EP0761936B1 - Actuating unit for an adjusting device, preferably for a valve lift adjusting device of internal combustion engines - Google Patents

Actuating unit for an adjusting device, preferably for a valve lift adjusting device of internal combustion engines Download PDF

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Publication number
EP0761936B1
EP0761936B1 EP96112593A EP96112593A EP0761936B1 EP 0761936 B1 EP0761936 B1 EP 0761936B1 EP 96112593 A EP96112593 A EP 96112593A EP 96112593 A EP96112593 A EP 96112593A EP 0761936 B1 EP0761936 B1 EP 0761936B1
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EP
European Patent Office
Prior art keywords
connection
actuating unit
pressure
valve piston
adjusting device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP96112593A
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German (de)
French (fr)
Other versions
EP0761936A3 (en
EP0761936A2 (en
Inventor
Katja Schienle
Wolfgang Stephan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
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Filing date
Publication date
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Publication of EP0761936A2 publication Critical patent/EP0761936A2/en
Publication of EP0761936A3 publication Critical patent/EP0761936A3/en
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Publication of EP0761936B1 publication Critical patent/EP0761936B1/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to an actuating unit for a Adjustment device, preferably for a valve lift adjustment device of motor vehicles, according to the preamble of claim 1.
  • valve lift adjustment devices of motor vehicles it is known to use a bolt as a coupling element use that hydraulically shifted if necessary is that an adjusting element forming a fixed component, the second cam of the camshaft is associated with a control element.
  • the corresponding valve lifter leads the motor vehicle has a modified stroke, whereby the opening cross section is changed so that a particularly appropriate amount of the fuel-air mixture can flow into the cylinder space of the engine.
  • the hydraulic medium pressurized by means of a pump become. There is a brief drop in pressure inside of the system until the pump reaches the required Has built up hydraulic pressure. Then there is a risk that the coupling element is not far enough into the locking hole is inserted and so it is carried too often on the bolt edge with increased surface pressure and increased Wear comes.
  • An actuation unit according to the preamble of claim 1 is from US-A-5 537 963 known.
  • the invention has for its object the generic Train the actuator so that the coupling element abruptly in its clutch position is moved without the risk of that it is for power transmission on a narrow edge area of the coupling element comes.
  • the actuation unit according to the invention has two tank connections on, one of which relieves pressure and the other is under pressure.
  • the hydraulic medium can be quickly displaced in this way become.
  • Through the pressure relief valve of the pressure-loaded tank connection ensures that in the entire system through the pressure relief valve certain residual pressure remains, causing an idle of the system is safely prevented.
  • Should the coupling process can be triggered accordingly large amount of hydraulic medium suddenly Be made available, so that a drop in pressure Start of the coupling process reliably avoided becomes.
  • the coupling element is suddenly in his clutch position shifted. It doesn't happen a power transmission on a narrow edge area of the coupling element.
  • the actuation unit is preferably for valve lift adjustment provided by motor vehicles.
  • Valve stroke adjustment devices act on cams Camshaft with rocker arms or hydraulic cups as control elements together, directly on the respective Act on valve tappet.
  • the valves are on the corresponding Controlled opening and closing of the cams.
  • the actuator can be in the low pressure range used in systems with residual pressure become.
  • FIG. 2 schematically shows a valve lift adjustment device, which is operated with the actuation unit according to FIG. 1 becomes.
  • a coupling element designed as a piston 1 is slidably mounted in a fixed component 2.
  • a movable component 3 is adjacent to this provided, in which a piston 4 is slidably mounted is. It is under the force of at least one compression spring 5 or a hydraulic pressure.
  • the coupling element 1 In order to couple the two components 2 and 3 together, the coupling element 1 is acted upon hydraulically, whereby it is shifted to the right in Fig. 2 and the Pushes piston 4 back against the force of spring 5. The Coupling element 1 is moved until it is in engages a piston 6 receiving bore 6. Then are both parts transverse to the axis of the coupling element 1 and the piston 4 positively connected to each other.
  • the coupling element 1 serves the actuating unit according to FIG. 1. It is as Switch valve formed and has a housing 7 in which a valve piston 8 is slidably mounted. He is in a bore 9 slidably mounted, in which a pressure connection 10, a working connection 11, a pressure-relieved Tank connection 12 and a pressure-loaded tank connection 13 flow out.
  • the work connection 11 is a Throttle point 14 connected to the pressure port 10.
  • Throttle point 14a could also be the diameter play of the Valve piston 8 can be used in the bore 9. In in this case the throttle point 14 would not be required.
  • the pressure-loaded tank connection 13 is against the tank (not shown) through a pressure relief valve 15 closed that towards the Tank opens.
  • the valve piston 8 can by a plunger 16 Electromagnets 26 against the force of at least one spring 18 are axially displaced in the bore 9.
  • the Valve piston 8 has two through an annular web 19 from each other separate ring grooves 20 and 21.
  • the ring groove 20 is through a radial bore 22 with a valve piston 8 axially penetrating bore 23 connected. These holes 22 and 23 are used for hydraulic relief of the in front of and behind the valve piston 8 space 24 and 25.
  • the leakage oil is discharged through the holes 22, 23, the annular groove 21 and the tank connections 12 and 13 dissipated.
  • valve piston 8 In Fig. 1 the valve piston 8 is in the upper half shown in its open position, in which the Electromagnet 26 excited and the plunger 16 extended is so that the valve piston 8 against the force of Compression spring 18 is moved.
  • the pressure connection 10 and the working connection 11 are connected to the annular groove 20, during the working connection 11 from the pressure-relieved Tank connection 12 and from the pressure-loaded tank connection 13 is separated by the annular web 19 of the valve piston 8.
  • the working connection 11 is located via the throttle point 14 also in connection with the pressure connection 10.
  • the valve piston 8 is in the lower half of FIG. 1 shown in its closed position, in which the Electromagnet 26 is not excited.
  • the plunger 16 is retracted while the valve piston 8 by force the spring 18 pushed back into its closed position has been.
  • the working connection is in this switch position 11 via the annular groove 21 with the pressure load Tank connection 13 connected.
  • the hydraulic medium can be in this closed position via the throttle 14 from the work connection 11 get into the pressure port 10. This Measure prevents the system from idling while the engine is running. This will cause leaks, for example through lubrication points. From the work connection 11 can the hydraulic medium via the annular groove 21 of the valve piston 8 and flow back the tank connection 13 to the tank.
  • a work line 30 is at the work connection 11 (Fig. 2) of the fixed component 2 connected, so that the coupling element 1 under this bias pressure of the hydraulic medium. However, this pressure is less than that of the compression spring on the Piston 4 and thus exerted on the coupling element 1 Drag. As a result, the coupling element 1 remains in its stop position shown in Fig. 2, in the it on the bottom 31 of a receiving the coupling element Bore 32 is present.
  • the valve piston 8 has on its the compression spring 18 facing End another ring land 27 that together with the annular web 19, the annular groove 21 axially limited.
  • the ring web 27 closes the pressure-relieved Tank connection 12.
  • the open position (upper Half in Fig. 1) is the tank connection 12 through the Ring web 27 only partially closed.
  • the hydraulic medium is relieved of pressure Tank connection 12 displaced freely as long as until the valve piston 8 almost reaches its end position (lower Half in Fig. 1) has reached completely. Only is the pressure-relieved tank connection 12 through the ring land 27 separated from the annular groove 21, while the pressure-loaded Tank connection 13 via the annular groove 21 with the Work port 11 communicates.
  • the valve piston has damping during the switching process 8 an axially penetrating end bore 28, which acts as a throttle and designed as a nozzle is. It opens into the central axial bore 23.
  • the throttle point 28 can of course any have other appropriate training, for example through a reduction in the diameter of the bore 23 is formed become.
  • These control edges 33a to 35a are at the work connection 11 and provided on the pressure-relieved tank connection 12.
  • the control edges 33 to 35 and 33a to 35a are like this to each other that the coverage is very low and is therefore referred to as a zero cut.
  • valve piston 8 is in its closed position (lower half in Fig. 1), then the work connection 11 with the pressure-loaded tank connection 13 via the annular groove 21 connected.
  • the pressure relief valve 15 ensures that the entire system in this a not switched state of the actuating unit has corresponding residual pressure. This will make a System idle in the valve piston closed position 8 prevented.
  • valve piston 8 is in again by the plunger 16 the ring bridge gives its open position 27 the pressure relieved after the shortest displacement Tank connection 12 free, so that the hydraulic medium over this tank connection 12 are immediately discharged to the tank can. In the end position, the ring web 19 then separates the Working connection 11 from the tank connection 12.
  • the actuating unit 3 is the actuating unit designed as a cartridge valve.
  • the electromagnet 26 is firmly connected to the housing 7 and will used as a unit in a corresponding component 36.
  • the actuation unit also has the pressure connection 10, the working connection 11, the pressure-relieved Working connection 12, the pressure-loaded tank connection 13, in which the pressure relief valve 15 sits, and the Throttle point 14.
  • the valve piston 8 is through the tappet 16 of the electromagnet 26 from its closed position (right half in Fig. 3) against the force of the compression spring 18 moved to the open position, which in Fig. 3 in the left half is shown. In this open position of the valve piston 8 is the pressure connection 10 via the Annular groove 20 connected to the working connection 11, the through the annular webs 19, 27 of the valve piston 8 of the two tank connections 12, 13 is separated.
  • the pressure-loaded tank connection 13 is different to the previous embodiment in the axial direction of the valve piston 8 and the electromagnet 26. On the mode of operation the actuation unit changes as a result however nothing. Otherwise, this embodiment works the same as the exemplary embodiment according to FIG. 1.
  • valve piston 8 If the electromagnet 26 is switched off and thus the Plunger 16 retracted, the valve piston 8 under pushed back the force of the compression spring 18 in its closed position.
  • the ring web 27 of the valve piston 8 closes the pressure-relieved tank connection 12 when pushing back of the valve piston 8 initially not, so that the displaced hydraulic medium through this tank connection 12 can be quickly discharged to the tank.
  • the pressure-relieved tank connection 12 closed by the ring land 27 Just before the valve piston 8 reaches its closed position (right Half in Fig. 3), the pressure-relieved tank connection 12 closed by the ring land 27.
  • the pressure relief valve 15 ensures that even when not excited Electromagnet 26 the system a corresponding residual pressure has, so that an idling of the system prevents becomes.
  • Fig. 3 is an embodiment with dashed lines shown, in which the throttle point between the Pressure connection 10 and the working connection 11 are not in the housing 7, but is provided in component 36.

Description

Die Erfindung betrifft eine Betätigungseinheit für eine Verstelleinrichtung, vorzugsweise für eine Ventilhubverstelleinrichtung von Kraftfahrzeugen, nach dem Oberbegriff des Anspruches 1.The invention relates to an actuating unit for a Adjustment device, preferably for a valve lift adjustment device of motor vehicles, according to the preamble of claim 1.

Bei Ventilhubverstelleinrichtungen von Kraftfahrzeugen ist es bekannt, als Kupplungselement einen Bolzen zu verwenden, der bei Bedarf hydraulisch so verschoben wird, daß ein ein feststehendes Bauteil bildendes Verstellelement, das einem zweiten Nocken der Nockenwelle zugeordnet ist, mit einem Steuerelement gekuppelt wird. Infolge des zweiten Nockens führt der entsprechende Ventilstößel des Kraftfahrzeuges einen veränderten Hub aus, wodurch der Öffnungsquerschnitt verändert wird, so daß eine besonders zugemessene Menge des Brennstoff-Luft-Gemisches in den Zylinderraum des Motors strömen kann. Damit das Kupplungselement verschoben wird, muß das Hydraulikmedium mittels einer Pumpe mit Druck beaufschlagt werden. Es kommt kurzzeitig zu einem Druckeinbruch innerhalb des Systems, bis die Pumpe den erforderlichen Hydraulikdruck aufgebaut hat. Dann besteht die Gefahr, daß das Kupplungselement nicht weit genug in die Rastbohrung eingeschoben wird und es so zu häufigem Tragen auf der Bolzenkante mit erhöhter Flächenpressung und erhöhtem Verschleiß kommt.In valve lift adjustment devices of motor vehicles it is known to use a bolt as a coupling element use that hydraulically shifted if necessary is that an adjusting element forming a fixed component, the second cam of the camshaft is associated with a control element. As a result of the second cam, the corresponding valve lifter leads the motor vehicle has a modified stroke, whereby the opening cross section is changed so that a particularly appropriate amount of the fuel-air mixture can flow into the cylinder space of the engine. In order to the coupling element is moved, the hydraulic medium pressurized by means of a pump become. There is a brief drop in pressure inside of the system until the pump reaches the required Has built up hydraulic pressure. Then there is a risk that the coupling element is not far enough into the locking hole is inserted and so it is carried too often on the bolt edge with increased surface pressure and increased Wear comes.

Eine Betätigungseinheit gemäß Oberbegriff von Anspruch 1 ist aus der US-A-5 537 963 bekannt.An actuation unit according to the preamble of claim 1 is from US-A-5 537 963 known.

Der Erfindung liegt die Aufgabe zugrunde, die gattungsgemäße Betätigungseinheit so auszubilden, daß das Kupplungselement schlagartig in seine Kupplungsstellung verschoben wird, ohne daß hierbei die Gefahr besteht, daß es zur Kraftübertragung auf einem schmalen Randbereich des Kupplungselementes kommt.The invention has for its object the generic Train the actuator so that the coupling element abruptly in its clutch position is moved without the risk of that it is for power transmission on a narrow edge area of the coupling element comes.

Diese Aufgabe wird bei der gattungsgemäßen Betätigungseinheit erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruches 1 gelöst.This task is in the generic actuator according to the invention with the characteristic features of claim 1 solved.

Die erfindungsgemäße Betätigungseinheit weist zwei Tankanschlüsse auf, von denen der eine druckentlastet und der andere druckbelastet ist. Beim Verfahren des Ventilkolbens wird das Hydraulikmedium bis kurz vor Erreichen der Endstellung über den druckentlasteten Tankanschluß abgeführt, da er mit dem Arbeitsanschluß verbunden ist. Das Hydraulikmedium kann auf diese Weise schnell verdrängt werden. Durch das Druckbegrenzungsventil des druckbelasteten Tankanschlusses wird gewährleistet, daß im gesamten System ein durch das Druckbegrenzungsventil bestimmter Restdruck bestehen bleibt, wodurch ein Leerlaufen des Systems sicher verhindert wird. Soll der Kupplungsvorgang ausgelöst werden, kann somit eine entsprechend große Menge an Hydraulikmedium schlagartig zur Verfügung gestellt werden, so daß ein Druckeinbruch zu Beginn des Kupplungsvorganges zuverlässig vermieden wird. Das Kupplungselement wird darum schlagartig in seine Kupplungsstellung verschoben. Es kommt nicht zu einer Kraftübertragung auf einem schmalen Randbereich des Kupplungselementes.The actuation unit according to the invention has two tank connections on, one of which relieves pressure and the other is under pressure. When moving the valve piston the hydraulic medium is until shortly before reaching the end position via the pressure-relieved tank connection dissipated because it is connected to the work connection. The hydraulic medium can be quickly displaced in this way become. Through the pressure relief valve of the pressure-loaded tank connection ensures that in the entire system through the pressure relief valve certain residual pressure remains, causing an idle of the system is safely prevented. Should the coupling process can be triggered accordingly large amount of hydraulic medium suddenly Be made available, so that a drop in pressure Start of the coupling process reliably avoided becomes. The coupling element is suddenly in his clutch position shifted. It doesn't happen a power transmission on a narrow edge area of the coupling element.

Weitere Merkmale der Erfindung ergeben sich aus den weiteren Ansprüchen, der Beschreibung und den Zeichnungen.Further features of the invention result from the others Claims, the description and the drawings.

Die Erfindung wird anhand zweier in den Zeichnungen dargestellter Ausführungsbeispiele näher erläutert. Es zeigen

Fig. 1
im Axialschnitt eine als Ventil ausgebildete erfindungsgemäße Betätigungseinheit,
Fig. 2
im Schnitt und in schematischer Darstellung eine Ventilhubverstelleinrichtung, die durch die Betätigungseinheit gemäß Fig. 1 betätigt wird,
Fig. 3
im Axialschnitt eine zweite Ausführungsform einer erfindungsgemäßen Betätigungseinheit.
The invention is explained in more detail using two exemplary embodiments shown in the drawings. Show it
Fig. 1
in axial section an actuating unit according to the invention designed as a valve,
Fig. 2
in section and in a schematic representation a valve lift adjustment device which is actuated by the actuating unit according to FIG. 1,
Fig. 3
in axial section a second embodiment of an actuating unit according to the invention.

Die Betätigungseinheit ist vorzugsweise für die Ventilhubverstellung von Kraftfahrzeugen vorgesehen. Bei solchen Ventilhubverstelleinrichtungen wirken Nocken einer Nockenwelle mit Schwinghebeln oder Hydrotassen als Steuerelemente zusammen, die unmittelbar auf den jeweiligen Ventilstößel einwirken. Die Ventile werden über die entsprechenden Nocken gesteuert geöffnet und geschlossen. Darüber hinaus kann die Betätigungseinheit im Niederdruckbereich bei Anlagen mit Restdrucknotwendigkeit eingesetzt werden.The actuation unit is preferably for valve lift adjustment provided by motor vehicles. In such Valve stroke adjustment devices act on cams Camshaft with rocker arms or hydraulic cups as control elements together, directly on the respective Act on valve tappet. The valves are on the corresponding Controlled opening and closing of the cams. In addition, the actuator can be in the low pressure range used in systems with residual pressure become.

Fig. 2 zeigt schematisch eine Ventilhubverstelleinrichtung, die mit der Betätigungseinheit gemäß Fig. 1 betätigt wird. Ein als Kolben ausgebildetes Kupplungselement 1 ist in einem feststehenden Bauteil 2 verschiebbar gelagert. Benachbart hierzu ist ein bewegliches Bauteil 3 vorgesehen, in dem ein Kolben 4 verschiebbar gelagert ist. Er steht unter der Kraft wenigstens einer Druckfeder 5 oder eines Hydraulikdruckes.2 schematically shows a valve lift adjustment device, which is operated with the actuation unit according to FIG. 1 becomes. A coupling element designed as a piston 1 is slidably mounted in a fixed component 2. A movable component 3 is adjacent to this provided, in which a piston 4 is slidably mounted is. It is under the force of at least one compression spring 5 or a hydraulic pressure.

Um die beiden Bauteile 2 und 3 miteinander zu koppeln, wird das Kupplungselement 1 hydraulisch beaufschlagt, wodurch es in Fig. 2 nach rechts verschoben wird und den Kolben 4 gegen die Kraft der Feder 5 zurückschiebt. Das Kupplungselement 1 wird so weit verschoben, bis es in eine den Kolben 4 aufnehmende Bohrung 6 eingreift. Dann sind beide Teile quer zur Achse des Kupplungselementes 1 und des Kolbens 4 formschlüssig miteinander verbunden.In order to couple the two components 2 and 3 together, the coupling element 1 is acted upon hydraulically, whereby it is shifted to the right in Fig. 2 and the Pushes piston 4 back against the force of spring 5. The Coupling element 1 is moved until it is in engages a piston 6 receiving bore 6. Then are both parts transverse to the axis of the coupling element 1 and the piston 4 positively connected to each other.

Zur hydraulischen Beaufschlagung des Kupplungselementes 1 dient die Betätigungseinheit gemäß Fig. 1. Sie ist als Schaltventil ausgebildet und hat ein Gehäuse 7, in dem ein Ventilkolben 8 verschiebbar gelagert ist. Er ist in einer Bohrung 9 verschiebbar gelagert, in die ein Druckanschluß 10, ein Arbeitsanschluß 11, ein druckentlasteter Tankanschluß 12 sowie ein druckbelasteter Tankanschluß 13 münden. Der Arbeitsanschluß 11 ist über eine Drosselstelle 14 mit dem Druckanschluß 10 verbunden. Als Drosselstelle 14a könnte auch das Durchmesserspiel des Ventilkolbens 8 in der Bohrung 9 verwendet werden. In diesem Falle wäre die Drosselstelle 14 nicht erforderlich. Infolge des Durchmesserspiels könnte das Hydraulikmedium auch vom Druckanschluß 10 zum Arbeitsanschluß 11 gelangen. Der druckbelastete Tankanschluß 13 ist gegen den (nicht dargestellten) Tank durch ein Druckbegrenzungsventil 15 geschlossen, das in Richtung auf den Tank öffnet. For hydraulic loading of the coupling element 1 serves the actuating unit according to FIG. 1. It is as Switch valve formed and has a housing 7 in which a valve piston 8 is slidably mounted. He is in a bore 9 slidably mounted, in which a pressure connection 10, a working connection 11, a pressure-relieved Tank connection 12 and a pressure-loaded tank connection 13 flow out. The work connection 11 is a Throttle point 14 connected to the pressure port 10. As Throttle point 14a could also be the diameter play of the Valve piston 8 can be used in the bore 9. In in this case the throttle point 14 would not be required. As a result of the diameter play, the hydraulic medium could also from the pressure connection 10 to the work connection 11 arrive. The pressure-loaded tank connection 13 is against the tank (not shown) through a pressure relief valve 15 closed that towards the Tank opens.

Der Ventilkolben 8 kann durch einen Stößel 16 eines Elektromagneten 26 gegen die Kraft wenigstens einer Feder 18 in der Bohrung 9 axial verschoben werden. Der Ventilkolben 8 hat zwei durch einen Ringsteg 19 voneinander getrennte Ringnuten 20 und 21. Die Ringnut 20 ist durch eine Radialbohrung 22 mit einer den Ventilkolben 8 axial durchsetzenden Bohrung 23 verbunden. Diese Bohrungen 22 und 23 dienen zur hydraulischen Entlastung des vor und hinter dem Ventilkolben 8 befindlichen Raumes 24 und 25. Das anfallende Leckageöl wird über die Bohrungen 22, 23, die Ringnut 21 und die Tankanschlüsse 12 und 13 abgeführt.The valve piston 8 can by a plunger 16 Electromagnets 26 against the force of at least one spring 18 are axially displaced in the bore 9. The Valve piston 8 has two through an annular web 19 from each other separate ring grooves 20 and 21. The ring groove 20 is through a radial bore 22 with a valve piston 8 axially penetrating bore 23 connected. These holes 22 and 23 are used for hydraulic relief of the in front of and behind the valve piston 8 space 24 and 25. The leakage oil is discharged through the holes 22, 23, the annular groove 21 and the tank connections 12 and 13 dissipated.

In Fig. 1 ist der Ventilkolben 8 in der oberen Hälfte in seiner Öffnungsstellung dargestellt, in welcher der Elektromagnet 26 erregt und der Stößel 16 ausgefahren ist, so daß der Ventilkolben 8 gegen die Kraft der Druckfeder 18 verschoben ist. Der Druckanschluß 10 und der Arbeitsanschluß 11 sind mit der Ringnut 20 verbunden, während der Arbeitsanschluß 11 vom druckentlasteten Tankanschluß 12 und vom druckbelasteten Tankanschluß 13 durch den Ringsteg 19 des Ventilkolbens 8 getrennt ist. Über die Drosselstelle 14 steht der Arbeitsanschluß 11 auch in Verbindung mit dem Druckanschluß 10.In Fig. 1 the valve piston 8 is in the upper half shown in its open position, in which the Electromagnet 26 excited and the plunger 16 extended is so that the valve piston 8 against the force of Compression spring 18 is moved. The pressure connection 10 and the working connection 11 are connected to the annular groove 20, during the working connection 11 from the pressure-relieved Tank connection 12 and from the pressure-loaded tank connection 13 is separated by the annular web 19 of the valve piston 8. The working connection 11 is located via the throttle point 14 also in connection with the pressure connection 10.

In der unteren Hälfte der Fig. 1 ist der Ventilkolben 8 in seiner Schließstellung dargestellt, in welcher der Elektromagnet 26 nicht erregt ist. Der Stößel 16 ist zurückgefahren, während der Ventilkolben 8 durch die Kraft der Feder 18 in seine Schließstellung zurückgeschoben worden ist. In dieser Schaltstellung ist der Arbeitsanschluß 11 über die Ringnut 21 mit dem druckbelasteten Tankanschluß 13 verbunden. Das Hydraulikmedium kann in dieser Schließstellung über die Drosselstelle 14 vom Arbeitsanschluß 11 in den Druckanschluß 10 gelangen. Diese Maßnahme verhindert ein Leerlaufen des Systems, während der Motor läuft. Dadurch werden Leckagen, beispielsweise durch Schmierstellen, ausgeglichen. Vom Arbeitsanschluß 11 kann das Hydraulikmedium über die Ringnut 21 des Ventilkolbens 8 und den Tankanschluß 13 zum Tank zurückströmen.The valve piston 8 is in the lower half of FIG. 1 shown in its closed position, in which the Electromagnet 26 is not excited. The plunger 16 is retracted while the valve piston 8 by force the spring 18 pushed back into its closed position has been. The working connection is in this switch position 11 via the annular groove 21 with the pressure load Tank connection 13 connected. The hydraulic medium can be in this closed position via the throttle 14 from the work connection 11 get into the pressure port 10. This Measure prevents the system from idling while the engine is running. This will cause leaks, for example through lubrication points. From the work connection 11 can the hydraulic medium via the annular groove 21 of the valve piston 8 and flow back the tank connection 13 to the tank.

An den Arbeitsanschluß 11 ist eine Arbeitsleitung 30 (Fig. 2) des feststehenden Bauteiles 2 angeschlossen, so daß auch das Kupplungselement 1 unter diesem Vorspanndruck des Hydraulikmediums steht. Dieser Druck ist allerdings geringer als die von der Druckfeder auf den Kolben 4 und damit auf das Kupplungselement 1 ausgeübte Gegenkraft. Dadurch bleibt das Kupplungselement 1 in seiner in Fig. 2 dargestellten Anschlagstellung, in der es am Boden 31 einer das Kupplungselement aufnehmenden Bohrung 32 anliegt.A work line 30 is at the work connection 11 (Fig. 2) of the fixed component 2 connected, so that the coupling element 1 under this bias pressure of the hydraulic medium. However, this pressure is less than that of the compression spring on the Piston 4 and thus exerted on the coupling element 1 Drag. As a result, the coupling element 1 remains in its stop position shown in Fig. 2, in the it on the bottom 31 of a receiving the coupling element Bore 32 is present.

Der Ventilkolben 8 hat an seinem der Druckfeder 18 zugewandten Ende einen weiteren Ringsteg 27, der zusammen mit dem Ringsteg 19 die Ringnut 21 axial begrenzt. In der Schließstellung des Ventilkolbens 8 (untere Hälfte in Fig. 1) verschließt der Ringsteg 27 den druckentlasteten Tankanschluß 12. In der Offenstellung (obere Hälfte in Fig. 1) ist der Tankanschluß 12 durch den Ringsteg 27 nur teilweise verschlossen. Beim Zurückfahren des Ventilkolbens 8 aus der Offenstellung in die Schließstellung wird das Hydraulikmedium über den druckentlasteten Tankanschluß 12 so lange frei verdrängt, bis der Ventilkolben 8 nahezu seine Endstellung (untere Hälfte in Fig. 1) vollständig erreicht hat. Erst dann ist der druckentlastete Tankanschluß 12 durch den Ringsteg 27 von der Ringnut 21 getrennt, während der druckbelastete Tankanschluß 13 über die Ringnut 21 mit dem Arbeitsanschluß 11 in Verbindung steht.The valve piston 8 has on its the compression spring 18 facing End another ring land 27 that together with the annular web 19, the annular groove 21 axially limited. In the closed position of the valve piston 8 (lower half in Fig. 1) the ring web 27 closes the pressure-relieved Tank connection 12. In the open position (upper Half in Fig. 1) is the tank connection 12 through the Ring web 27 only partially closed. When driving back of the valve piston 8 from the open position in the In the closed position, the hydraulic medium is relieved of pressure Tank connection 12 displaced freely as long as until the valve piston 8 almost reaches its end position (lower Half in Fig. 1) has reached completely. Only is the pressure-relieved tank connection 12 through the ring land 27 separated from the annular groove 21, while the pressure-loaded Tank connection 13 via the annular groove 21 with the Work port 11 communicates.

Da das Hydraulikmedium beim Zurückfahren über den druckentlasteten Tankanschluß 12 frei verdrängt wird, kann der Ventilkolben 8 durch die Druckfeder 18 zuverlässig in seine Schließstellung zurückgefahren werden, in der er den Druckanschluß 10 vom Arbeitsanschluß 11 mit seinem Ringsteg 19 trennt.Because the hydraulic medium when returning over the pressure-relieved Tank connection 12 is displaced freely, can the valve piston 8 by the compression spring 18 reliably be returned to its closed position in which he the pressure port 10 from the working port 11 with his Ring web 19 separates.

Zur Dämpfung während des Schaltvorganges hat der Ventilkolben 8 eine axial ihn durchsetzende stirnseitige Bohrung 28, die als Drosselstelle wirkt und als Düse ausgebildet ist. Sie mündet in die zentrale axiale Bohrung 23. Die Drosselstelle 28 kann selbstverständlich jede andere geeignete Ausbildung haben, zum Beispiel durch eine Verkleinerung des Durchmessers der Bohrung 23 gebildet werden.The valve piston has damping during the switching process 8 an axially penetrating end bore 28, which acts as a throttle and designed as a nozzle is. It opens into the central axial bore 23. The throttle point 28 can of course any have other appropriate training, for example through a reduction in the diameter of the bore 23 is formed become.

Die beiden Ringstege 19 und 27 des Ventilkolbens 8 bilden Steuerkanten 33, 34 und 35, die mit entsprechenden Steuerkanten 33a bis 35a des Gehäuses 7 zusammenwirken. Diese Steuerkanten 33a bis 35a sind am Arbeitsanschluß 11 sowie am druckentlasteten Tankanschluß 12 vorgesehen. Die Steuerkanten 33 bis 35 und 33a bis 35a sind so zueinander ausgebildet, daß die Überdeckung sehr gering ist und darum als Nullschnitt bezeichnet wird.Form the two ring webs 19 and 27 of the valve piston 8 Control edges 33, 34 and 35 with corresponding ones Control edges 33a to 35a of the housing 7 cooperate. These control edges 33a to 35a are at the work connection 11 and provided on the pressure-relieved tank connection 12. The control edges 33 to 35 and 33a to 35a are like this to each other that the coverage is very low and is therefore referred to as a zero cut.

Befindet sich der Ventilkolben 8 in seiner Schließstellung (untere Hälfte in Fig. 1), dann ist der Arbeitsanschluß 11 mit dem druckbelasteten Tankanschluß 13 über die Ringnut 21 verbunden. Das Druckbegrenzungsventil 15 gewährleistet, daß das gesamte System auch in diesem nicht geschalteten Zustand der Betätigungseinheit einen entsprechenden Restdruck aufweist. Dadurch wird ein Leerlaufen des Systems in der Schließstellung'des Ventilkolbens 8 verhindert.The valve piston 8 is in its closed position (lower half in Fig. 1), then the work connection 11 with the pressure-loaded tank connection 13 via the annular groove 21 connected. The pressure relief valve 15 ensures that the entire system in this a not switched state of the actuating unit has corresponding residual pressure. This will make a System idle in the valve piston closed position 8 prevented.

Beim Zurückfahren des Ventilkolbens 8 aus der Offenstellung (obere Hälfte in Fig. 1) in die Schließstellung (untere Hälfte in Fig. 1) wird das Hydraulikmedium über den druckentlasteten Tankanschluß 12 zum Tank abgeführt, während der druckbelastete Tankanschluß 13 infolge des Druckbegrenzungsventiles 15 geschlossen bleibt. Kurz bevor der Ventilkolben 8 seine Schließstellung erreicht, wird der druckentlastete Tankanschluß 12 geschlossen. Das unter Druck stehende Hydraulikmedium wird dann am Ende des Verschiebeweges des Ventilkolbens 8 über den druckbelasteten Tankanschluß 13 abgeführt, solange der Druck des Hydraulikmediums größer ist als der durch das Druckbegrenzungsventil 15 bestimmte Druck.When the valve piston 8 moves back from the open position (upper half in Fig. 1) in the closed position (lower half in Fig. 1) the hydraulic medium is over discharged the pressure-relieved tank connection 12 to the tank, during the pressure-loaded tank connection 13 as a result of Pressure relief valve 15 remains closed. Shortly before the valve piston 8 reaches its closed position, the pressure-relieved tank connection 12 is closed. The pressurized hydraulic medium is then on End of the displacement of the valve piston 8 over the discharged pressure-charged tank port 13 as long as the Pressure of the hydraulic medium is greater than that by the Pressure relief valve 15 certain pressure.

Wird der Ventilkolben 8 durch den Stößel 16 wieder in seine Offenstellung zurückgeschoben, gibt der Ringsteg 27 nach kürzestem Verschiebeweg den druckentlasteten Tankanschluß 12 frei, so daß das Hydraulikmedium über diesen Tankanschluß 12 sofort zum Tank abgeführt werden kann. In der Endstellung trennt dann der Ringsteg 19 den Arbeitsanschluß 11 vom Tankanschluß 12.The valve piston 8 is in again by the plunger 16 the ring bridge gives its open position 27 the pressure relieved after the shortest displacement Tank connection 12 free, so that the hydraulic medium over this tank connection 12 are immediately discharged to the tank can. In the end position, the ring web 19 then separates the Working connection 11 from the tank connection 12.

Bei der Ausführungsform nach Fig. 3 ist die Betätigungseinheit als Cartridge-Ventil ausgebildet. Der Elektromagnet 26 ist mit dem Gehäuse 7 fest verbunden und wird als Einheit in einem entsprechenden Bauteil 36 eingesetzt. Die Betätigungseinheit hat ebenfalls den Druckanschluß 10, den Arbeitsanschluß 11, den druckentlasteten Arbeitsanschluß 12, den druckbelasteten Tankanschluß 13, in dem das Druckbegrenzungsventil 15 sitzt, und die Drosselstelle 14. Der Ventilkolben 8 wird durch den Stößel 16 des Elektromagneten 26 aus seiner Schließlage (rechte Hälfte in Fig. 3) gegen die Kraft der Druckfeder 18 in die Offenstellung verschoben, die in Fig. 3 in der linken Hälfte dargestellt ist. In dieser Offenstellung des Ventilkolbens 8 ist der Druckanschluß 10 über die Ringnut 20 mit dem Arbeitsanschluß 11 verbunden, der durch die Ringstege 19, 27 des Ventilkolbens 8 von den beiden Tankanschlüssen 12, 13 getrennt ist.3 is the actuating unit designed as a cartridge valve. The electromagnet 26 is firmly connected to the housing 7 and will used as a unit in a corresponding component 36. The actuation unit also has the pressure connection 10, the working connection 11, the pressure-relieved Working connection 12, the pressure-loaded tank connection 13, in which the pressure relief valve 15 sits, and the Throttle point 14. The valve piston 8 is through the tappet 16 of the electromagnet 26 from its closed position (right half in Fig. 3) against the force of the compression spring 18 moved to the open position, which in Fig. 3 in the left half is shown. In this open position of the valve piston 8 is the pressure connection 10 via the Annular groove 20 connected to the working connection 11, the through the annular webs 19, 27 of the valve piston 8 of the two tank connections 12, 13 is separated.

Der druckbelastete Tankanschluß 13 liegt im Unterschied zum vorigen Ausführungsbeispiel in Achsrichtung des Ventilkolbens 8 sowie des Elektromagneten 26. An der Wirkungsweise der Betätigungseinheit ändert sich dadurch jedoch nichts. Im übrigen arbeitet diese Ausführungsform gleich wie das Ausführungsbeispiel nach Fig. 1.The pressure-loaded tank connection 13 is different to the previous embodiment in the axial direction of the valve piston 8 and the electromagnet 26. On the mode of operation the actuation unit changes as a result however nothing. Otherwise, this embodiment works the same as the exemplary embodiment according to FIG. 1.

Wird der Elektromagnet 26 abgeschaltet und damit der Stößel 16 zurückgefahren, wird der Ventilkolben 8 unter der Kraft der Druckfeder 18 in seine Schließstellung zurückgeschoben. Der Ringsteg 27 des Ventilkolbens 8 verschließt den druckentlasteten Tankanschluß 12 beim Zurückschieben des Ventilkolbens 8 zunächst nicht, so daß das verdrängte Hydraulikmedium über diesen Tankanschluß 12 rasch zum Tank abgeführt werden kann. Erst kurz bevor der Ventilkolben 8 seine Schließstellung erreicht (rechte Hälfte in Fig. 3), wird der druckentlastete Tankanschluß 12 durch den Ringsteg 27 geschlossen. Wie bei der vorigen Ausführungsform wird durch das Druckbegrenzungsventil 15 gewährleistet, daß auch bei nicht erregtem Elektromagneten 26 das System einen entsprechenden Restdruck aufweist, so daß ein Leerlaufen des Systems verhindert wird. If the electromagnet 26 is switched off and thus the Plunger 16 retracted, the valve piston 8 under pushed back the force of the compression spring 18 in its closed position. The ring web 27 of the valve piston 8 closes the pressure-relieved tank connection 12 when pushing back of the valve piston 8 initially not, so that the displaced hydraulic medium through this tank connection 12 can be quickly discharged to the tank. Just before the valve piston 8 reaches its closed position (right Half in Fig. 3), the pressure-relieved tank connection 12 closed by the ring land 27. As with the previous embodiment is through the pressure relief valve 15 ensures that even when not excited Electromagnet 26 the system a corresponding residual pressure has, so that an idling of the system prevents becomes.

In Fig. 3 ist mit gestrichelten Linien eine Ausführungsform dargestellt, bei der die Drosselstelle zwischen dem Druckanschluß 10 und dem Arbeitsanschluß 11 nicht im Gehäuse 7, sondern im Bauteil 36 vorgesehen ist.In Fig. 3 is an embodiment with dashed lines shown, in which the throttle point between the Pressure connection 10 and the working connection 11 are not in the housing 7, but is provided in component 36.

Claims (7)

  1. An actuating unit for an adjusting device, preferably for a valve-lift adjusting device in motor vehicles, comprising at least one coupling member, to which a fixed and a movable component of the adjusting device are connectable and which is hydraulically adjustable via at least one valve piston of the actuating unit, by means of which, in a closed position, at least one operating connection is disconnectable from a pressure connection,
    characterised in that the actuating unit has a depressurised filling connection (12) and a pressurised filling connection (13) provided with a pressure-limiting valve (15), in that the depressurised filling connection (12) is connected to the operating connection (11) during displacement of the valve piston (8) until shortly before reaching the respective end position, and in that, in the closed position, the operating connection (11) is connected to the pressurised filling connection (13).
  2. An actuating unit according to claim 1, characterised in that the valve piston (8) has a ring land (27) disconnecting the depressurised filling connection (12) from the operating connection (11) when the valve piston (8) is in the closed position.
  3. An actuating unit according to claim 1 or 2, characterised in that the valve piston (8) has a further ring land (19) disconnecting the pressure connection (10) from the operating connection (11) when the valve piston (8) is in the closed position.
  4. An actuating unit according to any one of claims 1 to 3, characterised in that the pressure connection (10) is connected to the operating connection (11) via a throttle (14).
  5. An actuating unit according to claim 4, characterised in that the throttle (14) is provided in a housing (7) of the actuating unit.
  6. An actuating unit according to claim 4, characterised in that the throttle (14) is provided in a component (36) receiving the housing (7) of the actuating unit.
  7. An actuating unit according to any one of claims 1 to 6, characterised in that the valve piston (8) has at least one throttle (28) connecting a hydraulic chamber (24) upstream of the valve piston (8) to an axial bore (23) of the valve piston (8).
EP96112593A 1995-08-26 1996-08-03 Actuating unit for an adjusting device, preferably for a valve lift adjusting device of internal combustion engines Expired - Lifetime EP0761936B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19531444 1995-08-26
DE19531444A DE19531444A1 (en) 1995-08-26 1995-08-26 Actuating unit for an adjustment device, preferably for a valve lift adjustment device of motor vehicles

Publications (3)

Publication Number Publication Date
EP0761936A2 EP0761936A2 (en) 1997-03-12
EP0761936A3 EP0761936A3 (en) 1998-01-21
EP0761936B1 true EP0761936B1 (en) 2001-01-10

Family

ID=7770471

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96112593A Expired - Lifetime EP0761936B1 (en) 1995-08-26 1996-08-03 Actuating unit for an adjusting device, preferably for a valve lift adjusting device of internal combustion engines

Country Status (5)

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US (1) US5732612A (en)
EP (1) EP0761936B1 (en)
JP (1) JPH09105302A (en)
DE (2) DE19531444A1 (en)
ES (1) ES2153064T3 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005028805A1 (en) * 2005-06-22 2007-01-04 GM Global Technology Operations, Inc., Detroit Device for hydraulic valve lift switching
US10731519B2 (en) * 2018-09-19 2020-08-04 Hyundai Motor Company Control system and control method for hydraulic variable valve
CN110966062B (en) * 2018-09-30 2022-09-27 现代自动车株式会社 Control system and control method for hydraulic variable valve

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3224119A1 (en) * 1982-06-29 1983-12-29 Robert Bosch Gmbh, 7000 Stuttgart HYDRAULIC ELECTROMAGNETICALLY ACTUATED VALVE
JPS6090906A (en) * 1983-10-25 1985-05-22 Honda Motor Co Ltd Valve suspending device in engine
US4525695A (en) * 1984-04-04 1985-06-25 Parker Hannifin Corporation Force motor with ball mounted armature
JPS60240813A (en) * 1984-05-14 1985-11-29 Honda Motor Co Ltd Valve mechanism with valve pausing function
US4971114A (en) * 1988-11-21 1990-11-20 Diesel Kiki Co., Ltd. Electromagnetic proportional pressure control valve
JP2853237B2 (en) * 1990-02-09 1999-02-03 住友電気工業株式会社 Hydraulic pressure control device
DE9402206U1 (en) * 1994-02-10 1994-05-05 Hydraulik Ring Gmbh Electro proportional solenoid valve unit
US5598871A (en) * 1994-04-05 1997-02-04 Sturman Industries Static and dynamic pressure balance double flow three-way control valve
JP3373947B2 (en) * 1994-09-02 2003-02-04 本田技研工業株式会社 Valve train for multi-cylinder internal combustion engine

Also Published As

Publication number Publication date
DE59606295D1 (en) 2001-02-15
EP0761936A3 (en) 1998-01-21
DE19531444A1 (en) 1997-02-27
US5732612A (en) 1998-03-31
ES2153064T3 (en) 2001-02-16
EP0761936A2 (en) 1997-03-12
JPH09105302A (en) 1997-04-22

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