators 17, 18 of the return 36 is shut off and the second working chamber 28 of the first valve actuator 17 is connected to the outlet 191 of the pressure supply device 19. Since the area of the actuating piston 26 delimiting the second working chamber 28 is larger than the effective area of the actuating piston 26 in the first working chamber 27, the high pressure present in the second working chamber 28 causes the actuating piston 26 to move downward and via the valve stem 161 the valve closing body 162 lifts off the valve seat 15 so that the gas exchange valve 12 opens.
  • Gas exchange valves 12, 13 are controlled with a smaller or larger stroke. If a larger opening cross-section is now required, after a defined stroke of the actuating piston 26 in the first valve actuator 17, the outlet 31 is released by the actuating piston 28 so that high pressure now also builds up in the second working space 28 of the second valve actuator 18. The excess force in the second working chamber 28 which acts on the actuating piston 26 in the second valve actuator 18 now displaces the actuating piston 26, so that the valve member 13 also opens.
  • the spacing of the two outlets 30, 31 on the first valve actuator 17 is designed in an energy-optimal manner 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, for example by the second one Outlet 31 is moved into a displaceable adjusting ring on the cylinder housing 25, which is in liquid-tight connection with the second working chamber 28. A lifting drive acts on the adjusting ring and is controlled by an electronic control device which also 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 double arrow 39 assigned to the second outlet 31.
  • a plurality of second outlets 31 can be arranged one behind the other in the stroke direction of the adjusting piston 26 and can be closed one after the other by the adjusting ring.
  • the lifting height of the respective gas exchange valve 12 or 13 when opening depends primarily on the actuation duration of the first control valve 34.
  • a mechanical stroke limitation provided at least in the first valve actuator 17 then takes effect.
  • the stroke limitation schematically indicated in the drawing only as a stop 38 is designed, for example, in such a way that the actuating piston 26 in the first valve actuator 17 is prevented from a further stroke movement in the valve opening direction shortly after the outlet 31 is released to the second working space 28 of the second valve actuator 18.
  • Such a stroke limitation makes sense energetically, since then only hydraulic energy for adjusting the
  • Actuating piston 26 is required in the second valve actuator 18.
  • a prerequisite for such a stroke limitation is that the sum of the opening cross sections 14 in both gas exchange valves 12, 13 that can still be achieved by the stroke limitation is sufficient for the full-load range of the internal combustion engine.
  • the stroke 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 spaces 28 of the two valve actuators 17, 18.

Landscapes

  • 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

Vorrichtung zur Steuerung von GaswechselventilenDevice for controlling gas exchange valves
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 AI) 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 Entlästungsleitung 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 AI), each valve actuator, the actuating piston of which is connected in one piece to the valve tappet of the associated gas exchange valve, is constantly connected to a high-pressure source with its first working chamber and, on the one hand, to a supply line to the one with its second working chamber High-pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a second control valve alternately releasing or closing a relief line. The electrical control valves are designed as 2/2-way solenoid valves with spring return. With de-energized control valves, the first work area is still under high pressure, while the second work space is separated from the high pressure source and connected to the relief line. The gas exchange valve is closed. Both control valves are energized to open the gas exchange valve. Due to the switching control valves, the second working space of the valve actuator is blocked on the one hand by the second control valve with respect to the relief line and on the other hand connected to the supply line to the high pressure source by the first control valve. The gas exchange valve opens, the size of the opening stroke depending on the formation of the electrical control signal applied to the first electrical control valve and the opening speed on the pressure applied by the high pressure source. In order to keep the gas exchange valve in a certain open position, the first control valve is then switched off so that it shuts off the supply line to the second working area of the valve actuator. In this way, all valve opening positions of the gas exchange valve can be set by means of an electrical control device for generating control signals. To control a gas exchange valve, two electrical control valves are required, which act accordingly on the assigned valve actuator with 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 einesThe inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that one by the direct hydraulic coupling of the second working spaces of two valve actuators
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.Valve actuator pairs for the implementation of the hydraulic Energy in a linear movement of the gas exchange valves the number of control valves required for the control of two valve actuators is reduced from four to just two. Since this also halves the number of output stages required to control the control valves in the electronic control unit and thus also reduces the wiring effort, the overall manufacturing costs for the control device can be significantly reduced. In addition, the installation space required is reduced due to the elimination of components and cabling, the low number of valves reduces the probability of failure of the control valves, and both the hydraulic and electrical energy requirements are reduced.
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 allow advantageous developments and improvements of the device for controlling gas exchange valves specified in claim 1.
Gemäß einer bevorzugten Ausführungsform der Erfindung sind die beiden von dem ersten und zweiten Ventilsteller betätigten Gaswechselventile in demselbenAccording to a preferred embodiment of the invention, the two gas exchange valves actuated by the first and second valve actuators are in the same
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 zweitenCombustion cylinder of the internal combustion engine arranged. This has the advantage that the excess force of the second valve actuator for opening the associated gas exchange valve does not have to be designed at the same level as that of the first valve actuator, which has to open the associated gas exchange valve against the maximum counterpressure occurring in the combustion cylinder, but can be designed to be lower , because the counterforce to open the second
Gaswechselventils des gleichen Verbrennungszylinders zum Teil bereits über das geöffnete erste Gaswechselventil abbauen konnte.Gas exchange valve of the same combustion cylinder in part could already dismantle via the opened 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 has a mechanical stroke limitation, which is designed such that it blocks the further stroke movement of the actuating piston in the valve opening direction after the outlet on the first valve actuator connected to the second working space of the second valve actuator is released. 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; By blocking the control piston in the first valve actuator, the entire excess force can be used to displace the control piston in the second valve actuator and to open the second gas exchange valve. The stroke speed of both gas exchange valves is pressure-dependent and is influenced by the overlap of the strokes in connection 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. Beschreibung des AusführungsbeispielsThe invention is described 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. Description 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 for controlling gas exchange valves shown in the circuit diagram in FIG. 1, a pair of gas exchange valves 12, 13, which are arranged in a combustion cylinder 10 of an internal combustion engine, which is only shown in part, are controlled in an energy-optimized manner as a function of an operating map of the internal combustion engine. The gas exchange valves 12, 13 can be intake valves or exhaust valves which close a combustion chamber 11 formed in the combustion cylinder 10 in a gas-tight manner. Each gas exchange valve 12, 13 has, in a known manner, a valve seat 15 enclosing an opening cross section 14 in the combustion cylinder and a valve member 16 with a valve closing body 162 seated on an axially displaceably guided valve stem 161, 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. ZurThe device for controlling the two gas exchange valves 12, 13 shown in the drawing in the block diagram has a first valve actuator 17 actuating the gas exchange valve 12 and a second valve actuator 18 actuating the gas exchange valve 13. The two hydraulic valve actuators 17, 18, also called actuators, each act on the valve stem 161 of the two gas exchange valves 12, 13. to
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.Valve control devices also include one Pressure supply device 19, which comprises a preferably controllable high-pressure pump 20, which conveys fluid, for example hydraulic oil, from a fluid reservoir 21, a check valve 22 and a pressure accumulator 23. A permanent, controllable high pressure is present at the outlet 191 of the pressure supply device 19 tapped between the nonreturn valve 22 and the pressure accumulator 23, which can also be preceded by a second nonreturn valve 24 with the passage direction pointing towards the outlet 191.
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.The two hydraulic valve actuators 17, 18 are of identical design and each are designed as double-acting working cylinders with a cylinder housing 25 and an actuating piston 26 which is axially displaceable therein and divides the interior of the cylinder housing 25 into a first working chamber 27 and a second working chamber 28. The first two working spaces 27 of the two valve actuators 17, 18 are permanently connected to the outlet 191 of the pressure supply device 19. The second working chamber 28 of the first valve actuator 17 has an inlet 29 and two outlets 30, 31, the second outlet 31 being arranged at such a stroke distance from the first outlet 30 that 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 only released after a predetermined opening stroke of the actuating piston 26 to open the gas exchange valve 12 to the second working space 28. The second working space 28 of the second valve actuator 18 has an inlet 32 and an outlet 33.
Der Einlaß 29 am ersten Ventilsteller 17 ist über ein erstes Steuerventil 3.4 mit dem Ausgang 191 derThe inlet 29 on the first valve actuator 17 is via a first Control valve 3.4 with the outlet 191 of the
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.Pressure supply device 19 connected. The first outlet 30 of the first valve actuator 17 is connected to the valve inlet of a second control valve 35, the valve outlet of which is connected to a return 36 to the fluid reservoir 21.
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 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 is connected via a check valve 37 to the valve inlet of the second control valve 35. The direction of passage of the check valve 37 points 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 mode of action of. 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.If, as shown in the drawing, the first control valve 34 is closed and the second control valve 35 is open, the two second working spaces 28 of the valve actuators 17, 18 are depressurized, and the high pressure of the pressure supply device present in the first working spaces 27 of the valve actuators 17, 18 19 ensures that the actuating pistons 26 are in their upper stroke end position and thereby hold 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 Ventilschliefi>körper 162 vom Ventilsitz 15 abhebt, so daß das Gaswechselventil 12 öffnet.If the control valves 34, 35 are switched over, the second working spaces 28 of the two valve actuators 17, 18 of the return 36 is shut off and the second working chamber 28 of the first valve actuator 17 is connected to the outlet 191 of the pressure supply device 19. Since the area of the actuating piston 26 delimiting the second working chamber 28 is larger than the effective area of the actuating piston 26 in the first working chamber 27, the high pressure present in the second working chamber 28 causes the actuating piston 26 to move downward and via the valve stem 161 the valve closing body 162 lifts off the valve seat 15 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 beideDepending on the operating point of the internal combustion engine, different opening cross sections 14 must be provided in the combustion cylinder 10, i. H. it only needs one gas exchange valve 12 or both
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.Gas exchange valves 12, 13 are controlled with a smaller or larger stroke. If a larger opening cross-section is now required, after a defined stroke of the actuating piston 26 in the first valve actuator 17, the outlet 31 is released by the actuating piston 28 so that high pressure now also builds up in the second working space 28 of the second valve actuator 18. The excess force in the second working chamber 28 which acts on the actuating piston 26 in the second valve actuator 18 now displaces the actuating piston 26, so that the valve member 13 also 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 spacing of the two outlets 30, 31 on the first valve actuator 17 is designed in an energy-optimal manner 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, for example by the second one Outlet 31 is moved into a displaceable adjusting ring on the cylinder housing 25, which is in liquid-tight connection with the second working chamber 28. A lifting drive acts on the adjusting ring and is controlled by an electronic control device which also 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 double arrow 39 assigned to the second outlet 31. Alternatively, a plurality of second outlets 31 can be arranged one behind the other in the stroke direction of the adjusting piston 26 and can be closed one after the other by the adjusting ring.
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 desThe lifting height of the respective gas exchange valve 12 or 13 when opening depends primarily on the actuation duration of the first control valve 34. In the event of longer activation, a mechanical stroke limitation provided at least in the first valve actuator 17 then takes effect. The stroke limitation schematically indicated in the drawing only as a stop 38 is designed, for example, in such a way that the actuating piston 26 in the first valve actuator 17 is prevented from a further stroke movement in the valve opening direction shortly after the outlet 31 is released to the second working space 28 of the second valve actuator 18. Such a stroke limitation makes sense energetically, since then only hydraulic energy for adjusting the
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. 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. Actuating piston 26 is required in the second valve actuator 18. A prerequisite for such a stroke limitation is that the sum of the opening cross sections 14 in both gas exchange valves 12, 13 that can still be achieved by the stroke limitation is sufficient for the full-load range of the internal combustion engine. The stroke 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 spaces 28 of the two valve actuators 17, 18.

Claims

Ansprüche Expectations
1. Vorrichtung zur Steuerung von Gaswechselventilen (12, 13) in Verbrennungszylindern (10) einer Brennkraftmaschine mit jeweils einem Gaswechselventil (12, 13) zugeordneten, hydraulischen Ventilstellern (17, 18), die jeweils einen auf das Gaswechselventil (12, 13) wirkenden Stellkolben (26) und zwei von dem Stellkolben1. Device for controlling gas exchange valves (12, 13) in combustion cylinders (10) of an internal combustion engine, each with a gas exchange valve (12, 13) associated with hydraulic valve actuators (17, 18), each acting on the gas exchange valve (12, 13) Actuating piston (26) and two of the actuating piston
(26) begrenzte hydraulische Arbeitsräume (27, 28) aufweisen, von denen der das Gaswechselventil (12, 13) in Schließrichtung beaufschlagende erste Arbeitsraum(26) have limited hydraulic work spaces (27, 28), of which the first work space acting on the gas exchange valve (12, 13) in the closing direction
(27) ständig mit einem unter Druck stehenden Fluid befüllt ist und der das Gaswechselventil (12, 13) in(27) is constantly filled with a pressurized fluid and the gas exchange valve (12, 13) in
Öffnungsrichtung beaufschlagende zweite Arbeitsraum (28) über ein erstes und zweites elektrisches Steuerventil (34, 35) wechselweise mit einem unter Druck stehenden Fluid befüllbar und entlastbar ist, dadurch gekennzeichnet, daß die Befüllung des zweitenThe second working chamber (28) acting on the opening direction can be alternately filled and relieved with a pressurized fluid via a first and second electrical control valve (34, 35), characterized in that the filling of the second
Arbeitsraums (28) des zweiten Ventilstellers (18) eines Ventilstellerpaars über den mit dem ersten Steuerventil (34) verbundenen zweiten Arbeitsraum (28) des ersten Ventilstellers (17) nach einem vorgegebenen Hub des Stellkolbens (26) des ersten Ventilstellers (17) in Richtung Öffnen des zugeordneten Gaswechselventils (12) vorgenommen ist .Working space (28) of the second valve actuator (18) of a pair of valve actuators via the second working space (28) of the first valve actuator (17) connected to the first control valve (34) after a predetermined stroke of the actuating piston (26) of the first valve actuator (17) in Direction of opening the associated gas exchange valve (12) is made.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der zweite Arbeitsraum (28) des ersten Ventilstellers2. Device according to claim 1, characterized in that the second working space (28) of the first valve actuator
(17) einen mit dem ersten Steuerventil (34) verbundenen Einlaß (29) und zwei Auslässe (30, 31) aufweist, von denen ein erster Auslaß (30) mit dem zweiten Steuerventil (35) und ein zweiter Auslaß (31) mit dem zweiten Arbeitsraum (28) des zweiten Ventilstellers (18) verbunden ist, der seinerseits über ein Rückschlagventil (37) mit zum zweiten Arbeitsraum (28) weisender Sperrichtung an dem zweiten Steuerventil (35) angeschlossen ist, und daß der zweite Auslaß (31) im zweiten Arbeitsraum (28) des ersten Ventilstellers (17) in einem solchen Hubabstand vom ersten Auslaß (30) angeordnet ist, daß er vom Stellkolben (26) des ersten Ventilstellers (17) in dessen das Schließen des zugeordneten Gaswechselventils (12) bewirkenden Schließstellung verschlossen ist und nach einem vorgegebenen Hub des Stellkolbens (26) in eine das Öffnen des zugeordneten Gaswechselventils (12) bewirkende Öffnungsrichtung freigegeben wird.(17) has an inlet (29) connected to the first control valve (34) and two outlets (30, 31), of which a first outlet (30) with the second control valve (35) and a second outlet (31) with the second working chamber (28) of the second valve actuator (18) is connected, which in turn is connected to the second control valve (35) via a check valve (37) with the blocking direction pointing to the second working chamber (28), and that the second outlet (31) in second working chamber (28) of the first valve actuator (17) is arranged at such a stroke distance from the first outlet (30) that it is closed by the actuating piston (26) of the first valve actuator (17) in its closed position causing the associated gas exchange valve (12) to close and after a predetermined stroke of the actuating piston (26) is released in an opening direction causing the associated gas exchange valve (12) to open.
3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der gegenseitige Hubabstand der beiden Auslässe (30, 31) am ersten Ventilsteller (17) gesteuert variierbar ist.3. Apparatus according to claim 2, characterized in that the mutual stroke distance of the two outlets (30, 31) on the first valve actuator (17) can be varied in a controlled manner.
4. Vorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der zweite Arbeitsraum (28) des zweiten Ventilstellers (18) einen mit dem zweiten Auslaß (31) am ersten Ventilsteller (17) verbundenen Einlaß4. Apparatus according to claim 2 or 3, characterized in that the second working space (28) of the second valve actuator (18) one with the second outlet (31) at the first valve actuator (17) connected inlet
(32) und einen an dem Rückschlagventil (37) angeschlossenen Auslaß (33) aufweist.(32) and an outlet (33) connected to the check valve (37).
5. Vorrichtung nach einem der Ansprüche 2 - 4, dadurch gekennzeichnet, daß der erste Ventilsteller (17) eine mechanische Hubbegrenzung (38) aufweist, die so ausgelegt ist, daß sie nach Freigeben des zweiten Auslasses (31) durch den Stellkolben (26) eine weitere Hubbewegung des Stellkolbens (26) in Richtung Öffnen des zugeordneten Gaswechselventils (12) blockiert.5. Device according to one of claims 2-4, characterized in that the first valve actuator (17) has a mechanical stroke limiter (38) which is designed such that it is released by the actuating piston (26) after the second outlet (31) has been released. a further stroke movement of the actuating piston (26) in the direction of opening the associated gas exchange valve (12) is blocked.
6. Vorrichtung nach einem der Ansprüche 1 - 5, dadurch gekennzeichnet, daß die beiden von dem ersten und zweiten Ventilsteller (17, 18) betätigten Gaswechselventile (12, 13) in demselben Verbrennungszylinder (10) angeordnet sind.6. Device according to one of claims 1-5, characterized in that the two by the first and second valve actuators (17, 18) actuated gas exchange valves (12, 13) are arranged in the same combustion cylinder (10).
7. Vorrichtung nach einem der Ansprüche 1 - 8, dadurch gekennzeichnet, daß die dem ersten und zweiten7. Device according to one of claims 1-8, characterized in that the first and second
Ventilsteller (17, 18) zugeordneten Gaswechselventile (12, 13) als Ein- oder Auslaßventile eingesetzt sind. Valve actuators (17, 18) associated with gas exchange valves (12, 13) 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)

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

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EP (1) EP1440224B1 (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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WO2003038245A1 (en) 2003-05-08
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US7089896B2 (en) 2006-08-15
EP1440224B1 (en) 2007-09-26

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