EP1415070B1 - Device for controlling gas exchange valves - Google Patents

Device for controlling gas exchange valves Download PDF

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Publication number
EP1415070B1
EP1415070B1 EP02745076A EP02745076A EP1415070B1 EP 1415070 B1 EP1415070 B1 EP 1415070B1 EP 02745076 A EP02745076 A EP 02745076A EP 02745076 A EP02745076 A EP 02745076A EP 1415070 B1 EP1415070 B1 EP 1415070B1
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EP
European Patent Office
Prior art keywords
valve
valves
control
gas exchange
case
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EP02745076A
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German (de)
French (fr)
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EP1415070A1 (en
Inventor
Udo Diehl
Bernd Rosenau
Uwe Hammer
Volker Beuche
Peter Lang
Stefan Reimer
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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

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 In a known device of this type (DE 198 26 047 A1) is each valve actuator, the actuator 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 its second working space on the one hand to a supply to the High pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a discharge line alternately releasing or closing second control valve.
  • 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 use of a composed of a first and a second electrical control valve control valve pair for the alternating control of total two valve actuators two electrical control valves per valve pair can be saved. Since the electrical control valves designed primarily as 2/2-way solenoid valves must realize extremely short switching times, in practice about 0.3 ms with an opening cross-section of 3 mm 2 , such control valves are very expensive, so that the reduction of the number of control valves in the control device brings a significant cost savings. Due to the smaller number of electrical control valves, the number of power amplifiers and the amount of electrical wiring for the control of the control valves is reduced, which leads to a further cost savings.
  • the switching of the control valves by means of two trained as 3/2-way valves switching valves is made, of which three controlled valve connections of the first with the first and second electrical control valve is connected and the two alternately alsschaltbaren on the first valve port further valve connections are connected to the second working spaces of the two valve actuators.
  • Simple change-over valves which can be controlled electrically or hydraulically, are very inexpensive as mass-produced articles, especially when no fast switching times are required.
  • the common closed state of two gas exchange valves in combustion cylinders with a 360 ° crank angle offset their ignition extends over a crank angle range of about 60 °, is a sufficiently large period of time for the reversal of the changeover valves available.
  • the switching valves are, especially if they are hydraulically controlled, compared to the 2/2-way solenoid valves quite small, so that also reduces the space required for the valve control device space requirement compared to the known valve control.
  • the invention is at the control input of the hydraulically controlled changeover valves' permanently on a hydraulic pressure, which is increased for reversing the change-over valves in their working position by means of a reciprocating piston.
  • the reciprocating piston can be driven by a cam which rotates with respect to the rotational speed of the crankshaft and can be driven to rotate in a pressure chamber communicating with the respective control input.
  • the illustrated in the circuit diagram in Fig. 1 apparatus for controlling gas exchange valves in combustion cylinders of an internal combustion engine is used to control a total of four gas exchange valves 10 (Fig. 2), of which one is arranged in a combustion cylinder of a four-cylinder four-stroke engine.
  • the gas exchange valves 10 may be the intake valves or the exhaust valves of the combustion cylinders.
  • the combustion cylinders, not shown here are symbolic with I, II, III and IV, which are assigned in Fig. 1 the valve actuators 11 for the gas exchange valves 10 of the respective combustion cylinder.
  • the device has a total of four hydraulic valve actuator 11, one of which is associated with a gas exchange valve 10 in the combustion cylinders I - IV.
  • Each valve actuator 11 has a working cylinder 12 in which an actuating piston 13 is guided axially displaceable.
  • the actuating piston 13 divides the working cylinder 12 in two limited by him, hydraulic working spaces 121 and 122 and is fixedly connected to the valve stem 14 of the gas exchange valve 10.
  • a valve plate 11 is shown schematically in conjunction with a gas exchange valve 10 in an enlarged view.
  • the valve stem 14 carries at its end remote from the actuating piston 13 a plate-shaped valve sealing surface 15 which cooperates to control an opening cross section with a formed on the housing 16 of the combustion cylinder of the engine valve seat surface 17.
  • the working cylinder 12 has a total of three hydraulic connections, of which two hydraulic connections 122a and 122b open in the second working space 122 and a hydraulic connection 121a in the first working space 121.
  • the device further comprises a pressure supply device 22, which consists of a fluid reservoir 18, a prefeed pump 29, a high pressure pump 19, a check valve 20 and a memory 21 for pulsation damping and energy storage.
  • a pressure supply device 22 which consists of a fluid reservoir 18, a prefeed pump 29, a high pressure pump 19, a check valve 20 and a memory 21 for pulsation damping and energy storage.
  • the tapped between the check valve 20 and the memory 21 output 221 of Pressure supply device 22 is connected via a line 23 to all hydraulic ports 121a of the four valve actuators 11, so that the first working chambers 121 of the valve plate 11 are constantly acted upon by the output 221 of the pressure supply device 22 pending hydraulic pressure.
  • the second working chambers 122 of the working cylinders 12 are connected on the one hand via first electrical control valves 24 and 26 to the output 221 of the pressure supply device 22 and on the other hand via second electrical control valves 25 and 27 to a discharge line 28, which in turn opens into the fluid reservoir 18.
  • All control valves 24-27 are designed as 2/2-way solenoid valves with spring return. In each case, a first control valve 24 or 26 and a second control valve 25 and 27 form a control valve pair, with the respective two valve actuators 11 are controlled alternately.
  • the two valve actuators 11 controlled by the control valve pairs 24, 25 and 26, 27 are each associated with gas exchange valves 10 in combustion cylinders of this type whose ignition times are offset by 360 ° crank angle from one another.
  • control valve pair 24, 25 controls the two valve actuators 11 of the gas exchange valves 10 in the first and third combustion cylinders I and III and the control valve pair 26, 27, the valve plate 11 for the gas exchange valves 10 in the second and fourth combustion cylinder II and IV, wherein the control of each two valve actuator 11 takes place alternately and the switching of the control valve pair 24, 25 or 26, 27 of the one valve actuator 11 to the other valve actuator 11 during the closed state of the two of the Valve actuators 11 actuated gas exchange valves 10 is performed.
  • the Umschaltüng the two control valves 24 and 25 or 26 and 27 of each control valve pair is synchronous.
  • switching valves 30 - 33 For switching the two control valve pairs 24, 25 and 26, 27 of the one valve actuator 11 to the other valve actuator 11 is effected by switching valves 30 - 33, which are formed in the embodiment of FIG. 1 as a hydraulically controlled 3/2-way valves with spring return.
  • Each switching valve 30-33 has two switching positions and three controlled valve ports 34-36, of which the first valve port 34 is connected to the respective associated control valves 24 and 25 or 26 and 27 and the two connectable to the first valve port 34 further valve ports 35th and 36 are connected to the second working spaces 122 of the valve actuator 11.
  • the first valve port 34 to the first control valve 24, the second valve port 25 to the second working chamber 122 of the valve actuator 11 for the first combustion cylinder I and the second valve port 36 to the second working space 122 of the valve actuator 11 for the third combustion cylinder III connected.
  • the first valve port 34 of the switching valve 31 is connected to the second control valve 25, the second valve port 35 to the second working space 122 of the valve actuator 11 for the first combustion cylinder I and the third valve port 36 to the working space 122 of the valve actuator 11 for the third combustion cylinder III.
  • the control of the changeover valves 30-33 is hydraulically against the spring force of a return spring, to which the control inputs of the changeover valves 30 and 31 via a check valve 37 and the control inputs of the changeover valves 32 and 33 are connected via a check valve 38 to the outlet of the prefeed pump 29.
  • the switching valves 30-33 are designed so that they can not be moved out of their rest position shown in Fig. 1 by the pending at the outlet of the prefeed pump 29 hydraulic pressure.
  • the hydraulic pressure at the control inputs of the changeover valves 30-34 is increased by means of a reciprocating piston 40 and 41.
  • Each reciprocating piston 40 and 41 defines a fluid-filled pressure chamber 42 or 43 communicating with the outlet of the prefeed pump 29 and is driven by a cam 44 or 45 for lifting movement.
  • the pressure chamber 42 is connected to the control inputs of the changeover valves 30 and 31 and the pressure chamber 43 to the control inputs of the changeover valves 32, 33.
  • the two cams 44, 45 run at half the speed of the crankshaft, with each cam rotation of the voltage applied to the control inputs hydraulic pressure from the pressure level at the outlet of the feed pump 29 increases to a required to switch the switching valves 30 - 33 maximum pressure and back to the original pressure level is reduced.
  • By moving the pistons 41 and 42 in Fig. 1 upwards the pressure is increased and the associated changeover valves 30 - 33 switch over.
  • the provision of the piston 41, 42 takes place by the restoring force of the return springs of the changeover valves and by the permanently applied pressure of the prefeed pump 29.
  • the prefeed pump 29 also provides for the compensation of leakage losses.
  • Fig. 3 respectively shows the valve lift in dependence on the crank angle for the various valves.
  • Diagram a, b, f and g shows respectively the valve lift of the here intake valves forming gas exchange valves 10 in the first, third, second and fourth combustion cylinder I, III, II and IV, diagram c the valve lift of the changeover valves 30 31, diagram h the valve lift of Changeover valves 32 and 33, diagram d the valve lift of the control valve 24, diagram e the valve lift of the control valve 25, diagram i the valve lift of the control valve 26 and diagram k the valve lift of the control valve 27.
  • each gas exchange valve 10 is controlled by the associated valve actuator 11 in such a way that for closing the gas exchange valve 10 of the second working chamber 122 of the valve actuator 11 via the second electrical control valve 25 and 27 connected to the discharge line 28 and via the first electric control valve 24 and 26 is shut off from the outlet 221 of the pressure supply device 22.
  • pressure of the actuating piston 13 in Fig. 2 is shifted upward until the valve sealing surface 15 of the gas exchange valve 10 rests on the valve seat surface 17 on the housing 16 of the combustion cylinder of the internal combustion engine.
  • the actuating piston 13 takes the in Fig. 1 shown position within the working cylinder 12 of the valve actuator 11 a.
  • All control valves 24 - 27 are de-energized and assume their basic or rest position.
  • the second electric control valve 25 and 27 is transferred to its blocking position in which the second working space 122 is shut off from the discharge line 28, and the first electric control valve 24 and 26 is transferred to its working position, so that the second working space 122 is connected to the output 221 of the pressure supply device 22 and the system pressure is now present in the second working chamber 122 of the valve actuator 11. Since the piston area of the actuating piston 13, which delimits the first working space 121, is smaller than the area of the actuating piston 13, which delimits the second working space 122, a displacement force is produced which moves the actuating piston 13 in FIG. 1 to the right or in FIG moved down, whereby the gas exchange valve 10 is opened. The.
  • the size of the opening stroke of the gas exchange valve 10 is dependent on the opening duration and opening speed of the first control valve 24 and 26, respectively.
  • valve actuator 11 For the control of the gas exchange valve 10 in the combustion cylinder I associated valve actuator 11 are the switching valves 30, 31 in the rest or basic position A shown in Fig. 1, as shown in diagram c in Fig. 3.
  • the valve lift of the gas exchange valve 10 in the cylinder I as a function of the crank angle is shown in diagram a.
  • the switching valves 30, 31 and 32, 33 each have a crankangle range of approximately 300.degree. In position A and in position B. The corresponding changeover is effected by the cams 44, 45, which rotate at half crankshaft speed.
  • the changeover valves can not be operated hydraulically but electrically, the currentless changeover valve occupying position A and the energized changeover valve occupying position B or vice versa. It is also possible, in the described hydraulically controlled switching valves 30 - 33 instead of the spring return, a second hydraulic control input, counteracting the first.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)

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, the actuator 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 its second working space on the one hand to a supply to the High pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a discharge line alternately releasing or closing second control valve. 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.

Weitere bekannte Vorrichtungen gehen aus den Dokumenten EP 0 905 361 und EP 0 721 055 hervor.Other known devices are evident from the documents EP 0 905 361 and EP 0 721 055.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Vorrichtung zur Steuerung von Gaswechselventilen mit dem Merkmalen des Anspruchs 1 hat den Vorteil, daß durch die Nutzung eines sich aus einem ersten und einem zweiten elektrischen Steuerventil zusammensetzenden Steuerventilpaars zur wechselnden Ansteuerung von insgesamt zwei Ventilstellern zwei elektrische Steuerventile pro Ventilstellerpaar eingespart werden. Da die vornehmlich als 2/2-Wegemagnetventile ausgebildeten elektrischen Steuerventile extrem kleine Schaltzeiten realisieren müssen, in der Praxis ca. 0,3 ms bei einem Öffnungsquerschnitt von 3 mm2, sind solche Steuerventile sehr teuer, so daß die Verringerung der Zahl der Steuerventile in der Steuervorrichtung eine deutliche Kosteneinsparung mit sich bringt. Durch die geringere Zahl von elektrischen Steuerventilen reduziert sich auch die Zahl der Endstufen und der Aufwand an elektrischer Verkabelung für die Ansteuerung der Steuerventile, was zu einer weiteren Kostenersparnis führt.The inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by the use of a composed of a first and a second electrical control valve control valve pair for the alternating control of total two valve actuators two electrical control valves per valve pair can be saved. Since the electrical control valves designed primarily as 2/2-way solenoid valves must realize extremely short switching times, in practice about 0.3 ms with an opening cross-section of 3 mm 2 , such control valves are very expensive, so that the reduction of the number of control valves in the control device brings a significant cost savings. Due to the smaller number of electrical control valves, the number of power amplifiers and the amount of electrical wiring for the control of the control valves is reduced, which leads to a further cost savings.

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 ist die Umschaltung der Steuerventile mittels zweier als 3/2-Wegeventile ausgebildeter Umschaltventile vorgenommen, von deren jeweils drei gesteuerten Ventilanschlüsse der erste mit dem ersten bzw. zweiten elektrischen Steuerventil verbunden ist und die wechselweise auf den ersten Ventilanschluß aufschaltbaren beiden weiteren Ventilanschlüsse an den zweiten Arbeitsräumen der beiden Ventilsteller angeschlossen sind. Einfache Umschaltventile, die elektrisch oder hydraulisch angesteuert werden können, sind als Massenartikel sehr preiswert, insbesondere dann, wenn keine schnellen Schaltzeiten gefordert werden. Da beispielsweise bei einem Vierzylinder-Viertaktmotor der gemeinsame Schließzustand zweier Gaswechselventile in Verbrennungszylindern mit einem 360°-Kurbelwinkelversatz ihrer Zündzeitpunkte sich über eine Kurbelwinkelbereich von ca. 60° erstreckt, steht eine ausreichend große Zeitspanne für die Umsteuerung der Umschaltventile zur Verfügung. Durch den Einsatz der preiswerten Umschaltventile wird zwar die Ventilzahl insgesamt wieder erhöht, doch bleibt dabei ein wesentliches Kosteneinsparpotential zurück. Die Umschaltventile sind, insbesondere wenn sie hydraulisch angesteuert sind, im Vergleich zu den 2/2-Wegemagnetventilen recht bauklein, so daß sich auch der für die Ventilsteuervorrichtung erforderliche Bauraumbedarf gegenüber der bekannten Ventilsteuerung reduziert.According to a preferred embodiment of the invention, the switching of the control valves by means of two trained as 3/2-way valves switching valves is made, of which three controlled valve connections of the first with the first and second electrical control valve is connected and the two alternately aufschaltbaren on the first valve port further valve connections are connected to the second working spaces of the two valve actuators. Simple change-over valves, which can be controlled electrically or hydraulically, are very inexpensive as mass-produced articles, especially when no fast switching times are required. For example, at a Four-cylinder four-stroke engine, the common closed state of two gas exchange valves in combustion cylinders with a 360 ° crank angle offset their ignition extends over a crank angle range of about 60 °, is a sufficiently large period of time for the reversal of the changeover valves available. By using the inexpensive changeover valves, the total number of valves is increased again, but there remains a significant cost savings potential. The switching valves are, especially if they are hydraulically controlled, compared to the 2/2-way solenoid valves quite small, so that also reduces the space required for the valve control device space requirement compared to the known valve control.

Gemäß einer vorteilhaften Ausführungsform der Erfindung steht am Steuereingang der hydraulisch gesteuerten Umschaltventile ' permanent ein hydraulischer Druck an, der zur Umsteuerung der Umschaltventile in ihre Arbeitsstellung mittels eines Hubkolbens vergrößert wird. Der Hubkolben ist hierzu von einem mit gegenüber der Drehzahl der Kurbelwelle halbierter Drehzahl umlaufenden Nocken zur Hubbewegung in einer mit dem jeweiligen Steuereingang in Verbindung stehenden Druckkammer antreibbar. Durch diese konstruktive Maßnahme wird in einfacher Weise die Umschaltung der Umschaltventile mit der Kurbelwellendrehung synchronisiert.According to an advantageous embodiment of the invention is at the control input of the hydraulically controlled changeover valves' permanently on a hydraulic pressure, which is increased for reversing the change-over valves in their working position by means of a reciprocating piston. For this purpose, the reciprocating piston can be driven by a cam which rotates with respect to the rotational speed of the crankshaft and can be driven to rotate in a pressure chamber communicating with the respective control input. By this constructive measure, the switching of the switching valves is synchronized with the crankshaft rotation in a simple manner.

Zeichnungdrawing

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

Fig. 1
ein Schaltbild einer Vorrichtung zur Steuerung von vier in verschiedenen Verbrennungszylindern einer Vierzylinder-Brennkraftmaschine angeordneten Gaswechselventilen,
Fig. 2
eine schematisierte Darstellung eines Gaswechselventils in einem Verbrennungszylinder der Brennkraftmaschine,
Fig. 3
ein Diagramm des Ventilhubs verschiedener Ventile in der Vorrichtung gemäß Fig. 1 in Abhängigkeit von dem Kurbelwinkel.
The invention is described in more detail below with reference to an embodiment shown in the drawing. Show it:
Fig. 1
a circuit diagram of an apparatus for controlling four arranged in different combustion cylinders of a four-cylinder internal combustion engine gas exchange valves,
Fig. 2
a schematic representation of a gas exchange valve in a combustion cylinder of the internal combustion engine,
Fig. 3
a diagram of the valve lift of various valves in the apparatus of FIG. 1 in dependence on the crank angle.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die in Fig. 1 im Schaltbild dargestellte Vorrichtung zur Steuerung von Gaswechselventilen in Verbrennungszylindern einer Brennkraftmaschine dient zur Steuerung von insgesamt vier Gaswechselventilen 10 (Fig. 2), von denen jeweils eins in einem Verbrennungszylinder einer Vierzylinder-ViertaktBrennkraftmaschine angeordnet ist. Bei den Gaswechselventilen 10 kann es sich dabei um die Einlaßventile oder um die Auslaßventile der Verbrennungszylinder handeln. Die hier nicht dargestellten Verbrennungszylinder sind symbolisch mit I, II, III und IV bezeichnet, die in Fig. 1 den Ventilstellern 11 für die Gaswechselventile 10 des jeweiligen Verbrennungszylinders zugeordnet sind.The illustrated in the circuit diagram in Fig. 1 apparatus for controlling gas exchange valves in combustion cylinders of an internal combustion engine is used to control a total of four gas exchange valves 10 (Fig. 2), of which one is arranged in a combustion cylinder of a four-cylinder four-stroke engine. The gas exchange valves 10 may be the intake valves or the exhaust valves of the combustion cylinders. The combustion cylinders, not shown here are symbolic with I, II, III and IV, which are assigned in Fig. 1 the valve actuators 11 for the gas exchange valves 10 of the respective combustion cylinder.

Die Vorrichtung weist insgesamt vier hydraulische Ventilsteller 11 auf, von denen jeweils einer einem Gaswechselventil 10 in den Verbrennungszylindern I - IV zugeordnet ist. Jeder Ventilsteller 11 weist einen Arbeitszylinder 12 auf, in dem ein Stellkolben 13 axial verschieblich geführt ist. Der Stellkolben 13 unterteilt den Arbeitszylinder 12 in zwei von ihm begrenzte, hydraulische Arbeitsräume 121 und 122 und ist mit dem Ventilstößel 14 des Gaswechselventils 10 fest verbunden. In Fig. 2 ist in vergrößerter Darstellung ein Ventilsteller 11 in Verbindung mit einem Gaswechselventil 10 schematisiert dargestellt. Der Ventilstößel 14 trägt an seinem vom Stellkolben 13 abgekehrten Ende eine tellerförmige Ventildichtfläche 15, die zur Steuerung eines Öffnungsquerschnitts mit einer am Gehäuse 16 des Verbrennungszylinders der Brennkraftmaschine ausgebildeten Ventilsitzfläche 17 zusammenwirkt. Der Arbeitszylinder 12 weist insgesamt drei Hydraulikanschlüsse auf, von denen zwei Hydraulikanschlüsse 122a und 122b im zweiten Arbeitsraum 122 und ein Hydraulikanschluß 121a im ersten Arbeitsraum 121 münden.The device has a total of four hydraulic valve actuator 11, one of which is associated with a gas exchange valve 10 in the combustion cylinders I - IV. Each valve actuator 11 has a working cylinder 12 in which an actuating piston 13 is guided axially displaceable. The actuating piston 13 divides the working cylinder 12 in two limited by him, hydraulic working spaces 121 and 122 and is fixedly connected to the valve stem 14 of the gas exchange valve 10. In Fig. 2, a valve plate 11 is shown schematically in conjunction with a gas exchange valve 10 in an enlarged view. The valve stem 14 carries at its end remote from the actuating piston 13 a plate-shaped valve sealing surface 15 which cooperates to control an opening cross section with a formed on the housing 16 of the combustion cylinder of the engine valve seat surface 17. The working cylinder 12 has a total of three hydraulic connections, of which two hydraulic connections 122a and 122b open in the second working space 122 and a hydraulic connection 121a in the first working space 121.

Die Vorrichtung weist weiter eine Druckversorgungseinrichtung 22 auf, die aus einem Fluidreservoir 18, einer Vorförderpumpe 29, einer Hochdruckpumpe 19, einem Rückschlagventil 20 und einem Speicher 21 zur Pulsationsdämpfung und Energiespeicherung besteht. Der zwischen dem Rückschlagventil 20 und dem Speicher 21 abgegriffene Ausgang 221 der Druckversorgungseinrichtung 22 ist über eine Leitung 23 mit allen Hydraulikanschlüssen 121a der vier Ventilsteller 11 verbunden, so daß die ersten Arbeitsräume 121 der Ventilsteller 11 ständig mit dem am Ausgang 221 der Druckversorgungseinrichtung 22 anstehenden Hydraulikdruck beaufschlagt sind.The device further comprises a pressure supply device 22, which consists of a fluid reservoir 18, a prefeed pump 29, a high pressure pump 19, a check valve 20 and a memory 21 for pulsation damping and energy storage. The tapped between the check valve 20 and the memory 21 output 221 of Pressure supply device 22 is connected via a line 23 to all hydraulic ports 121a of the four valve actuators 11, so that the first working chambers 121 of the valve plate 11 are constantly acted upon by the output 221 of the pressure supply device 22 pending hydraulic pressure.

Die zweiten Arbeitsräume 122 der Arbeitszylinder 12 sind einerseits über erste elektrische Steuerventile 24 und 26 an den Ausgang 221 der Druckversorgungseinrichtung 22 und andererseits über zweite elektrische Steuerventile 25 und 27 an eine Entlastungsleitung 28 anschließbar, die ihrerseits im Fluidreservoir 18 mündet. Alle Steuerventile 24 - 27 sind als 2/2-Wegemagnetventile mit Federrückstellung ausgebildet. Jeweils ein erstes Steuerventil 24 bzw. 26 und ein zweites Steuerventil 25 bzw. 27 bilden ein Steuerventilpaar, mit dem jeweils zwei Ventilsteller 11 wechselweise angesteuert werden. Die beiden von den Steuerventilpaaren 24, 25 bzw. 26, 27 angesteuerten Ventilsteller 11 sind jeweils Gaswechselventilen 10 in solchen Verbrennungszylindern zugeordnet, deren Zündzeitpunkte um 360° Kurbelwinkel gegeneinander versetzt sind. So steuert das Steuerventilpaar 24, 25 die beiden Ventilsteller 11 der Gaswechselventile 10 in dem ersten und dritten Verbrennungszylinder I und III und das Steuerventilpaar 26, 27 die Ventilsteller 11 für die Gaswechselventile 10 in dem zweiten und vierten Verbrennungszylinder II und IV, wobei die Steuerung der jeweils beiden Ventilsteller 11 wechselweise erfolgt und die Umschaltung des Steuerventilpaars 24, 25 bzw. 26, 27 von dem einen Ventilsteller 11 auf den anderen Ventilsteller 11 während des Schließzustandes der beiden von den Ventilstellern 11 betätigten Gaswechselventile 10 durchgeführt wird. Die Umschaltüng der beiden Steuerventile 24 und 25 bzw. 26 und 27 eines jeden Steuerventilpaars erfolgt synchron.The second working chambers 122 of the working cylinders 12 are connected on the one hand via first electrical control valves 24 and 26 to the output 221 of the pressure supply device 22 and on the other hand via second electrical control valves 25 and 27 to a discharge line 28, which in turn opens into the fluid reservoir 18. All control valves 24-27 are designed as 2/2-way solenoid valves with spring return. In each case, a first control valve 24 or 26 and a second control valve 25 and 27 form a control valve pair, with the respective two valve actuators 11 are controlled alternately. The two valve actuators 11 controlled by the control valve pairs 24, 25 and 26, 27 are each associated with gas exchange valves 10 in combustion cylinders of this type whose ignition times are offset by 360 ° crank angle from one another. Thus, the control valve pair 24, 25 controls the two valve actuators 11 of the gas exchange valves 10 in the first and third combustion cylinders I and III and the control valve pair 26, 27, the valve plate 11 for the gas exchange valves 10 in the second and fourth combustion cylinder II and IV, wherein the control of each two valve actuator 11 takes place alternately and the switching of the control valve pair 24, 25 or 26, 27 of the one valve actuator 11 to the other valve actuator 11 during the closed state of the two of the Valve actuators 11 actuated gas exchange valves 10 is performed. The Umschaltüng the two control valves 24 and 25 or 26 and 27 of each control valve pair is synchronous.

Zur Umschaltung der beiden Steuerventilpaare 24, 25 bzw. 26, 27 von dem einen Ventilsteller 11 auf den anderen Ventilsteller 11 erfolgt durch Umschaltventile 30 - 33, die im Ausführungsbeispiel der Fig. 1 als hydraulisch gesteuerte 3/2-Wegeventile mit Federrückstellung ausgebildet sind. Jedes Umschaltventil 30 - 33 weist zwei Schaltstellungen und drei gesteuerte Ventilanschlüsse 34 - 36 auf, von denen der erste Ventilanschluß 34 mit den jeweils zugeordneten Steuerventilen 24 und 25 bzw. 26 und 27 verbunden ist und die beiden auf den ersten Ventilanschluß 34 aufschaltbaren weiteren Ventilanschlüsse 35 und 36 an den zweiten Arbeitsräumen 122 der Ventilsteller 11 angeschlossen sind. So ist bei dem Umschaltventil 30 der erste Ventilanschluß 34 mit dem ersten Steuerventil 24, der zweite Ventilanschluß 25 mit dem zweiten Arbeitsraum 122 des Ventilstellers 11 für den ersten Verbrennungszylinder I und der zweite Ventilanschluß 36 mit dem zweiten Arbeitsraum 122 des Ventilstellers 11 für den dritten Verbrennungszylinder III verbunden. Der erste Ventilanschluß 34 des Umschaltventils 31 ist mit dem zweiten Steuerventil 25, der zweite Ventilanschluß 35 mit dem zweiten Arbeitsraum 122 des Ventilstellers 11 für den ersten Verbrennungszylinder I und der dritte Ventilanschluß 36 mit dem Arbeitsraum 122 des Ventilstellers 11 für den dritten Verbrennungszylinder III verbunden. Entsprechendes gilt für die Umschaltventile 32, 33 in Verbindung mit dem Steuerventilpaar 26, 27 und den Ventilstellern 11 für den zweiten und vierten Verbrennungszylinder II und IV.For switching the two control valve pairs 24, 25 and 26, 27 of the one valve actuator 11 to the other valve actuator 11 is effected by switching valves 30 - 33, which are formed in the embodiment of FIG. 1 as a hydraulically controlled 3/2-way valves with spring return. Each switching valve 30-33 has two switching positions and three controlled valve ports 34-36, of which the first valve port 34 is connected to the respective associated control valves 24 and 25 or 26 and 27 and the two connectable to the first valve port 34 further valve ports 35th and 36 are connected to the second working spaces 122 of the valve actuator 11. Thus, in the switching valve 30, the first valve port 34 to the first control valve 24, the second valve port 25 to the second working chamber 122 of the valve actuator 11 for the first combustion cylinder I and the second valve port 36 to the second working space 122 of the valve actuator 11 for the third combustion cylinder III connected. The first valve port 34 of the switching valve 31 is connected to the second control valve 25, the second valve port 35 to the second working space 122 of the valve actuator 11 for the first combustion cylinder I and the third valve port 36 to the working space 122 of the valve actuator 11 for the third combustion cylinder III. The same applies to the switching valves 32, 33 in conjunction with the Control valve pair 26, 27 and the valve actuators 11 for the second and fourth combustion cylinder II and IV.

Die Steuerung der Umschaltventile 30 - 33 erfolgt hydraulisch gegen die Federkraft einer Rückstellfeder, wozu die Steuereingänge der Umschaltventile 30 und 31 über ein Rückschlagventil 37 und die Steuereingänge der Umschaltventile 32 und 33 über ein Rückschlagventil 38 mit dem Auslaß der Vorförderpumpe 29 verbunden sind. Die Umschaltventile 30 - 33 sind dabei so ausgelegt, daß sie durch den am Auslaß der Vorförderpumpe 29 anstehenden Hydraulikdruck nicht aus ihrer in Fig. 1 dargestellten Ruhestellung herausbewegbar sind. Zum Schalten der Umschaltventile 30 - 33 wird mittels eines Hubkolbens 40 und 41 der Hydraulikdruck an den Steuereingängen der Umschaltventile 30 - 34 vergrößert. Jeder Hubkolben 40 bzw. 41 begrenzt eine mit dem Auslaß der Vorförderpumpe 29 in Verbindung stehende, fluidgefüllte Druckkammer 42 bzw. 43 und wird durch einen Nocken 44 bzw. 45 zur Hubbewegung angetrieben. Die Druckkammer 42 ist mit den Steuereingängen der Umschaltventile 30 und 31 und die Druckkammer 43 mit den Steuereingängen der Umschaltventile 32, 33 verbunden. Die beiden Nocken 44, 45 laufen mit halber Drehzahl der Kurbelwelle um, wobei bei jeder Nockenumdrehung der an den Steuereingängen anliegende Hydraulikdruck von dem Druckniveau am Auslaß der Vorförderpumpe 29 auf einen zum Umschalten der Umschaltventile 30 - 33 erforderlichen Maximaldruck anwächst und wieder auf das ursprüngliche Druckniveau reduziert wird. Durch Verschieben der Kolben 41 und 42 in Fig. 1 nach oben wird der Druck erhöht und die zugeordneten Umschaltventile 30 - 33 schalten um. Die Rückstellung der Kolben 41, 42 erfolgt durch die Rückstellkraft der Rückstellfedern der Umschaltventile und durch den permanent anliegenden Druck der Vorförderpumpe 29. Die Vorförderpumpe 29 sorgt ebenfalls für den Ausgleich von Leckageverlusten.The control of the changeover valves 30-33 is hydraulically against the spring force of a return spring, to which the control inputs of the changeover valves 30 and 31 via a check valve 37 and the control inputs of the changeover valves 32 and 33 are connected via a check valve 38 to the outlet of the prefeed pump 29. The switching valves 30-33 are designed so that they can not be moved out of their rest position shown in Fig. 1 by the pending at the outlet of the prefeed pump 29 hydraulic pressure. For switching the changeover valves 30-33, the hydraulic pressure at the control inputs of the changeover valves 30-34 is increased by means of a reciprocating piston 40 and 41. Each reciprocating piston 40 and 41 defines a fluid-filled pressure chamber 42 or 43 communicating with the outlet of the prefeed pump 29 and is driven by a cam 44 or 45 for lifting movement. The pressure chamber 42 is connected to the control inputs of the changeover valves 30 and 31 and the pressure chamber 43 to the control inputs of the changeover valves 32, 33. The two cams 44, 45 run at half the speed of the crankshaft, with each cam rotation of the voltage applied to the control inputs hydraulic pressure from the pressure level at the outlet of the feed pump 29 increases to a required to switch the switching valves 30 - 33 maximum pressure and back to the original pressure level is reduced. By moving the pistons 41 and 42 in Fig. 1 upwards, the pressure is increased and the associated changeover valves 30 - 33 switch over. The provision of the piston 41, 42 takes place by the restoring force of the return springs of the changeover valves and by the permanently applied pressure of the prefeed pump 29. The prefeed pump 29 also provides for the compensation of leakage losses.

Die Funktionsweise der beschriebenen Vorrichtung wird anhand der Fig. 3 im folgenden näher beschrieben. Dabei zeigt die Fig. 3 jeweils den Ventilhub in Abhängigkeit von dem Kurbelwinkel für die verschiedenen Ventile. Diagramm a, b, f und g zeigt jeweils den Ventilhub der hier Einlaßventile bildenden Gaswechselventile 10 in dem ersten, dritten, zweiten und vierten Verbrennungszylinder I, III, II und IV, Diagramm c den Ventilhub der Umschaltventile 30 31, Diagramm h den Ventilhub der Umschaltventile 32 und 33, Diagramm d den Ventilhub des Steuerventils 24, Diagramm e den Ventilhub des Steuerventils 25, Diagramm i den Ventilhub des Steuerventils 26 und Diagramm k den Ventilhub des Steuerventils 27.The operation of the device described will be described with reference to FIG. 3 in the following. In this case, Fig. 3 respectively shows the valve lift in dependence on the crank angle for the various valves. Diagram a, b, f and g shows respectively the valve lift of the here intake valves forming gas exchange valves 10 in the first, third, second and fourth combustion cylinder I, III, II and IV, diagram c the valve lift of the changeover valves 30 31, diagram h the valve lift of Changeover valves 32 and 33, diagram d the valve lift of the control valve 24, diagram e the valve lift of the control valve 25, diagram i the valve lift of the control valve 26 and diagram k the valve lift of the control valve 27.

Grundsätzlich wird jedes Gaswechselventil 10 von dem zugeordneten Ventilsteller 11 in der Weise gesteuert, daß zum Schließen des Gaswechselventils 10 der zweiten Arbeitsraum 122 des Ventilstellers 11 über das zweite elektrische Steuerventil 25 bzw. 27 an die Entlastungsleitung 28 angeschlossen und über das erste elektrische Steuerventil 24 bzw. 26 von dem Ausgang 221 der Druckversorgungseinrichtung 22 abgesperrt wird. Durch den im ersten Arbeitsraum 121 des Ventilstellers 11 herrschenden Systemdruck wird der Stellkolben 13 in Fig. 2 nach oben verschoben, bis die Ventildichtfläche 15 des Gaswechselventils 10 auf der Ventilsitzfläche 17 am Gehäuse 16 des Verbrennungszylinders der Brennkraftmaschine aufliegt. Der Stellkolben 13 nimmt die in Fig. 1 dargestellte Lage innerhalb des Arbeitszylinders 12 des Ventilstellers 11 ein. Alle Steuerventile 24 - 27 sind stromlos und nehmen ihre Grund- oder Ruhestellung ein. Zum Öffnen des Gaswechselventils 10 wird das zweite elektrische Steuerventil 25 bzw. 27 in seine Sperrstellung überführt, in welcher der zweite Arbeitsraum 122 gegenüber der Entlastungsleitung 28 abgesperrt ist, und wird das erste elektrische Steuerventil 24 bzw. 26 in seine Arbeitsstellung überführt, so daß der zweite Arbeitsraum 122 mit dem Ausgang 221 der Druckversorgungseinrichtung 22 verbunden ist und der Systemdruck nunmehr auch im zweiten Arbeitsraum 122 des Ventilstellers 11 ansteht. Da die Kolbenfläche des Stellkolbens 13, die den ersten Arbeitsraum 121 begrenzt, kleiner ist als die Fläche des Stellkolbens 13, die den zweiten Arbeitsraum 122 begrenzt, entsteht eine Verschiebekraft, die den Stellkolben 13 in Fig. 1 nach rechts bzw. in Fig. 2 nach unten bewegt, wodurch das Gaswechselventil 10 geöffnet wird. Die. Größe des Öffnungshubs des Gaswechselventils 10 ist von der Öffnungsdauer und Öffnungsgeschwindigkeit des ersten Steuerventils 24 bzw. 26 abhängig.Basically, each gas exchange valve 10 is controlled by the associated valve actuator 11 in such a way that for closing the gas exchange valve 10 of the second working chamber 122 of the valve actuator 11 via the second electrical control valve 25 and 27 connected to the discharge line 28 and via the first electric control valve 24 and 26 is shut off from the outlet 221 of the pressure supply device 22. By the prevailing in the first working space 121 of the valve actuator 11 system pressure of the actuating piston 13 in Fig. 2 is shifted upward until the valve sealing surface 15 of the gas exchange valve 10 rests on the valve seat surface 17 on the housing 16 of the combustion cylinder of the internal combustion engine. The actuating piston 13 takes the in Fig. 1 shown position within the working cylinder 12 of the valve actuator 11 a. All control valves 24 - 27 are de-energized and assume their basic or rest position. To open the gas exchange valve 10, the second electric control valve 25 and 27 is transferred to its blocking position in which the second working space 122 is shut off from the discharge line 28, and the first electric control valve 24 and 26 is transferred to its working position, so that the second working space 122 is connected to the output 221 of the pressure supply device 22 and the system pressure is now present in the second working chamber 122 of the valve actuator 11. Since the piston area of the actuating piston 13, which delimits the first working space 121, is smaller than the area of the actuating piston 13, which delimits the second working space 122, a displacement force is produced which moves the actuating piston 13 in FIG. 1 to the right or in FIG moved down, whereby the gas exchange valve 10 is opened. The. The size of the opening stroke of the gas exchange valve 10 is dependent on the opening duration and opening speed of the first control valve 24 and 26, respectively.

Ist der gewünschte Hub des Gaswechselventils 10 erreicht, so wird die Bestromung des ersten Steuerventils 24 bzw. 26 aufgehoben, und das erste Steuerventil 24 bzw. 26 fällt in seine Sperrstellung zurück. Der Druck im zweiten Arbeitsraum 122 wird gehalten, so daß das Gaswechselventil 10 den eingenommenen Öffnungshub unverändert beibehält. Zum Schließen des Gaswechselventils 10 wird dann das zweite Steuerventil 25 bzw. 27 stromlos geschaltet. Diagramm d zeigt die Ansteuerung des ersten Steuerventils 24, Diagramm e die Ansteuerung des zweiten Steuerventils 25. Diagramm i zeigt die Ansteuerung des ersten Steuerventils 26 und Diagramm k die Ansteuerung des zweiten Steuerventils 27. Die ersten Steuerventile 24 und 26 sind stromlos gesperrt während die zweiten Steuerventile 25, 27 stromlos offen sind.If the desired stroke of the gas exchange valve 10 is reached, the energization of the first control valve 24 and 26 is canceled, and the first control valve 24 and 26 falls back into its blocking position. The pressure in the second working chamber 122 is maintained, so that the gas exchange valve 10 maintains the assumed opening stroke unchanged. To close the gas exchange valve 10, the second control valve 25 and 27 is then de-energized. Diagram d shows the activation of the first control valve 24, diagram e the Control of the second control valve 25. Diagram i shows the control of the first control valve 26 and diagram k the control of the second control valve 27. The first control valves 24 and 26 are de-energized while the second control valves 25, 27 are normally open.

Zur Steuerung des dem Gaswechselventil 10 im Verbrennungszylinder I zugeordneten Ventilstellers 11 befinden sich die Umschaltventile 30, 31 in der in Fig. 1 dargestellten Ruhe- oder Grundstellung A, wie dies Diagramm c in Fig. 3 zeigt. Der Ventilhub des Gaswechselventils 10 im Zylinder I in Abhängigkeit vom Kurbelwinkel zeigt Diagramm a.For the control of the gas exchange valve 10 in the combustion cylinder I associated valve actuator 11 are the switching valves 30, 31 in the rest or basic position A shown in Fig. 1, as shown in diagram c in Fig. 3. The valve lift of the gas exchange valve 10 in the cylinder I as a function of the crank angle is shown in diagram a.

Zum Ansteuern des Ventilstellers 11 zum Betätigen des dem dritten Verbrennungszylinder III zugeordneten Gaswechselventils 10 werden die beiden Umschaltventile 30, 31 in ihrer Arbeitsstellung B umgesteuert. Hierdurch wird der zweite Arbeitsraum 122 des Ventilstellers 11 zur Betätigung des Gaswechselventils 10 im dritten Verbrennungszylinder III an die beiden Steuerventile 24, 25 angeschlossen. Der Ventilsteuervorgang für das Gaswechselventil 10 im Verbrennungszylinder III läuft dann in gleicher Weise ab wie vorstehend zu Verbrennungszylinder I beschrieben worden ist. Diagramm b zeigt den Hub des Gaswechselventils 10 im Verbrennungszylinder III in Abhängigkeit vom Kurbelwinkel, während sich die Umschaltventile 30, 31 in der Stellung B befinden (Diagramm c). Wie aus den Diagrammen a, b und c zu erkennen ist, sind die Schließzeitpunkte der Gaswechselventile 10 in den Verbrennungszylindern I und III, die etwa den Zündzeitpunkten in den Verbrennungszylindern I und III entspricht, um 360° Kurbelwinkel versetzt. Bei einem maximalen Öffnungswinkel der Gaswechselventile 10 von ca. 240° steht für die Umschaltung der beiden Umschaltventile 30, 31 in dem Kurbelwinkelbereich, in.dem beide Gaswechselventile 10 im Zylinder I und III geschlossen sind, genügend Zeit zur Verfügung. Dieser Umschaltbereich ist in Diagramm c mit S bezeichnet und überdeckt etwa 60° Kurbelwinkel.For driving the valve actuator 11 for actuating the gas exchange valve 10 assigned to the third combustion cylinder III, the two changeover valves 30, 31 are reversed in their working position B. As a result, the second working chamber 122 of the valve actuator 11 is connected to the two control valves 24, 25 for actuating the gas exchange valve 10 in the third combustion cylinder III. The valve control process for the gas exchange valve 10 in the combustion cylinder III then proceeds in the same manner as has been described above for combustion cylinder I. Diagram b shows the stroke of the gas exchange valve 10 in the combustion cylinder III as a function of the crank angle, while the switching valves 30, 31 are in the position B (diagram c). As can be seen from the diagrams a, b and c, the closing times of the gas exchange valves 10 in the combustion cylinders I and III, which corresponds approximately to the ignition times in the combustion cylinders I and III, offset by 360 ° crank angle. At a The maximum opening angle of the gas exchange valves 10 of approximately 240 ° is sufficient time for the switching of the two changeover valves 30, 31 in the crank angle range, in.dem both gas exchange valves 10 are closed in the cylinder I and III. This switching range is denoted by S in diagram c and covers about 60 ° crank angle.

In dem unteren Teil der Fig. 3 mit den Diagrammen f - k sind die entsprechenden Verhältnisse zur Steuerung der Gaswechselventile 10 in den Verbrennungszylindern II und IV dargestellt. Die Diagramme entsprechen den beschriebenen Diagrammen a - e und sind lediglich um einen Kurbelwinkel von 180° verschoben. Insoweit gelten die vorstehenden Ausführungen auch für die Steuerventile 26 und 27 in Verbindung mit dem Umschaltventilen 32, 33.In the lower part of Fig. 3 with the diagrams f - k, the corresponding conditions for controlling the gas exchange valves 10 in the combustion cylinders II and IV are shown. The diagrams correspond to the diagrams a - e described and are only shifted by a crank angle of 180 °. In that regard, the above statements also apply to the control valves 26 and 27 in conjunction with the switching valves 32, 33rd

Wie aus den Diagrammen c und h in Fig. 3 hervorgeht, stehen die Umschaltventile 30, 31 bzw. 32, 33 jeweils über einen Kurbelwinkelbereich von ca. 300° in Stellung A und in Stellung B. Die entsprechende Umschaltung wird durch die Nocken 44, 45 bewirkt, die mit halber Kurbelwellendrehzahl rotieren.As can be seen from the diagrams c and h in FIG. 3, the switching valves 30, 31 and 32, 33 each have a crankangle range of approximately 300.degree. In position A and in position B. The corresponding changeover is effected by the cams 44, 45, which rotate at half crankshaft speed.

Die Erfindung ist nicht auf das beschriebene Ausführungsbeispiel beschränkt. So können beispielsweise die Umschaltventile nicht hydraulisch sondern elektrisch betätigt werden, wobei das stromlose Umschaltventil Stellung A und das bestromte Umschaltventil Stellung B einnimmt oder umgekehrt. Es ist auch möglich, bei den beschriebenen hydraulisch gesteuerten Umschaltventilen 30 - 33 anstelle der Federrückstellung einen zweiten hydraulischen Steuereingang, der dem ersten entgegenwirkt, vorzusehen.The invention is not limited to the embodiment described. Thus, for example, the changeover valves can not be operated hydraulically but electrically, the currentless changeover valve occupying position A and the energized changeover valve occupying position B or vice versa. It is also possible, in the described hydraulically controlled switching valves 30 - 33 instead of the spring return, a second hydraulic control input, counteracting the first.

Claims (10)

  1. Apparatus for controlling gas exchange valves in combustion cylinders of an internal combustion engine, having hydraulic valve actuators (11) which are assigned in each case to one gas exchange valve (10) and have in each case one actuating piston (13) which acts on the gas exchange valve (10) and two hydraulic working spaces (121, 122) which are delimited by the actuating piston (13) and of which the first working space (121) which loads the gas exchange valve (10) in the closing direction is always filled with a pressurized fluid and the second working space (122) which loads the gas exchange valve (10) in the opening direction can be filled with and relieved of a pressurized fluid alternately via a first and second electric control valve (24 and 25 or 26 and 27), characterized in that in each case two valve actuators (11) are actuated by the same first control valve (24 or 26) and the same second control valve (25 or 27), and the first and second control valves (24 and 25 or 26 and 27) are switched over from one valve actuator (11) to the other during the closed state of the two gas exchange valves (10) which are actuated by the said valve actuators (11).
  2. Apparatus according to Claim 1, characterized in that the two valve actuators (11) which are actuated by the same control valves (24, 25 or 26, 27) are assigned in each case to one gas exchange valve (10) in combustion cylinders (I, III or II, IV) of such a type, the ignition instants of which are offset by 360° crank angle with respect to one another.
  3. Apparatus according to Claim 1 or 2, characterized in that the control valves (24, 25 or 26, 27) are switched over synchronously from one valve actuator (11) to the other.
  4. Apparatus according to one of Claims 1 to 3, characterized in that the control valves (24, 25 or 26, 27) are switched over in each case by means of two switchover valves (30, 31 or 32, 33) which are configured as 3/2-way valves having in each case two switching positions and three controlled valve connections (34, 35, 36), of which a first valve connection (34) is connected to the first or second electric control valve (24 or 25) and two further valve connections (35, 36) which can be switched alternately onto the first valve connection (34) are connected to the second working spaces (122) of the two valve actuators (11).
  5. Apparatus according to one of Claims 1 to 4, characterized in that the switchover valves (30-33) in each case have a hydraulic control input having a spring restoring means.
  6. Apparatus according to one of Claims 1 to 5, characterized in that the switchover of the switchover valves (30-33) is derived from the rotational movement of a crankshaft of the internal combustion engine.
  7. Apparatus according to Claims 5 and 6, characterized in that a permanent, hydraulic pressure prevails at the control input of the switchover valves (30-33), and in that the hydraulic pressure can be varied by means of a reciprocating piston (40, 41) which can be driven by a cam (44, 45) which rotates at half the rotational speed of the crankshaft.
  8. Apparatus according to Claim 7, characterized in that the control inputs of the switchover valves (30-33) are connected via in each case one non-return valve (37, 38) to a pressure source which supplies a constant hydraulic pressure and is preferably configured as a prefeed pump 29, and in that the spring force of the spring restoring means is set in such a way that the restoring force which is produced by it is marginally greater than the valve switchover force which is produced at the control input by the hydraulic pressure of the pressure source.
  9. Apparatus according to one of Claims 5 to 8, characterized in that the two switchover valves (30, 31 or 32, 33) which are assigned in each case to two valve actuators (11) are combined to form a valve unit with a common hydraulic control input having a spring restoring means.
  10. Apparatus according to one of Claims 1 to 9, characterized in that the gas exchange valves (10) are used as inlet and/or outlet valves for the combustion cylinders of the internal combustion engine.
EP02745076A 2001-07-24 2002-05-23 Device for controlling gas exchange valves Expired - Lifetime EP1415070B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10136020A DE10136020A1 (en) 2001-07-24 2001-07-24 Control device for IC engine gas changing valves has common electrically-operated control valves associated with each pair of hydraulic valve setting devices for respective gas changing valves
DE10136020 2001-07-24
PCT/DE2002/001868 WO2003012263A1 (en) 2001-07-24 2002-05-23 Device for controlling gas exchange valves

Publications (2)

Publication Number Publication Date
EP1415070A1 EP1415070A1 (en) 2004-05-06
EP1415070B1 true EP1415070B1 (en) 2006-12-20

Family

ID=7692908

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02745076A Expired - Lifetime EP1415070B1 (en) 2001-07-24 2002-05-23 Device for controlling gas exchange valves

Country Status (7)

Country Link
US (1) US6889639B2 (en)
EP (1) EP1415070B1 (en)
JP (1) JP2005508469A (en)
KR (1) KR20040019331A (en)
BR (1) BR0205797A (en)
DE (2) DE10136020A1 (en)
WO (1) WO2003012263A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007138057A1 (en) * 2006-05-26 2007-12-06 Robert Bosch Gmbh Method for controlling the gas exchange of an internal combustion engine
DE102006042912A1 (en) * 2006-09-13 2008-03-27 Volkswagen Ag Internal combustion engine with mixed camshafts
DE102009046943A1 (en) * 2009-11-20 2011-05-26 Robert Bosch Gmbh Electrohydraulic actuator
WO2015175213A1 (en) * 2014-05-12 2015-11-19 Borgwarner Inc. Crankshaft driven valve actuation
WO2016010732A1 (en) * 2014-07-16 2016-01-21 Borgwarner Inc. Crankshaft driven valve actuation using a connecting rod
CN110689980A (en) * 2019-11-01 2020-01-14 中核核电运行管理有限公司 Air control device for underwater emergency gripping tool of cobalt isotope rod bundle

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4009695A (en) * 1972-11-14 1977-03-01 Ule Louis A Programmed valve system for internal combustion engine
JPS59170414A (en) * 1983-03-18 1984-09-26 Nissan Motor Co Ltd Hydraulic type valve drive device
US5231959A (en) * 1992-12-16 1993-08-03 Moog Controls, Inc. Intake or exhaust valve actuator
US5497736A (en) * 1995-01-06 1996-03-12 Ford Motor Company Electric actuator for rotary valve control of electrohydraulic valvetrain
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
JP3622446B2 (en) * 1997-09-30 2005-02-23 日産自動車株式会社 Diesel engine combustion control system
DE19826047A1 (en) 1998-06-12 1999-12-16 Bosch Gmbh Robert Device for controlling a gas exchange valve for internal combustion engines

Also Published As

Publication number Publication date
WO2003012263A1 (en) 2003-02-13
DE50209020D1 (en) 2007-02-01
US20040035379A1 (en) 2004-02-26
KR20040019331A (en) 2004-03-05
DE10136020A1 (en) 2003-02-13
US6889639B2 (en) 2005-05-10
EP1415070A1 (en) 2004-05-06
JP2005508469A (en) 2005-03-31
BR0205797A (en) 2003-07-22

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