EP1521902B1 - Device for the control of gas exchange valves - Google Patents

Device for the control of gas exchange valves Download PDF

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Publication number
EP1521902B1
EP1521902B1 EP03717127A EP03717127A EP1521902B1 EP 1521902 B1 EP1521902 B1 EP 1521902B1 EP 03717127 A EP03717127 A EP 03717127A EP 03717127 A EP03717127 A EP 03717127A EP 1521902 B1 EP1521902 B1 EP 1521902B1
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EP
European Patent Office
Prior art keywords
valve
working chamber
iia
iib
valves
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EP03717127A
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German (de)
French (fr)
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EP1521902A1 (en
Inventor
Udo Diehl
Bernd Rosenau
Christian Grosse
Simon Kieser
Ralph Engelberg
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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 (see EP-A-647 770 ).
  • each valve actuator whose actuating piston is preferably integrally connected to the valve stem of the associated gas exchange valve, constantly connected to its first working space with a high-pressure fluid fluid source and its second working space on the one hand to a supply line to the fluid pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a leading to a fluid reservoir discharge line alternately releasing or closing second electric control valve.
  • the electrical control valves are designed as 2/2-way solenoid valves with spring return.
  • Gas exchange valve takes the actuator piston of the valve actuator due to the permanently connected to the fluid pressure source first working space and separated by the first electrical control valve from the fluid pressure source and connected by the second electrical control valve with the discharge line second working space a basic position.
  • both electrical control valves are switched.
  • Characterized the second working space of the valve actuator is on the one hand blocked by the second electrical control valve with respect to the discharge line and on the other hand connected by the first electric control valve to the supply line to the fluid pressure source. Since the actuating piston surface delimiting the second working chamber in the valve actuator is greater than the actuating piston surface delimiting the first working chamber, the actuating piston moves out of its basic position while reducing the volume of the first working chamber and thereby opens the gas exchange valve.
  • the size of the opening stroke depends on the configuration of the electric control signal applied to the first electric control valve, and the opening speed depends on the fluid pressure supplied from the fluid pressure source.
  • the first electric control valve is then switched so that it shuts off the supply line to the second working space of the valve actuator. In this way, all opening positions of the gas exchange valve can be adjusted by means of an electrical control device for generating control signals.
  • the closing of the gas exchange valve is carried out by resetting the second electrical control valve in its open position, so that the first working space of the valve actuator back to the Relief line is connected.
  • two electrical control valves are required in each case act on the second working space of the associated valve actuator in accordance with fluid pressure or depressurize.
  • the inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by replacing a first electric control valve of a valve actuator in the valve actuator pair by a simple switching valve, via which the fluid pressure in the second working space by means of the second working space of the other Controlled valve actuator pending fluid pressure, the number of electrical control valves per valve pair is reduced.
  • a second electrical control valve in the valve actuator pair replaced by a simple check valve that connects the second working space of a valve actuator with the second valve control valve associated second electrical control valve, so can be saved per valve actuator pair two solenoid valves.
  • the switching valve is arranged in a connecting line between the second working spaces of the two valve actuators of the valve actuator pair. If this is either electromotive, electromagnetically or hydraulically actuated, designed as a 2/2-way valve switching unlocked, the second working space of a valve actuator is supplied via the second working space of the other valve actuator with fluid pressure and thus the actuator piston of the valve actuator in the direction of opening the gas exchange valve , By a suitable choice of the timing of the unlocking of the switching valve can different opening times of the actuated by this valve actuator gas exchange valve can be realized or this gas exchange valve can be kept closed if necessary.
  • the only first electrical control valve in the valve actuator pair must be designed so that in extreme cases, it can provide the total volume flow that both valve actuators of a valve actuator pair need to perform a simultaneous or staggered but always parallel stroke.
  • By controlling the second electrical control valves different closing times can be realized on both gas exchange valves. If, as noted above, one of the two second electrical control valves replaced by a check valve, the closing of the gas exchange valves is effected at the same time.
  • the changeover valve is a hydraulically operated 2/2-way valve with two hydraulic control inputs and is designed so that a valve unlocking occurs only when both control inputs.
  • One control input is connected to the second working space connected to the single first electrical control valve and the other control input is connected to the outlet of a further switching valve acted on the input side by a fluid pressure.
  • the second working space of the valve actuator connected to the changeover valve is connected directly to the fluid pressure source via the changeover valve. As soon as the only first electric control valve is actuated, the fluid pressure which it supplies into the second working space is also applied to the one control input of the changeover valve.
  • the unlocking of the switching valve can then at any time by applying the second control input are performed wherein flows with switching of the switching valve fluid directly from the fluid pressure source into the second working space of the other valve actuator.
  • This embodiment has the advantage that the only first electric control valve in the valve pair to be dimensioned only for the supply of a single valve actuator and not the entire amount of fluid must switch to control both valve actuator.
  • discontinuities in the lifting movement of a valve actuator which can be caused during the stroke of its actuating piston by the connection of the other valve actuator and by the thus occurring, additional fluid requirement of the second working chamber of the subsequent valve actuator, avoided.
  • all switching valves of the existing valve pairs are unlocked with the further switching valve, so that only a single further switching valve is present in the device, which brings advantages in terms of reducing manufacturing costs and space with it.
  • the application of the further switching valve with fluid pressure is effected by the fact that the valve inlet is connected via a check valve to the connected to the single first electrical control valve second working space of the valve pair.
  • the pressurization of the further switching valve can also be effected by an external fluid pressure source, for example the low-pressure circuit of the internal combustion engine.
  • Fig. 1 shown in the diagram device for controlling gas exchange valves in combustion cylinders of an internal combustion engine is for the control of a total of eight gas exchange valves 10, such as one in Fig. 3 schematically outlined, each of which are 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 in the combustion cylinders act.
  • the device comprises a plurality of hydraulic valve actuators 11, in the exemplary embodiment a total of eight valve actuators 11, of which one each actuates a gas exchange valve 10.
  • 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 pressure or working spaces 121 and 122 and is fixedly connected to a valve tappet 14 of the gas exchange valve 10.
  • Fig. 3 is a schematic representation of a valve actuator 11 in conjunction with an open gas exchange valve 10 is shown in enlarged scale.
  • the valve stem 14 carries at its end remote from the actuating piston 13 a valve sealing surface 15 which cooperates to control an opening cross-section with a formed in the cylinder head 16 of the combustion cylinder of the internal combustion engine valve seat surface 17.
  • the working cylinder 12 has a total of three hydraulic connections, of which two hydraulic ports 122a and 122b in the upper pressure chamber or second working space 122 and a hydraulic connection 121a in the lower pressure chamber or first working space 121 open.
  • the device further has a pressure supply device 20, whose output 201 forms a fluid pressure source for feeding the valve actuator 11.
  • the pressure supply device 20 comprises a high-pressure pump 21, which promotes fluid from a fluid reservoir 18, a discharge valve 22 arranged on the outlet side of the high-pressure pump 21 and a storage 23 for pulsation damping and energy storage.
  • the output 201 of the pressure supply device 20, which is tapped between the check valve 22 and the memory 23, is connected via a line 24 with the Hydraulic connections 121a of the first working spaces 121 connected in all of the total of eight valve actuators 11, so that the first working spaces 121 of the valve plate 11 are constantly applied to the output 201 of the pressure supply means 20 pending, high fluid or hydraulic pressure.
  • valve actuators 11 Of the total of eight existing valve actuators 11, two valve actuators 11 are combined to form a pair of valve actuators each controlling two intake valves or two exhaust valves in the same combustion cylinder.
  • the assigned combustion cylinder is in Fig. 1 symbolized by dotted border 19 of the valve actuator pair with the associated control means.
  • the valve actuators 11 of a valve actuator pair are referred to below as 11a and 11b, and the description is restricted to a valve actuator pair associated with a combustion cylinder. However, it applies equally to the remaining three valve pairs associated with the remaining combustion cylinders.
  • the fluid connection 122a of the second working space 122 of the valve actuator 11a is connected to the line leading to the output 201 of the pressure supply device 20 via a first electrical control valve 25, which is designed as a 2/2-way solenoid valve with spring return, while the fluid connection 122b of the second Working space 122 of the valve actuator 11 a to a second electrical control valve 26, which is also designed as a 2/2-way solenoid valve with spring return is set.
  • the second electrical control valve 26 opens at an opening in the fluid reservoir 18 Return line 27 connected.
  • the fluid port 122a of the second working chamber 122 of the valve actuator 11b is connected to the fluid port 122b on the valve actuator 11a via a connecting line 28 in which a hydraulically releasable switching valve 29 is arranged with spring return.
  • the fluid port 122b of the second working space 122 of the valve actuator 11b is also connected via a check valve 30 to the inlet of the second electrical control valve 26.
  • the switching valve 29 has a hydraulic control input 291 which is connected via a control line 31 at the outlet of an electromagnetically actuated further switching valve 32.
  • the further switching valve 32 is connected via a check valve 33 to the second working chamber 122 of the valve actuator 11a.
  • the inlet side of the further switching valve 32 may also be connected to the outlet 201 of the pressure supply device 20 or to a low-pressure circuit of the internal combustion engine.
  • the outlet side of the further switching valve 32 is placed over corresponding control lines 31 to all control inputs 291 of the switching valves 29 for all valve actuator pairs. Is the switching valve 32 as in the embodiment of Fig.
  • valve actuators 11a and 11b of a valve actuator pair assume their basic position in which the first electrical control valve 25 shuts off the second working chamber 122 of the valve actuator 11a from the outlet 201 of the pressure supply device 20 and the second electrical control valve 26 closes the second working chamber 122 of the valve actuator 11a connects to the return line 27.
  • the second working space 122 of the valve actuator 11b is also connected to the return line 27 via the check valve 30 and the opened second electrical control valve 26.
  • the two changeover valves 29, 32 take their blocking position by the return action of their return springs.
  • the control valves 25, 26 are de-energized and the switching valve 29 is depressurized.
  • the second electrical control valve 26 is first transferred to its closed or shut-off position, so that the two second working chambers 122 of the two valve actuators 11a and 11b are completed.
  • the relief valve 35 is in his closed position transferred.
  • the first electrical control valve 25 is transferred to its working or open position, so that the second working chamber 122 of the valve actuator 11a is connected to the pressure supply device 20 and the available at the output 201 of the pressure supply device 20 system pressure is now present in the second working chamber 122 of the valve actuator 11a , Since the piston surface of the actuating piston 13, which limits the first working space 121, is smaller than the piston surface of the actuating piston 13, which limits the second working space 122, a displacement force is generated which causes the actuating piston 13 in FIG Fig. 1 moved to the right, whereby the gas exchange valve 10 is opened.
  • the size of the opening stroke of the gas exchange valve 10 is dependent on the opening duration and opening speed of the first electric control valve 25.
  • the first electrical control valve 25 is switched again (in the embodiment of Fig. 1 de-energized), so that it separates the second working space 122 of the valve actuator 11a from the line 24 to the pressure supply device 20.
  • the second electrical control valve 26 is also switched over (in the embodiment of FIGS Fig. 1 de-energized), so that it connects the working spaces 122 of the two valve actuators 11a and 11b to the return line 27. Due to the system pressure in the first working spaces 121 of the valve actuators 11a and 11b, the actuating pistons 13 in the working cylinders 12 of the two valve actuators 11a and 11b become in the Fig. 1 shown basic position, whereby the gas exchange valves 10 are closed with the same closing times.
  • the check valve 30 is replaced by another second electrical control valve 26, which is also designed as a 2/2-way solenoid valve and the inlet side of the second working chamber 122 of the valve actuator 11 b and outlet side to connect directly to the return line 27.
  • an electric or electromagnetic unlockable changeover valve can also be used.
  • the further switching valve 32 can also be replaced by an electric actuator that unlocks all reversing valves 29 directly by electric motor or also hydraulically.
  • Fig. 2 partially shown device for controlling gas exchange valves in combustion cylinders of an internal combustion engine is compared to the Fig. 1 described insofar as the local switching valve 29 is replaced with connecting line 28 between the second working chambers 122 of the two valve actuators 11a and 11b by a hydraulically controlled changeover valve 34, via which the second working chamber 122 of the valve actuator 11b directly to the line 24 to the output 201th the pressure supply device 20 is connected.
  • the control valve designed as "AND gate" control valve 34 has two hydraulic control inputs 341, 342, which must be acted upon for switching the change-over valve 34 both with a hydraulic pressure.
  • the switching valve 34 still has a hydraulic return input 343, which is used to transfer the switching valve 34 in the in Fig.
  • the electrically controlled switching valve 32 is designed here as a 3/3-way solenoid valve with spring return, the second valve outlet is connected to the fluid reservoir 18. Depending on the switching position of the 3/3-way solenoid valve, pressure can be built up in the control line 31, pressure maintained or pressure reduced.
  • the switching valve 32 may also but as in Fig. 1 be designed as a 2/2-way solenoid valve. In this case, as well as in Fig. 1 still vorzuhalten the designed as a 2/2-way solenoid valve relief valve 35.
  • the switching device according to Fig. 2 unchanged, so that the same components are provided with the same reference numerals.
  • the switching valve 34 can be unlocked by driving the other switching valve 32.
  • the switching valve 34 With the unlocking of the switching valve 34, fluid flows directly from the conduit 24 into the second working chamber 122 of the valve actuator 11b, and the actuating piston 13 in the working cylinder 12 of the valve actuator 11b is displaced in a parallel stroke to the actuating piston 13 in the working cylinder 12 of the valve actuator 11a that the gas exchange valve 10 actuated by the valve actuator 11b is opened accordingly.
  • the first electric control valve 25 must be dimensioned only for the supply of the valve actuator 11a with fluid, since the valve actuator 11b directly from the pressure supply device 20 is fed. At the same time discontinuities in the lifting movement of the valve actuator 11 a are avoided, which in the control device according to Fig. 1 can be caused by the additional fluid requirement of the valve actuator 11b during the connection of the valve actuator 11b during the stroke of the valve actuator 11a.

Abstract

A device for controlling gas-exchange valves of an internal combustion engine is provided, which device has hydraulic valve actuators each allocated to one gas-exchange valve. Each valve actuator has an actuating piston acting on the gas-exchange valve, and two hydraulic working chambers delimited by the actuating piston, of which the first working chamber acting upon the gas-exchange valve in the closing direction is constantly filled with fluid under pressure, and the second working chamber acting upon the gas-exchange valve in the opening direction is able to be alternately filled with fluid under pressure and relieved via two electric control valves. For the purpose of cost reduction, provided for each valve-actuator pair is a single first electric control valve that is acted upon with the fluid pressure on the intake side, and is connected on the outlet side to the second working chamber of one valve actuator. The second working chamber of the other valve actuator is filled with fluid with the aid of a switchover valve and the fluid pressure in the second working chamber of the one valve actuator.

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 (siehe EP-A-647770 ).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 (see EP-A-647 770 ).

Bei einer bekannten Vorrichtung dieser Art ( DE 198 26 047 A1 ) ist jeder Ventilsteller, dessen Stellkolben vorzugsweise einstückig mit dem Ventilstößel des zugeordneten Gaswechselventils verbunden ist, mit seinem ersten Arbeitsraum ständig mit einer unter Hochdruck stehendes Fluid liefernden Fluiddruckquelle verbunden und mit seinem zweiten Arbeitsraum einerseits an einem eine Zuführleitung zu der Fluiddruckquelle wechselweise schließenden oder freigebenden ersten elektrischen Steuerventil und andererseits an einem eine zu einem Fluidreservoir führende Entlastungsleitung wechselweise freigebenden oder schließenden zweiten elektrischen Steuerventil angeschlossen. Die elektrische Steuerventile sind als 2/2-Wegemagnetventile mit Federrückstellung ausgebildet. Bei geschlossenem Gaswechselventil nimmt der Stellkolben des Ventilstellers aufgrund des permanent an die Fluiddruckquelle angebundenen ersten Arbeitsraums und des durch das erste elektrische Steuerventil von der Fluiddruckquelle getrennten und durch das zweite elektrische Steuerventil mit der Entlastungsleitung verbundenen zweiten Arbeitsraums seine Grundstellung ein. Zum Öffnen des Gaswechselventils werden beide elektrische Steuerventile umgeschaltet. Dadurch wird der zweite Arbeitsraum des Ventilstellers einerseits durch das zweite elektrische Steuerventil gegenüber der Entlastungsleitung gesperrt und andererseits durch das erste elektrische Steuerventil mit der Zuführleitung zur Fluiddruckquelle verbunden. Da die den zweiten Arbeitsraum im Ventilsteller begrenzende Stellkolbenfläche größer ist als die den ersten Arbeitsraum begrenzende Stellkolbenfläche bewegt sich der Stellkolben unter Verkleinern des Volumens des ersten Arbeitsraums aus seiner Grundstellung heraus und öffnet dadurch das Gaswechselventil. Die Größe des Öffnungshubs hängt von der Ausbildung des an das erste elektrische Steuerventil angelegten elektrischen Steuersignals und die Öffnungsgeschwindigkeit hängt von dem von der Fluiddruckquelle eingesteuerten Fluiddruck ab. Um das Gaswechselventil in einer bestimmten Offenstellung zu halten, wird das erste elektrische Steuerventil anschließend umgeschaltet, so daß es die Zuführleitung zum zweiten Arbeitsraum des Ventilstellers absperrt. Auf diese Weise lassen sich mittels eines elektrischen Steuergeräts zur Steuersignalerzeugung sämtliche Öffnungspositionen des Gaswechselventils einstellen. Das Schließen des Gaswechselventils erfolgt durch Rücksetzen des zweiten elektrischen Steuerventils in seine Offenstellung, so daß der erste Arbeitsraum des Ventilstellers wieder an die Entlastungsleitung angeschlossen wird. Zur Steuerung eines Gaswechselventils sind jeweils zwei elektrische Steuerventile erforderlich, die den zweiten Arbeitsraum des zugeordneten Ventilstellers entsprechend mit Fluiddruck beaufschlagen oder druckentlasten.In a known device of this type ( DE 198 26 047 A1 ) is each valve actuator, whose actuating piston is preferably integrally connected to the valve stem of the associated gas exchange valve, constantly connected to its first working space with a high-pressure fluid fluid source and its second working space on the one hand to a supply line to the fluid pressure source alternately closing or releasing first electrical control valve and on the other hand connected to a leading to a fluid reservoir discharge line alternately releasing or closing second electric control valve. The electrical control valves are designed as 2/2-way solenoid valves with spring return. When closed Gas exchange valve takes the actuator piston of the valve actuator due to the permanently connected to the fluid pressure source first working space and separated by the first electrical control valve from the fluid pressure source and connected by the second electrical control valve with the discharge line second working space a basic position. To open the gas exchange valve both electrical control valves are switched. Characterized the second working space of the valve actuator is on the one hand blocked by the second electrical control valve with respect to the discharge line and on the other hand connected by the first electric control valve to the supply line to the fluid pressure source. Since the actuating piston surface delimiting the second working chamber in the valve actuator is greater than the actuating piston surface delimiting the first working chamber, the actuating piston moves out of its basic position while reducing the volume of the first working chamber and thereby opens the gas exchange valve. The size of the opening stroke depends on the configuration of the electric control signal applied to the first electric control valve, and the opening speed depends on the fluid pressure supplied from the fluid pressure source. In order to keep the gas exchange valve in a specific open position, the first electric control valve is then switched so that it shuts off the supply line to the second working space of the valve actuator. In this way, all opening positions of the gas exchange valve can be adjusted by means of an electrical control device for generating control signals. The closing of the gas exchange valve is carried out by resetting the second electrical control valve in its open position, so that the first working space of the valve actuator back to the Relief line is connected. To control a gas exchange valve two electrical control valves are required in each case act on the second working space of the associated valve actuator in accordance with fluid pressure or depressurize.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Vorrichtung zur Steuerung von Gaswechselventilen mit den Merkmalen des Anspruchs 1 hat den Vorteil, daß durch das Ersetzten des einen ersten elektrischen Steuerventils des einen Ventilstellers im Ventilstellerpaar durch eine einfaches Umschaltventil, über das der Fluiddruck im zweiten Arbeitsraum mittels des im zweiten Arbeitsraum des anderen Ventilstellers anstehenden Fluiddrucks gesteuert wird, die Zahl der elektrischen Steuerventile pro Ventilstellerpaar reduziert wird. Wird zusätzlich noch gemäß einer bevorzugten Ausführungsform der Erfindung ein zweites elektrisches Steuerventil im Ventilstellerpaar durch ein einfaches Rückschlagventil ersetzt, das den zweiten Arbeitsraum des einen Ventilstellers mit dem dem anderen Ventilsteller zugeordneten zweiten elektrischen Steuerventil verbindet, so können pro Ventilstellerpaar zwei Magnetventile eingespart werden. Da die üblicherweise 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 elektrischen Steuerventile sehr teuer, so daß die Verringerung der Zahl der elektrischen 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 diese Steuerventile, was zu einer weiteren Kostenersparnis führt. Die geringere Zahl an elektrischen Steuerventilen verringert auch den elektrischen Energiebedarf und senkt die Ausfallwahrscheinlichkeit der Vorrichtung. Durch das geringere Bauvolumen eines einfachen Umschaltventils gegenüber einem Magnetventil kann auch der zur Unterbringung der Vorrichtung im Fahrzeug erforderliche Bauraum reduziert werden. Das von einem einzigen ersten elektrischen Steuerventil und von zwei oder nur einem zweiten elektrischen Steuerventil gesteuerte Ventilstellerpaar umfaßt solche Ventilsteller, die zur Betätigung zweier gleichartiger Gaswechselventile, also zweier Einlaßventile oder zweier Auslaßventile, in demselben Verbrennungszylinder dienen.The inventive device for controlling gas exchange valves with the features of claim 1 has the advantage that by replacing a first electric control valve of a valve actuator in the valve actuator pair by a simple switching valve, via which the fluid pressure in the second working space by means of the second working space of the other Controlled valve actuator pending fluid pressure, the number of electrical control valves per valve pair is reduced. In addition, according to a preferred embodiment of the invention, a second electrical control valve in the valve actuator pair replaced by a simple check valve that connects the second working space of a valve actuator with the second valve control valve associated second electrical control valve, so can be saved per valve actuator pair two solenoid valves. Since usually designed as 2/2-way solenoid valves electrical control valves must realize extremely short switching times, in practice about 0.3 ms at an opening cross-section of 3 mm 2 , such electrical control valves are very expensive, so that the reduction in the number of electrical Control valves in the control device brings a significant cost savings. Due to the smaller number of electrical control valves is reduced also the number of output stages and the amount of electrical wiring for these control valves, resulting in further cost savings. The smaller number of electrical control valves also reduces the electrical energy requirement and reduces the probability of failure of the device. Due to the smaller construction volume of a simple switching valve with respect to a solenoid valve and the space required to accommodate the device in the vehicle space can be reduced. The controlled by a single first electric control valve and two or only a second electric control valve valve actuator pair includes those valve actuators, which serve to actuate two similar gas exchange valves, ie two intake valves or two exhaust valves in the same combustion cylinder.

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

Gemäß einer vorteilhaften Ausführungsform der Erfindung ist das Umschaltventil in einer Verbindungsleitung zwischen den zweiten Arbeitsräumen der beiden Ventilsteller des Ventilstellerpaars angeordnet. Wird das entweder elektromotorisch, elektromagnetisch oder hydraulisch betätigbare, als 2/2-Wegeventil ausgebildete Umschaltventil entsperrt, so wird der zweite Arbeitsraum des einen Ventilstellers über den zweiten Arbeitsraum des anderen Ventilstellers mit Fluiddruck versorgt und damit der Stellkolben des Ventilstellers in Richtung Öffnen des Gaswechselventils verschoben. Durch eine geeignete Wahl des Zeitpunkts der Entsperrung des Umschaltventils können unterschiedliche Öffnungszeiten des von diesem Ventilsteller betätigten Gaswechselventils realisiert werden oder dieses Gaswechselventil bei Bedarf geschlossen gehalten werden. Das einzige erste elektrische Steuerventil im Ventilstellerpaar muß so ausgelegt werden, daß es im Extremfall den gesamten Volumenstrom stellen kann, den beide Ventilsteller eines Ventilstellerpaars zur Ausführung eines gleichzeitigen oder versetzten, aber immer parallelen Hubs benötigen. Über die Ansteuerung der zweiten elektrischen Steuerventile können unterschiedliche Schließzeiten an beiden Gaswechselventile realisiert werden. Wird, wie vorstehend angemerkt, das eine der beiden zweiten elektrischen Steuerventile durch ein Rückschlagventil ersetzt, so wird das Schließen der Gaswechselventile zum gleichen Zeitpunkt bewirkt.According to an advantageous embodiment of the invention, the switching valve is arranged in a connecting line between the second working spaces of the two valve actuators of the valve actuator pair. If this is either electromotive, electromagnetically or hydraulically actuated, designed as a 2/2-way valve switching unlocked, the second working space of a valve actuator is supplied via the second working space of the other valve actuator with fluid pressure and thus the actuator piston of the valve actuator in the direction of opening the gas exchange valve , By a suitable choice of the timing of the unlocking of the switching valve can different opening times of the actuated by this valve actuator gas exchange valve can be realized or this gas exchange valve can be kept closed if necessary. The only first electrical control valve in the valve actuator pair must be designed so that in extreme cases, it can provide the total volume flow that both valve actuators of a valve actuator pair need to perform a simultaneous or staggered but always parallel stroke. By controlling the second electrical control valves different closing times can be realized on both gas exchange valves. If, as noted above, one of the two second electrical control valves replaced by a check valve, the closing of the gas exchange valves is effected at the same time.

Gemäß einer vorteilhaften Ausführungsform der Erfindung ist das Umschaltventil ein hydraulisch betätigtes 2/2-Wegeventil mit zwei hydraulischen Steuereingängen und ist so ausgebildet, daß eine Ventilentsperrung nur bei Beaufschlagung beider Steuereingänge erfolgt. Der eine Steuereingang ist an dem mit dem einzigen ersten elektrischen Steuerventil verbundenen zweiten Arbeitsraum und der andere Steuereingang an dem Auslaß eines eingangsseitig von einem Fluiddruck beaufschlagten weiteren Umschaltventils angeschlossen. Der zweite Arbeitsraum des mit dem Umschaltventil verbundenen Ventilstellers ist über das Umschaltventil direkt an die Fluiddruckquelle gelegt. Sobald das einzige erste elektrische Steuerventil angesteuert ist, steht der von diesem in den zweiten Arbeitsraum eingesteuerte Fluiddruck auch an dem einen Steuereingang des Umschaltventils an. Die Entsperrung des Umschaltventils kann dann zum beliebigen Zeitpunkt durch Beaufschlagung des zweiten Steuereingangs durchgeführt werden wobei mit Umschalten des Umschaltventils Fluid direkt aus der Fluiddruckquelle in den zweiten Arbeitsraum des anderen Ventilstellers einströmt. Diese Ausführungsform hat den Vorteil, daß das einzige erste elektrische Steuerventil im Ventilpaar nur für die Versorgung eines einzigen Ventilstellers dimensioniert werden und nicht die gesamte Fluidmenge zur Ansteuerung beider Ventilsteller schalten muß. Zudem werden Unstetigkeiten in der Hubbewegung des einen Ventilstellers, die während des Hubs seines Stellkolbens durch die Zuschaltung des anderen Ventilstellers und durch den damit auftretenden, zusätzlichen Fluidbedarf des zweiten Arbeitsraums des nachfolgenden Ventilstellers hervorgerufen werden können, vermieden.According to an advantageous embodiment of the invention, the changeover valve is a hydraulically operated 2/2-way valve with two hydraulic control inputs and is designed so that a valve unlocking occurs only when both control inputs. One control input is connected to the second working space connected to the single first electrical control valve and the other control input is connected to the outlet of a further switching valve acted on the input side by a fluid pressure. The second working space of the valve actuator connected to the changeover valve is connected directly to the fluid pressure source via the changeover valve. As soon as the only first electric control valve is actuated, the fluid pressure which it supplies into the second working space is also applied to the one control input of the changeover valve. The unlocking of the switching valve can then at any time by applying the second control input are performed wherein flows with switching of the switching valve fluid directly from the fluid pressure source into the second working space of the other valve actuator. This embodiment has the advantage that the only first electric control valve in the valve pair to be dimensioned only for the supply of a single valve actuator and not the entire amount of fluid must switch to control both valve actuator. In addition, discontinuities in the lifting movement of a valve actuator, which can be caused during the stroke of its actuating piston by the connection of the other valve actuator and by the thus occurring, additional fluid requirement of the second working chamber of the subsequent valve actuator, avoided.

Gemäß einer vorteilhaften Ausführungsform der Erfindung werden mit dem weiteren Umschaltventil alle Umschaltventile der vorhandene Ventilpaare entsperrt, so daß in der Vorrichtung nur ein einziges weiteres Umschaltventil vorhanden ist, was Vorteile hinsichtlich der Reduzierung von Fertigungskosten und Bauraum mit sich bringt.According to an advantageous embodiment of the invention, all switching valves of the existing valve pairs are unlocked with the further switching valve, so that only a single further switching valve is present in the device, which brings advantages in terms of reducing manufacturing costs and space with it.

Gemäß einer vorteilhaften Ausführungsform der Erfindung wird die Beaufschlagung des weiteren Umschaltventils mit Fluiddruck dadurch bewirkt, daß dessen Ventileinlaß über ein Rückschlagventil an dem mit dem einzigen ersten elektrischen Steuerventil verbundenen zweiten Arbeitsraum des Ventilpaars angeschlossen ist. Alternativ kann die Druckbeaufschlagung des weiteren Umschaltventils auch durch eine externe Fluiddruckquelle, z.B. den Niederdruckkreis der Brennkraftmaschine, bewirkt werden.According to an advantageous embodiment of the invention, the application of the further switching valve with fluid pressure is effected by the fact that the valve inlet is connected via a check valve to the connected to the single first electrical control valve second working space of the valve pair. Alternatively, the pressurization of the further switching valve can also be effected by an external fluid pressure source, for example the low-pressure circuit of the internal combustion engine.

Zeichnungdrawing

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

Fig. 1
ein Schaltbild einer Vorrichtung zur Steuerung von acht in vier verschiedenen Verbrennungszylindern einer Vierzylinder-Brennkraftmaschine angeordneten Gaswechselventilen,
Fig. 2
ausschnittweise ein nicht zur Erfindung gehörendes Schaltbild einer modifizierten Vorrichtung zur Steuerung von Gaswechselventilen,
Fig. 3
eine schematisierte Darstellung eines mit einem Ventilsteller verbundenen Gaswechselventils in einem Verbrennungszylinder der Brennkraftmaschine.
The invention is described in more detail below with reference to exemplary embodiments illustrated in the drawing. Show it:
Fig. 1
a circuit diagram of an apparatus for controlling eight gas exchange valves arranged in four different combustion cylinders of a four-cylinder internal combustion engine,
Fig. 2
a detail of a not belonging to the invention diagram of a modified device for controlling gas exchange valves,
Fig. 3
a schematic representation of a connected to a valve actuator gas exchange valve in a combustion cylinder of the internal combustion engine.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die in Fig. 1 im Schaltbild dargestellte Vorrichtung zur Steuerung von Gaswechselventilen in Verbrennungszylindern einer Brennkraftmaschine ist für die Steuerung von insgesamt acht Gaswechselventilen 10, wie eines in Fig. 3 schematisch skizziert ist, konzipiert, von denen jeweils zwei in einem Verbrennungszylinder einer Vierzylinder-ViertaktBrennkraftmaschine angeordnet sind. Bei den Gaswechselventilen 10 kann es sich dabei um die Einlaßventile oder um die Auslaßventile in den Verbrennungszylindern handeln. Die Vorrichtung umfaßt eine Mehrzahl von hydraulischen Ventilstellern 11, im Ausführungsbeispiel insgesamt acht Ventilsteller 11, von denen jeweils einer ein Gaswechselventil 10 betätigt. 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 Druck- oder Arbeitsräume 121 und 122 und ist mit einem Ventilstößel 14 des Gaswechselventils 10 fest verbunden. In Fig. 3 ist in vergrößerter Darstellung ein Ventilsteller 11 in Verbindung mit einem geöffneten Gaswechselventil 10 schematisiert dargestellt. Der Ventilstößel 14 trägt an seinem vom Stellkolben 13 abgekehrten Ende eine Ventildichtfläche 15, die zur Steuerung eines Öffnungsquerschnitts mit einer im Zylinderkopf 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 oberen Druckraum oder zweiten Arbeitsraum 122 und ein Hydraulikanschluß 121a im unteren Druckraum oder ersten Arbeitsraum 121 münden.In the Fig. 1 shown in the diagram device for controlling gas exchange valves in combustion cylinders of an internal combustion engine is for the control of a total of eight gas exchange valves 10, such as one in Fig. 3 schematically outlined, each of which are 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 in the combustion cylinders act. The device comprises a plurality of hydraulic valve actuators 11, in the exemplary embodiment a total of eight valve actuators 11, of which one each actuates a gas exchange valve 10. 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 pressure or working spaces 121 and 122 and is fixedly connected to a valve tappet 14 of the gas exchange valve 10. In Fig. 3 is a schematic representation of a valve actuator 11 in conjunction with an open gas exchange valve 10 is shown in enlarged scale. The valve stem 14 carries at its end remote from the actuating piston 13 a valve sealing surface 15 which cooperates to control an opening cross-section with a formed in the cylinder head 16 of the combustion cylinder of the internal combustion engine valve seat surface 17. The working cylinder 12 has a total of three hydraulic connections, of which two hydraulic ports 122a and 122b in the upper pressure chamber or second working space 122 and a hydraulic connection 121a in the lower pressure chamber or first working space 121 open.

Die Vorrichtung weist weiter eine Druckversorgungseinrichtung 20 auf, deren Ausgang 201 eine Fluiddruckquelle zur Speisung der Ventilsteller 11 bildet. Die Druckversorgungseinrichtung 20 umfaßt eine Hochdruckpumpe 21, die Fluid aus einem Fluidreservoir 18 fördert, ein an der Hochdruckpumpe 21 auslaßsseitig angeordnetes Rückschlagventil 22 und einen Speicher 23 zur Pulsationsdämpfung und Energiespeicherung. Der Ausgang 201 der Druckversorgungseinrichtung 20, der zwischen dem Rückschlagventil 22 und dem Speicher 23 abgegriffen ist, ist über eine Leitung 24 mit den Hydraulikanschlüssen 121a der ersten Arbeitsräume 121 in allen der insgesamt acht Ventilstellern 11 verbunden, so daß die ersten Arbeitsräume 121 der Ventilsteller 11 ständig mit dem am Ausgang 201 der Druckversorgungseinrichtung 20 anstehenden, hohen Fluid- oder Hydraulikdruck beaufschlagt sind.The device further has a pressure supply device 20, whose output 201 forms a fluid pressure source for feeding the valve actuator 11. The pressure supply device 20 comprises a high-pressure pump 21, which promotes fluid from a fluid reservoir 18, a discharge valve 22 arranged on the outlet side of the high-pressure pump 21 and a storage 23 for pulsation damping and energy storage. The output 201 of the pressure supply device 20, which is tapped between the check valve 22 and the memory 23, is connected via a line 24 with the Hydraulic connections 121a of the first working spaces 121 connected in all of the total of eight valve actuators 11, so that the first working spaces 121 of the valve plate 11 are constantly applied to the output 201 of the pressure supply means 20 pending, high fluid or hydraulic pressure.

Von den insgesamt acht vorhandenen Ventilstellern 11 sind jeweils zwei Ventilsteller 11 zu einem Ventilstellerpaar zusammengefaßt, die jeweils zwei Einlaßventile oder zwei Auslaßventile im gleichen Verbrennungszylinder steuern. Der zugeordnete Verbrennungszylinder ist in Fig. 1 durch punktierte Umrandung 19 des Ventilstellerpaars mit den zugehörigen Steuermitteln symbolisiert. Zur Vereinfachung der Beschreibung sind die Ventilsteller 11 eines Ventilstellerpaars im folgenden mit 11a und 11b bezeichnet und die Beschreibung nur auf ein einem Verbrennungszylinder zugeordnetes Ventilstellerpaar beschränkt. Sie gilt jedoch in gleicher Weise für die übrigen drei den verbleibenden Verbrennungszylindern zugeordneten Ventilstellerpaare.Of the total of eight existing valve actuators 11, two valve actuators 11 are combined to form a pair of valve actuators each controlling two intake valves or two exhaust valves in the same combustion cylinder. The assigned combustion cylinder is in Fig. 1 symbolized by dotted border 19 of the valve actuator pair with the associated control means. To simplify the description, the valve actuators 11 of a valve actuator pair are referred to below as 11a and 11b, and the description is restricted to a valve actuator pair associated with a combustion cylinder. However, it applies equally to the remaining three valve pairs associated with the remaining combustion cylinders.

Der Fluidanschluß 122a des zweiten Arbeitsraums 122 des Ventilsteller 11a ist über ein erstes elektrisches Steuerventil 25, das als 2/2-Wegemagnetventil mit Federrückstellung ausgebildet ist, an der zu dem Ausgang 201 der Druckversorgungseinrichtung 20 führenden Leitung 24 angeschlossen, während der Fluidanschluß 122b des zweiten Arbeitsraums 122 des Ventilstellers 11a an ein zweites elektrisches Steuerventil 26, das ebenfalls als 2/2-Wegemagnetventil mit Federrückstellung ausgebildet ist, gelegt ist. Ausgangsseitig ist das zweite elektrische Steuerventil 26 an einer in dem Fluidreservoir 18 mündenden Rücklaufleitung 27 angeschlossen. Der Fluidanschluß 122a des zweiten Arbeitsraums 122 des Ventilstellers 11b ist mit dem Fluidanschluß 122b am Ventilsteller 11a über eine Verbindungsleitung 28 verbunden, in der ein hydraulisch entsperrbares Umschaltventil 29 mit Federrückstellung angeordnet ist. Der Fluidanschluß 122b des zweiten Arbeitsraums 122 des Ventilstellers 11b ist über ein Rückschlagventil 30 ebenfalls an dem Einlaß des zweiten elektrischen Steuerventils 26 angeschlossen. Das Umschaltventil 29 weist einen hydraulischen Steuereingang 291 auf, der über eine Steuerleitung 31 an dem Auslaß eines elektromagnetisch betätigbaren weiteren Umschaltventils 32 angeschlossen ist. Einlaßseitig ist das weitere Umschaltventil 32 über ein Rückschlagventil 33 mit dem zweiten Arbeitsraum 122 des Ventilstellers 11a verbunden. Alternativ kann aber die Einlaßseite des weiteren Umschaltventils 32 auch an dem Ausgang 201 der Druckversorgungseinrichtung 20 oder an einem Niederdruckkreis der Brennkraftmaschine angeschlossen sein. Die Auslaßseite des weiteren Umschaltventils 32 ist dabei über entsprechende Steuerleitungen 31 an alle Steuereingänge 291 der Umschaltventile 29 für alle Ventilstellerpaare gelegt. Ist das Umschaltventil 32 wie im Ausführungsbeispiel der Fig. 1 als 2/2-Wegemagnetventil mit Federrückstellung ausgebildet, so muß zur Entlastung der Steuerleitung 31 noch ein als 2/2-Wegemangetventil mit Federrückstellung ausgebildetes Entlastungsventil 35 vorgesehen werden, dessen einer Ventilanschluß mit der Steuerleitung 31 und dessen anderer Ventilanschluß mit dem Fluidreservoir 18 verbunden ist. Dieses Entlastungsventil 35 kann entfallen, wenn das Umschaltventil 32 als 3/3-Wegemagnetventil mit Federrückstellung ausgebildet wird, wie dies in Fig. 2 dargestellt ist. In diesem Fall sind von den drei Ventilanschlüssen der Ventileinlaß über das Rückschlagventil 33 wiederum an dem zweiten Arbeitsraum 122 des Ventilstellers 11a, respektive, an dem Ausgang 201 der Druckversorgungsvorrichtung 20 angeschlossen und ein erster Ventilauslaß mit der Steuerleitung 31 und ein zweiter Ventilauslaß mit dem Fluidreservoir 18 verbunden.The fluid connection 122a of the second working space 122 of the valve actuator 11a is connected to the line leading to the output 201 of the pressure supply device 20 via a first electrical control valve 25, which is designed as a 2/2-way solenoid valve with spring return, while the fluid connection 122b of the second Working space 122 of the valve actuator 11 a to a second electrical control valve 26, which is also designed as a 2/2-way solenoid valve with spring return is set. On the output side, the second electrical control valve 26 opens at an opening in the fluid reservoir 18 Return line 27 connected. The fluid port 122a of the second working chamber 122 of the valve actuator 11b is connected to the fluid port 122b on the valve actuator 11a via a connecting line 28 in which a hydraulically releasable switching valve 29 is arranged with spring return. The fluid port 122b of the second working space 122 of the valve actuator 11b is also connected via a check valve 30 to the inlet of the second electrical control valve 26. The switching valve 29 has a hydraulic control input 291 which is connected via a control line 31 at the outlet of an electromagnetically actuated further switching valve 32. On the inlet side, the further switching valve 32 is connected via a check valve 33 to the second working chamber 122 of the valve actuator 11a. Alternatively, however, the inlet side of the further switching valve 32 may also be connected to the outlet 201 of the pressure supply device 20 or to a low-pressure circuit of the internal combustion engine. The outlet side of the further switching valve 32 is placed over corresponding control lines 31 to all control inputs 291 of the switching valves 29 for all valve actuator pairs. Is the switching valve 32 as in the embodiment of Fig. 1 designed as a 2/2-way solenoid valve with spring return, so must be provided to relieve the control line 31 designed as a 2/2-Wegemangetventil with spring return relief valve 35, whose one valve connection to the control line 31 and the other valve connection to the fluid reservoir 18 is connected , This relief valve 35 can be omitted if the switching valve 32 is formed as a 3/3-way solenoid valve with spring return, as shown in Fig. 2 is shown. In this case, of the three valve ports of the valve inlet via the check valve 33 in turn to the second working chamber 122 of the valve actuator 11a, respectively, connected to the output 201 of the pressure supply device 20 and a first valve outlet to the control line 31 and a second valve outlet to the fluid reservoir 18th connected.

Bei geschlossenen Gaswechselventilen 10 nehmen die Ventilsteller 11a und 11b eines Ventilstellerpaars ihre Grundstellung ein, in der das erste elektrische Steuerventil 25 den zweiten Arbeitsraum 122 des Ventilstellers 11a von dem Ausgang 201 der Druckversorgungseinrichtung 20 absperrt und das zweite elektrische Steuerventil 26 den zweiten Arbeitsraum 122 des Ventilstellers 11a an die Rücklaufleitung 27 anschließt. Der zweite Arbeitsraum 122 des Ventilstellers 11b ist über das Rückschlagventil 30 und das geöffnete zweite elektrische Steuerventil 26 ebenfalls an die Rücklaufleitung 27 gelegt. Die beiden Umschaltventile 29, 32 nehmen durch die Rückstellwirkung ihrer Rückstellfedern ihre Sperrstellung ein. Durch den in dem ersten Arbeitsraum 121 herrschenden Systemdruck ist der Stellkolben 13 maximal in seine Grundstellung verschoben und hält über den Ventilstößel 14 das Gaswechselventil 10 geschlossen. In dem dargestellten Ausführungsbeispiel sind die Steuerventile 25, 26 stromlos und das Umschaltventil 29 drucklos.With closed gas exchange valves 10, the valve actuators 11a and 11b of a valve actuator pair assume their basic position in which the first electrical control valve 25 shuts off the second working chamber 122 of the valve actuator 11a from the outlet 201 of the pressure supply device 20 and the second electrical control valve 26 closes the second working chamber 122 of the valve actuator 11a connects to the return line 27. The second working space 122 of the valve actuator 11b is also connected to the return line 27 via the check valve 30 and the opened second electrical control valve 26. The two changeover valves 29, 32 take their blocking position by the return action of their return springs. As a result of the system pressure prevailing in the first working chamber 121, the actuating piston 13 is displaced maximally into its basic position and holds the gas exchange valve 10 closed via the valve tappet 14. In the illustrated embodiment, the control valves 25, 26 are de-energized and the switching valve 29 is depressurized.

Zum Öffnen der Gaswechselventile 10 wird zunächst das zweite elektrische Steuerventil 26 in seine Schließ- oder Absperrstellung überführt, so daß die beiden zweiten Arbeitsräume 122 der beiden Ventilsteller 11a und 11b abgeschlossen sind. Das Entlastungsventil 35 ist in seine geschlossene Position überführt. Gleichzeitig wird das erste elektrische Steuerventil 25 in seine Arbeits- oder Offenstellung überführt, so daß der zweite Arbeitsraum 122 des Ventilstellers 11a mit der Druckversorgungseinrichtung 20 verbunden ist und der am Ausgang 201 der Druckversorgungseinrichtung 20 verfügbare Systemdruck nunmehr auch im zweiten Arbeitsraum 122 des Ventilstellers 11a ansteht. Da die Kolbenfläche des Stellkolbens 13, die den ersten Arbeitsraum 121 begrenzt, kleiner ist als die Kolbenfläche des Stellkolbens 13, die den zweiten Arbeitsraum 122 begrenzt, entsteht eine Verschiebekraft, die den Stellkolben 13 in Fig. 1 nach rechts bewegt, wodurch das Gaswechselventil 10 geöffnet wird. Die Größe des Öffnungshubs des Gaswechselventils 10 ist von der Öffnungsdauer und Öffnungsgeschwindigkeit des ersten elektrischen Steuerventils 25 abhängig.To open the gas exchange valves 10, the second electrical control valve 26 is first transferred to its closed or shut-off position, so that the two second working chambers 122 of the two valve actuators 11a and 11b are completed. The relief valve 35 is in his closed position transferred. At the same time, the first electrical control valve 25 is transferred to its working or open position, so that the second working chamber 122 of the valve actuator 11a is connected to the pressure supply device 20 and the available at the output 201 of the pressure supply device 20 system pressure is now present in the second working chamber 122 of the valve actuator 11a , Since the piston surface of the actuating piston 13, which limits the first working space 121, is smaller than the piston surface of the actuating piston 13, which limits the second working space 122, a displacement force is generated which causes the actuating piston 13 in FIG Fig. 1 moved to the right, whereby the gas exchange valve 10 is opened. The size of the opening stroke of the gas exchange valve 10 is dependent on the opening duration and opening speed of the first electric control valve 25.

Wird zu einem danach liegenden Zeitpunkt oder gleichzeitig mit dem ersten elektrischen Steuerventil 25 das weitere Umschaltventil 32 angesteuert, so entsperrt dieses das Umschaltventil 29 dadurch, daß der an den Steuereingang 291 des Umschaltventils 29 über das Rückschlagventil 33 und das geöffnete weitere Umschaltventil 32 gelangende Systemdruck das Umschaltventil 29 gegen die Kraft der Rückstellfeder umschaltet. Damit wird Fluid aus dem zweiten Arbeitsraum 122 des Ventilstellers 11a in den zweiten Arbeitsraum 122 des Ventilstellers 11b einströmen, und dessen Stellkolben 13 wird in Richtung Ventilöffnen verdrängt. Da nunmehr der gesamte Fluidstrom über das erste elektrische Steuerventil 25 fließt, ist es erforderlich, daß das erste elektrische Steuerventil 25 für den maximalen Volumenstrom durch beide Ventilsteller 11a und 11b ausgelegt ist. Nach Zuschalten des zweiten Ventilstellers 11b bewegt sich das von diesem Ventilsteller 11b betätigte Gaswechselventil 10 entsprechend der Ansteuerung des ersten elektrischen Steuerventils 25, so daß die Stellkolben 13 der beiden Ventilsteller 11a und 11b - je nach Zeitpunkt des Entsperrens des Umschaltventils 29 - einen gleichzeitigen oder versetzten, parallelen Hub ausführen.If the further changeover valve 32 is actuated at a later point in time or at the same time as the first electrical control valve 25, then the changeover valve 29 is unlocked by the system pressure reaching the control input 291 of the changeover valve 29 via the check valve 33 and the opened further changeover valve 32 Changeover valve 29 switches against the force of the return spring. Thus, fluid from the second working chamber 122 of the valve actuator 11a will flow into the second working space 122 of the valve actuator 11b, and its actuating piston 13 is displaced in the direction of valve opening. Since now the entire fluid flow flows through the first electric control valve 25, it is necessary that the first electric control valve 25 is designed for the maximum flow through both valve actuators 11a and 11b. After connecting the second Valve actuator 11b moves the operated by this valve actuator 11b gas exchange valve 10 according to the control of the first electric control valve 25, so that the actuating piston 13 of the two valve actuators 11a and 11b - depending on the time of unlocking the switching valve 29 - perform a simultaneous or offset, parallel stroke ,

Zum Halten der Gaswechselventile 10 in ihrer Offenstellung wird das erste elektrische Steuerventil 25 wieder umgeschaltet (im Ausführungsbeispiel der Fig. 1 stromlos geschaltet), so daß es den zweiten Arbeitsraum 122 des Ventilstellers 11a von der Leitung 24 zur Druckversorgungseinrichtung 20 trennt.To hold the gas exchange valves 10 in their open position, the first electrical control valve 25 is switched again (in the embodiment of Fig. 1 de-energized), so that it separates the second working space 122 of the valve actuator 11a from the line 24 to the pressure supply device 20.

Sollen die Gaswechselventile 10 nach einer bestimmten Öffnungszeit wieder geschlossen werden, so wird auch das zweite elektrische Steuerventil 26 umgeschaltet (im Ausführungsbeispiel der Fig. 1 stromlos geschaltet), so daß es die Arbeitsräume 122 der beiden Ventilsteller 11a und 11b an die Rücklaufleitung 27 anschließt. Durch den Systemdruck in den ersten Arbeitsräumen 121 der Ventilsteller 11a und 11b werden die Stellkolben 13 in den Arbeitszylindern 12 der beiden Ventilsteller 11a und 11b in die in Fig. 1 gezeigte Grundstellung zurückgeführt, wodurch die Gaswechselventile 10 mit gleichen Schließzeiten geschlossen werden.If the gas exchange valves 10 are to be closed again after a certain opening time, the second electrical control valve 26 is also switched over (in the embodiment of FIGS Fig. 1 de-energized), so that it connects the working spaces 122 of the two valve actuators 11a and 11b to the return line 27. Due to the system pressure in the first working spaces 121 of the valve actuators 11a and 11b, the actuating pistons 13 in the working cylinders 12 of the two valve actuators 11a and 11b become in the Fig. 1 shown basic position, whereby the gas exchange valves 10 are closed with the same closing times.

Will man unterschiedliche Schließzeiten realisieren, so ist das Rückschlagventil 30 durch ein weiteres zweites elektrisches Steuerventil 26 zu ersetzen, das ebenfalls als 2/2-Wegemagnetventil ausgebildet und einlaßseitig an dem zweiten Arbeitsraum 122 des Ventilstellers 11b und auslaßseitig unmittelbar an die Rücklaufleitung 27 anzuschließen ist.Will you realize different closing times, the check valve 30 is replaced by another second electrical control valve 26, which is also designed as a 2/2-way solenoid valve and the inlet side of the second working chamber 122 of the valve actuator 11 b and outlet side to connect directly to the return line 27.

Anstelle des hydraulisch entsperrbaren Umschaltventils 29 zwischen den beiden zweiten Arbeitsräumen 122 der beiden Ventilsteller 11a und 11b kann auch ein elektromotorisch oder elektromagnetisch entsperrbares Umschaltventil verwendet werden. Das weitere Umschaltventil 32 kann auch durch einen elektrischen Steller ersetzt werden, der alle Umschaltventile 29 direkt elektromotorisch oder ebenfalls hydraulisch entsperrt.Instead of the hydraulically releasable changeover valve 29 between the two second working chambers 122 of the two valve actuators 11a and 11b, an electric or electromagnetic unlockable changeover valve can also be used. The further switching valve 32 can also be replaced by an electric actuator that unlocks all reversing valves 29 directly by electric motor or also hydraulically.

Die in Fig. 2 ausschnittweise dargestellte Vorrichtung zur Steuerung von Gaswechselventilen in Verbrennungszylindern einer Brennkraftmaschine ist gegenüber der zu Fig. 1 beschriebenen Vorrichtung insoweit modifiziert, als das dortige Umschaltventil 29 mit Verbindungsleitung 28 zwischen den zweiten Arbeitsräumen 122 der beiden Ventilsteller 11a und 11b durch ein hydraulisch gesteuertes Umschaltventil 34 ersetzt ist, über das der zweite Arbeitsraum 122 des Ventilstellers 11b direkt mit der Leitung 24 zum Ausgang 201 der Druckversorgungseinrichtung 20 verbunden ist. Das steuermäßig als "UND-Glied" ausgeführte Umschaltventil 34 weist zwei hydraulische Steuereingänge 341, 342 auf, die zur Umschaltung des Umschaltventils 34 beide mit einem Hydraulikdruck beaufschlagt werden müssen. Das Umschaltventil 34 besitzt noch einen hydraulischen Rückstelleingang 343, der zum Überführen des Umschaltventils 34 in die in Fig. 2 dargestellte Schließ- oder Sperrstellung von einem Hydraulikdruck beaufschlagt ist und hierzu an die Leitung 24 zum Ausgang 201 der Druckversorgungseinrichtung 20 angeschlossen ist. Der eine Steuereingang 341 des Umschaltventils 34 ist an dem Fluidanschluß 122b des zweiten Arbeitsraum 122 des Ventilstellers 11a und der andere Steuereingang 342 über die Steuerleitung 31 an dem elektrisch gesteuerten weiteren Umschaltventil 32 angeschlossen. Das elektrisch gesteuerte Umschaltventil 32 ist hier als 3/3-Wegemagnetventil mit Federrückstellung ausgebildet, dessen zweiter Ventilauslaß mit dem Fluidreservoir 18 verbunden ist. Je nach Schaltstellung des 3/3-Wegemagnetventils kann in der Steuerleitung 31 Druck aufgebaut, Druck gehalten oder Druck abgebaut werden. Das Umschaltventil 32 kann aber auch wie in Fig. 1 als 2/2-Wegemagnetventil ausgebildet werden. In diesem Fall ist ebenso wie in Fig. 1 noch das als 2/2-Wegemagnetventil ausgebildete Entlastungsventil 35 vorzuhalten. Darüber hinaus ist die Schaltvorrichtung gemäß Fig. 2 unverändert, so daß gleiche Bauteile mit gleichen Bezugszeichen versehen sind.In the Fig. 2 partially shown device for controlling gas exchange valves in combustion cylinders of an internal combustion engine is compared to the Fig. 1 described insofar as the local switching valve 29 is replaced with connecting line 28 between the second working chambers 122 of the two valve actuators 11a and 11b by a hydraulically controlled changeover valve 34, via which the second working chamber 122 of the valve actuator 11b directly to the line 24 to the output 201th the pressure supply device 20 is connected. The control valve designed as "AND gate" control valve 34 has two hydraulic control inputs 341, 342, which must be acted upon for switching the change-over valve 34 both with a hydraulic pressure. The switching valve 34 still has a hydraulic return input 343, which is used to transfer the switching valve 34 in the in Fig. 2 shown closing or locking position is acted upon by a hydraulic pressure and this is connected to the line 24 to the output 201 of the pressure supply device 20. The one control input 341 of the Change-over valve 34 is connected to the fluid port 122b of the second working chamber 122 of the valve actuator 11a and the other control input 342 via the control line 31 to the electrically controlled further switching valve 32. The electrically controlled switching valve 32 is designed here as a 3/3-way solenoid valve with spring return, the second valve outlet is connected to the fluid reservoir 18. Depending on the switching position of the 3/3-way solenoid valve, pressure can be built up in the control line 31, pressure maintained or pressure reduced. The switching valve 32 may also but as in Fig. 1 be designed as a 2/2-way solenoid valve. In this case, as well as in Fig. 1 still vorzuhalten the designed as a 2/2-way solenoid valve relief valve 35. In addition, the switching device according to Fig. 2 unchanged, so that the same components are provided with the same reference numerals.

Bei anstehendem Druck im zweiten Arbeitsraum 122 des Ventilstellers 11a ist der Steuereingang 341 hydraulisch belastet, so daß danach zu jedem Zeitpunkt das Umschaltventil 34 durch Ansteuern des weiteren Umschaltventils 32 entsperrt werden kann. Mit Entsperren des Umschaltventils 34 strömt Fluid direkt aus der Leitung 24 in den zweiten Arbeitsraum 122 des Ventilstellers 11b ein, und der Stellkolben 13 im Arbeitszylinder 12 des Ventilstellers 11b wird in einem parallelen Hub zu dem Stellkolben 13 im Arbeitszylinder 12 des Ventilstellers 11a verschoben, so daß das vom Ventilsteller 11b betätigte Gaswechselventil 10 entsprechend geöffnet wird. Bei dieser modifizierten Steuervorrichtung muß das erste elektrische Steuerventil 25 nur für die Versorgung des Ventilstellers 11a mit Fluid dimensioniert werden, da der Ventilsteller 11b direkt von der Druckversorgungseinrichtung 20 gespeist wird. Gleichzeitig werden Unstetigkeiten in der Hubbewegung des Ventilstellers 11a vermieden, die bei der Steuervorrichtung gemäß Fig. 1 bei der Zuschaltung des Ventilstellers 11b während des Hubs des Ventilstellers 11a durch den zusätzlichen Fluidbedarf des Ventilstellers 11b hervorgerufen werden können.At pending pressure in the second working chamber 122 of the valve actuator 11a of the control input 341 is hydraulically loaded, so that thereafter at any time, the switching valve 34 can be unlocked by driving the other switching valve 32. With the unlocking of the switching valve 34, fluid flows directly from the conduit 24 into the second working chamber 122 of the valve actuator 11b, and the actuating piston 13 in the working cylinder 12 of the valve actuator 11b is displaced in a parallel stroke to the actuating piston 13 in the working cylinder 12 of the valve actuator 11a that the gas exchange valve 10 actuated by the valve actuator 11b is opened accordingly. In this modified control device, the first electric control valve 25 must be dimensioned only for the supply of the valve actuator 11a with fluid, since the valve actuator 11b directly from the pressure supply device 20 is fed. At the same time discontinuities in the lifting movement of the valve actuator 11 a are avoided, which in the control device according to Fig. 1 can be caused by the additional fluid requirement of the valve actuator 11b during the connection of the valve actuator 11b during the stroke of the valve actuator 11a.

Auch bei der Stedervorrichtung gemäß Fig. 2 trifft die vorstehende Beschreibung auf die weiteren, hier nicht dargestellten Ventilpaare für die anderen Verbrennungszylinder der Brennkraftmaschine zu.Also in the Stedervorrichtung according to Fig. 2 applies the above description to the other, not shown here valve pairs for the other combustion cylinder of the internal combustion engine.

Claims (11)

  1. Device for controlling gas exchange valves (10) in combustion cylinders of an internal combustion engine, having hydraulic valve adjusters (11) which are assigned to in each case one gas exchange valve (10) and which have in each case one actuating piston (13), which acts on the gas exchange valve (10), and two hydraulic working chambers (121, 122) which are delimited by the actuating piston (13) and of which the first working chamber (121), which acts on the gas exchange valve (10) in the closing direction, is permanently filled with a pressurized fluid by means of a connection to a fluid pressure source (20), and the second working chamber (122), which acts on the gas exchange valve (10) in the opening direction, can be filled with the pressurized fluid by means of a first electric control valve (25) connected at the inlet side to the fluid pressure source (201) and can be relieved of pressure by means of a second electric control valve (26) connected at the outlet side to a low pressure level, with a single first electric control valve (25) being provided for in each case one valve adjuster pair (IIa, IIb), which single first electric control valve (25) is connected at the outlet side to the second working chamber (122) of one of the two valve adjusters (IIa), and with the filling of the second working chamber (122) of the other valve adjuster (IIb) with fluid being carried out by means of a switching valve (29), which can be switched between a blocking position and a passage position, and the fluid pressure in the second working chamber (122), which is connected to the single first electric control valve (25), of the one valve adjuster (IIa), with the switching valve (29) being arranged in a connecting line (28) between the two working chambers (122) of the two valve adjusters (IIa, IIb) of the valve adjuster pair (IIa, IIb), characterized in that the switching valve (29) is a hydraulically actuated 2/2 directional control valve and has a control inlet which is connected to the valve outlet of a further switching valve (32) which is subjected to a fluid pressure, wherein for the fluid pressurization of the further switching valve (32), the valve inlet thereof is connected via a non-return valve (33) to the second working chamber (122), which is connected to the single first electric control valve (25), of the valve adjuster pair, or wherein the pressurization of the further switching valve (32) is effected by means of an external fluid pressure source.
  2. Device according to Claim 1, characterized in that the valve adjuster pair comprises two such valve adjusters (IIa, IIb) which are assigned to two identical gas exchange valves (10), either two outlet valves or two inlet valves, in the same combustion cylinder (19).
  3. Device according to Claim 1, characterized in that the switching valve (29) is an electromotively or electromagnetically actuable 2/2 directional control valve.
  4. Device according to Claim 3, characterized in that the 2/2 directional control valve has a restoring spring (292) for restoring into the blocking position.
  5. Device according to Claim 4, characterized in that the 2/2 directional control valve has a hydraulic restoring control input (343) for restoring into the blocking position and in that the restoring control input is connected to the fluid pressure source (201).
  6. Device according to Claim 5, characterized in that the further switching valve (32) is embodied as a 2/2 directional control solenoid valve with spring restoring means, and in that the valve outlet thereof has connected to it a relief valve (35) which is preferably embodied as a 2/2 directional control solenoid valve with spring restoring means and by means of which a connection to a fluid reservoir (18) can be produced.
  7. Device according to Claim 5, characterized in that the further switching valve (32) is embodied as a 3/3 directional control solenoid valve with spring restoring means, the second valve outlet of which is connected to a fluid reservoir (18).
  8. Device according to one of Claims 1-7, characterized in that a single second electric control valve (26) is provided for in each case one valve adjuster pair (IIa, IIb), the valve inlet of which single second electric control valve (26) is connected directly to the second working chamber (122), which is connected to the single first electric control valve (25), of the one valve adjuster (IIa), and via a non-return valve (30) to the second working chamber (122) of the other valve adjuster (IIb).
  9. Device according to one of Claims 1-8, characterized in that two second electric control valves (26) are provided for in each case one valve adjuster pair (IIa, IIb), in each case one of which two second electric control valves (26) is connected at the inlet side to a second working chamber (122) of the two valve adjusters (IIa, IIb).
  10. Device according to one of Claims 1-9, characterized in that at least one valve adjuster pair (IIa, IIb) is provided per combustion cylinder, and in that the further switching valve (32) is connected at the outlet side to all the hydraulic switching valves (29) assigned to in each case one valve adjuster pair (IIa, IIb).
  11. Device according to Claims 1 and 10, characterized in that the connection of the valve inlet of the further switching valve (32) to all the valve adjuster pairs (IIa, IIb) is carried out.
EP03717127A 2002-07-06 2003-03-05 Device for the control of gas exchange valves Expired - Lifetime EP1521902B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10230478 2002-07-06
DE10230478A DE10230478A1 (en) 2002-07-06 2002-07-06 Device for controlling gas exchange valves
PCT/DE2003/000697 WO2004005679A1 (en) 2002-07-06 2003-03-05 Device for the control of gas exchange valves

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EP1521902A1 EP1521902A1 (en) 2005-04-13
EP1521902B1 true EP1521902B1 (en) 2009-06-17

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US (1) US7134408B2 (en)
EP (1) EP1521902B1 (en)
JP (1) JP4399360B2 (en)
AT (1) ATE434117T1 (en)
DE (2) DE10230478A1 (en)
WO (1) WO2004005679A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7204212B2 (en) * 2005-01-12 2007-04-17 Temic Automotive Of North America, Inc. Camless engine hydraulic valve actuated system
EP2063075A1 (en) * 2007-11-23 2009-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Fluid actuated valve mechanism
JP5589634B2 (en) * 2010-07-20 2014-09-17 いすゞ自動車株式会社 Camless engine valve opening / closing control device
FI20106256A0 (en) * 2010-11-30 2010-11-30 Waertsilae Finland Oy System and method for actuating the gas exchange valve of an internal combustion engine, cylinder head, and method for regenerating an internal combustion engine
US10113453B2 (en) * 2015-04-24 2018-10-30 Randy Wayne McReynolds Multi-fuel compression ignition engine
KR102371063B1 (en) 2017-11-20 2022-03-07 현대자동차주식회사 Control system for variable valve apparatus and oil control valve

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Publication number Priority date Publication date Assignee Title
DE69212730T2 (en) 1991-06-24 1996-12-05 Ford Werke Ag Hydraulic valve control for internal combustion engines
DE4407585C2 (en) * 1994-03-08 1996-09-19 Mtu Friedrichshafen Gmbh Variable valve timing
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
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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EP1521902A1 (en) 2005-04-13
DE10230478A1 (en) 2004-01-15
JP2005532496A (en) 2005-10-27
US20050005881A1 (en) 2005-01-13
ATE434117T1 (en) 2009-07-15
JP4399360B2 (en) 2010-01-13
US7134408B2 (en) 2006-11-14
WO2004005679A1 (en) 2004-01-15
DE50311613D1 (en) 2009-07-30

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