EP2226476B1 - Hydraulic unit for a cylinder head of a combustion engine with hydraulically variable gas exchange valve drive - Google Patents

Hydraulic unit for a cylinder head of a combustion engine with hydraulically variable gas exchange valve drive Download PDF

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Publication number
EP2226476B1
EP2226476B1 EP20100154527 EP10154527A EP2226476B1 EP 2226476 B1 EP2226476 B1 EP 2226476B1 EP 20100154527 EP20100154527 EP 20100154527 EP 10154527 A EP10154527 A EP 10154527A EP 2226476 B1 EP2226476 B1 EP 2226476B1
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EP
European Patent Office
Prior art keywords
hydraulic
housing
housing part
seal
unit
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.)
Not-in-force
Application number
EP20100154527
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German (de)
French (fr)
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EP2226476A1 (en
Inventor
Mario Kuhl
Andreas Eichenberg
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2226476A1 publication Critical patent/EP2226476A1/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423Details relating to the hydraulic feeding circuit
    • F01L2001/34446Fluid accumulators for the feeding circuit
    • YGENERAL 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
    • Y10TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10TTECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00Fluid handling
    • Y10T137/8593Systems
    • Y10T137/86493Multi-way valve unit

Definitions

  • Such a hydraulic unit is from the unpublished EP 2 060 754 A2 (State of the art according to Art. 54 (3) EPC).
  • the lower housing part is formed very compact design, and in the intermediate housing part is also a substantially flat plate, so that each of the intermediate pressure chambers is limited to a correspondingly small volume.
  • a small-volume medium-pressure chamber during the starting process of the internal combustion engine can be problematic, especially if it is a starting operation at low ambient temperatures and after a long period of stoppage of the internal combustion engine.
  • This problem applies to a greater extent in a short time repetitive starting operations, since in this case the hydraulic fluid consumption from the medium-pressure space can be greater than the nachge deviste from the hydraulic fluid supply to the internal combustion engine volume.
  • Such multi-start operations are typical, for example, for taxi cabs at taxi stands.
  • Another hydraulic unit is off DE 10 2006 008 676 A1 known.
  • the present invention is therefore based on the object, a hydraulic unit of the type mentioned in such a way that the throttle opening between the medium-pressure chamber and the low-pressure chamber with little effort and at the same time as precisely produced.
  • the throttle opening extends in a housing seal, as a separate Component is arranged either between the lower housing part or the upper housing part on the one hand and the intermediate housing part on the other hand, wherein the intermediate portion of the housing passing through portion of the hydraulic fluid channel is formed throttle-poor.
  • the displacement of the throttle opening from the intermediate housing part in the housing seal leads to a significantly lower production costs, since the throttle opening in particular by punching a single or multi-layer metal seal, as it is often used as such in the cylinder head of internal combustion engines, precise and inexpensive to produce.
  • the intermediate housing part is significantly less expensive to produce as a result of its now dropping throttle effect.
  • the housing seal should be formed as a flat gasket and have a tubular elevation which limits the throttle opening in the manner of a nozzle.
  • the nozzle-like geometry of the throttle opening leads to a pronounced viscosity dependency of the hydraulic fluid volume flow such that the volume flow to be throttled at low temperatures / high-viscosity hydraulic fluid is significantly smaller than at high temperatures / low-viscosity hydraulic fluid.
  • This throttle characteristic is particularly advantageous when the upper housing part is provided with an opening into the cylinder head overflow. This not only serves to vent the low pressure chamber, but also the cooling of the hydraulic unit by escaping heated hydraulic fluid via low pressure chamber in the cylinder head and thus can be returned to the cooled hydraulic fluid circuit of the engine.
  • the viscosity-dependent throttle effect causes a needs-based flushing of the hydraulic unit, which is ideally such that when hot hydraulic fluid flushing the largest possible and cold hydraulic fluid is carried out no rinsing of the hydraulic unit.
  • the housing seal is expediently arranged between the housing lower part and the housing intermediate part, and the elevation extends into a through-bore in the housing intermediate part Gas bubbles in the medium-pressure space can escape in the best possible way into the low-pressure space.
  • a further housing seal may be provided, which is likewise designed as a separate component and is arranged between the lower housing part and the upper housing part on the side facing away from the housing seal of the intermediate housing part. Consequently, the hydraulic unit is sealed by means of separate housing seals in the region of both joints on the intermediate housing part to the environment.
  • these housing seals may be formed differently from one another so that the section of the hydraulic fluid channel which passes through the further housing seal is of low-throttle design.
  • the function of the further housing seal in this case is limited to the sealing of the hydraulic unit to the environment.
  • the housing seal and the further housing seal can also be identical parts. Due to corresponding unit-price effects, further reduced production costs are to be expected. Due to the then double throttle effect is also possible to run the throttle openings with a relatively large cross-section in favor of further improved manufacturability.
  • the known manner of operation of the hydraulic gas exchange valve drive 1 can be summarized to the effect that the high pressure chamber 11 between the transmitter unit 6 and the slave unit 8 acts as a hydraulic linkage, which - neglecting leaks - proportional to the stroke of the cam 3 displaced by the pump plunger 7 hydraulic volume as a function of the opening time and the opening duration of the hydraulic valve 10 in a first, the slave piston 9 acting sub-volume and in a second, in the medium pressure chamber 12 including pressure accumulator 13 effluent partial volume is split.
  • the stroke transmission of the pump tappet 7 to the slave piston 9 and therefore not only the timing, but also the lifting height of the gas exchange valve 4 are fully variable adjustable.
  • FIG. 2 Cross-section shown hydraulic unit 5 for a 4-cylinder in-line engine has as a further essential part of a common Hydraulic housing 19, so that the hydraulic unit 5 can be mounted as a preassembled and possibly already filled with hydraulic fluid assembly in the cylinder head 2 of the internal combustion engine.
  • the composite in sandwich construction hydraulic housing 19 consists of a lower housing part 20, a housing intermediate part 21 and a housing upper part 22.
  • To seal the parting line between the housing base 20 and housing intermediate part 21 extends a housing seal 23, and for sealing the parting line between the housing intermediate part 21 and upper housing part 22 extends a further housing seal 24.
  • Both seals 23, 24 are separate components in the form of single-layer metal seals.
  • the housing parts 20, 21, 22 are screwed together hydraulically sealingly at various screwing points 25.
  • the lower housing part 20 separate Verschraubungspond 26 on.
  • the four transmitter units 6 extending in the housing lower part 20 each include the pump plunger 7, which is spring-loaded in the return stroke direction and which is driven by a cam-operated drag lever, not shown here.
  • the pivotable mounting of the drag levers takes place by means of support elements 27, which are also accommodated in the lower housing part 20. From the intermediate housing part 21 outgoing bracket 28, serve as a captive for the drag lever with not mounted in the cylinder head 2 hydraulic unit 5. This is further designed so that each of the transmitter units 6 with two extending in the housing base 20 slave units 8 (see FIG. 1 ) cooperates.
  • the respective one encoder unit 6 and the two slave units 8 associated hydraulic valves 10 can be seen with electrical connectors 29.
  • the medium-pressure chamber 12 with the high-pressure chamber 11 (see FIG. 1 ) connecting hydraulic valves 10 are fixed in a known per se and not shown here in valve receptacles in the housing base 20. Further recognizable is the pressure accumulator 13 connected to the medium-pressure chamber 12 with the compensating piston 14 which is acted on by spring force.
  • Each serving as a hydraulic fluid reservoir for the associated medium-pressure chamber 12 low-pressure spaces 16 are formed by bulges in the upper housing part 22, which is made by deep-drawing of sheet steel.
  • the low-pressure chamber 16 and the medium-pressure chamber 12 are connected to each other via a hydraulic fluid channel, which extends through the housing seals 23, 24 and the intermediate housing part 21.
  • a partition 18 according to FIG. 1 is used between the housing base 20 and housing intermediate part 21 inserted housing seal 23 with punched throttle opening 17 ', which has a diameter of about 0.4 mm.
  • the further housing seal 24 between housing intermediate part 21 and housing upper part 22 differs from the housing seal 23 in that its passage 30 as well as the through bore 31 in the housing intermediate part 21 has a multiple of the cross section of the throttle opening 17 '.
  • the passage 30 and the easy-to-produce through-hole 31 thus represent throttle-poor portions of the hydraulic fluid channel.
  • FIG. 3 alternative embodiment of the housing seals is in FIG. 4 shown.
  • the housing seal 23 and the further housing seal 24 are designed as identical parts, so that the hydraulic medium channel passing through the intermediate housing part 21 and connecting the low-pressure chamber 16 with the medium-pressure chamber 12 has two throttling sections.
  • the diameter of the likewise punched throttle openings 17 is clearly more than 0.4 mm.
  • the throttle-poor through-bore 31 in the intermediate housing part 21 is unchanged compared to the aforementioned exemplary embodiment.
  • FIGS. 5 and 6 Further embodiments of inventive housing seals 23 and 24 are shown.
  • the length of the comparatively small material thickness of the housing seals 23 and 24 corresponds and their throttle characteristic thus resembles that of a viscous iris independent, the throttle opening 17"' limited by a tubular elevation 33 of the housing seal 23
  • the elevation 33 produced in a deep-drawing step and extending into the through-bore 31 by a multiple of the material thickness of the housing seal 23 causes the throttle opening 17 "'to assume the geometry of a viscosity-dependent and laminar-flow nozzle
  • FIGS. 5 and 6 Embodiments shown differ only in that the further housing seal 24 according to either the throttle-poor passage 30 FIG. 3 or the orifice-type throttle opening 17 "connected in series with the throttle opening 17"'in FIG FIG. 4 having.
  • each medium-pressure chamber 12 may also be connected via two or more such hydraulic fluid channels to the associated low-pressure chamber 16. It is also conceivable to associate each of two medium-pressure chambers 12 with two or more low-pressure chambers 16 separated from one another. This applies in a corresponding manner to the alternative embodiments according to the FIGS. 4 to 6 ,
  • vent 32 can be gas bubbles, which pass through the throttle opening 17 from the medium-pressure chamber 12 in the low-pressure chamber 16 during operation of the internal combustion engine, via a running in the upper housing part 22 and opening into the cylinder head 2 vent 32 are deposited in the interior of the cylinder head 2. This also applies to excess hydraulic fluid, in which case the vent opening 32 serves as an overflow.

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

Abstract

The unit (5) has a drive-side master unit (6), a driven-side slave unit, a high-pressure chamber, a controllable hydraulic valve (10), a medium-pressure chamber (12) running into a housing bottom part (20). A throttle opening is formed as a part of a hydraulic medium channel passing via a housing middle part (21). The throttle opening runs into a flat housing seal (23) that is arranged as a separate component either between the bottom part or a housing top part (22) and the middle part. A section of the hydraulic medium channel passing via the middle part exhibits a low-throttle construction.

Description

Die Erfindung betrifft eine Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb. Die Hydraulikeinheit umfasst:

  • ■ zumindest eine antriebseitige Gebereinheit,
  • ■ zumindest eine abtriebseitige Nehmereinheit,
  • ■ zumindest ein ansteuerbares Hydraulikventil,
  • ■ zumindest einen Mitteldruckraum,
  • ■ zumindest einen Hochdruckraum, der im Übertragungssinn zwischen der zugehörigen Gebereinheit und der zugehörigen Nehmereinheit angeordnet und über das zugehörige Hydraulikventil mit dem zugehörigen Mitteldruckraum verbindbar ist,
  • ■ zumindest einen als Hydraulikmittelreservoir dienenden Niederdruckraum, der über eine Drosselöffnung mit dem zugehörigen Mitteldruckraum verbunden ist,
  • ■ und ein Hydraulikgehäuse mit einem Gehäuseunterteil, einem Gehäusezwischenteil und einem Gehäuseoberteil,
    wobei die Gebereinheit, die Nehmereinheit, der Hochdruckraum, das Hydraulikventil und der Mitteldruckraum im Gehäuseunterteil verlaufen, der Niederdruckraum im Gehäuseoberteil ausgebildet ist und die Drosselöffnung Teil eines das Gehäusezwischenteil durchsetzenden Hydraulikmittelkanals ist.
The invention relates to a hydraulic unit for a cylinder head of an internal combustion engine with hydraulically variable gas exchange valve train. The hydraulic unit comprises:
  • At least one drive-side transmitter unit,
  • At least one output-side receiving unit,
  • At least one controllable hydraulic valve,
  • ■ at least one medium-pressure space,
  • At least one high-pressure space, which is arranged in the direction of transmission between the associated transmitter unit and the associated slave unit and can be connected to the associated medium-pressure chamber via the associated hydraulic valve,
  • At least one low-pressure space serving as a hydraulic medium reservoir, which is connected via a throttle opening to the associated medium-pressure space,
  • ■ and a hydraulic housing with a housing lower part, a housing intermediate part and a housing upper part,
    wherein the transmitter unit, the receiver unit, the high-pressure chamber, the hydraulic valve and the medium-pressure chamber run in the lower housing part, the low-pressure chamber is formed in the upper housing part and the throttle opening is part of the housing intermediate part passing through the hydraulic fluid channel.

Hintergrund der ErfindungBackground of the invention

Eine derartige Hydraulikeinheit geht aus der nicht vorveröffentlichten EP 2 060 754 A2 (Stand der Technik nach Art. 54(3) EPÜ) hervor. Bei der dort vorgeschlagenen Hydraulikeinheit sind alle wesentlichen, für die hydraulisch variable Übertragung von Nockenerhebungen auf die Gaswechselventile erforderlichen Bauteile und die Druckräume in einem gemeinsamen Hydraulikgehäuse in Sandwichbauweise zusammengefasst. Das Gehäuseunterteil ist sehr kompakt bauend ausgebildet, und bei dem Gehäusezwischenteil handelt es sich zudem um eine im wesentlichen flache Platte, so dass jeder der Mitteldruckräume auf ein entsprechend kleines Volumen begrenzt ist.Such a hydraulic unit is from the unpublished EP 2 060 754 A2 (State of the art according to Art. 54 (3) EPC). In the hydraulic unit proposed there are all essential, required for the hydraulically variable transmission of cam lobes on the gas exchange valves components and the pressure chambers in a common hydraulic housing in sandwich construction summarized. The lower housing part is formed very compact design, and in the intermediate housing part is also a substantially flat plate, so that each of the intermediate pressure chambers is limited to a correspondingly small volume.

Wie es in der zitierten Druckschrift erläutert ist, kann jedoch ein kleinvolumiger Mitteldruckraum beim Startvorgang der Brennkraftmaschine problematisch sein, insbesondere wenn es sich um einen Startvorgang bei tiefen Außentemperaturen und nach längerem Stillstand der Brennkraftmaschine handelt. Dies liegt darin begründet, dass die Hydraulikmittelversorgung der Brennkraftmaschine während des Startvorgangs noch keinen ausreichenden Hydraulikmittelstrom in den Mitteldruckraum fördert und lediglich das im Mitteldruckraum verbliebene und zudem bei tiefen Temperaturen geschrumpfte Hydraulikmittelvolumen unzureichend groß für ein vollständiges Wiederbefüllen eines dann expandierenden Hochdruckraums ist. Diese Problematik gilt in verstärktem Maße für sich in kurzer Zeitfolge wiederholende Startvorgänge, da in diesem Fall der Hydraulikmittelverbrauch aus dem Mitteldruckraum größer als das von der Hydraulikmittelversorgung der Brennkraftmaschine nachgeförderte Volumen sein kann. Solche Mehrfachstartvorgänge sind beispielsweise für Taxifahrzeuge an Taxiständen typisch.As explained in the cited document, however, a small-volume medium-pressure chamber during the starting process of the internal combustion engine can be problematic, especially if it is a starting operation at low ambient temperatures and after a long period of stoppage of the internal combustion engine. This is due to the fact that the hydraulic fluid supply of the internal combustion engine still does not promote sufficient hydraulic fluid flow into the medium-pressure space during start-up and only the hydraulic fluid volume remaining in the medium-pressure space and shrunk at low temperatures is insufficiently large for a complete refilling of a then-expanding high-pressure space. This problem applies to a greater extent in a short time repetitive starting operations, since in this case the hydraulic fluid consumption from the medium-pressure space can be greater than the nachgeförderte from the hydraulic fluid supply to the internal combustion engine volume. Such multi-start operations are typical, for example, for taxi cabs at taxi stands.

Zur Lösung dieser Problematik wird in der zitierten Druckschrift vorgeschlagen, im Gehäuseoberteil einen als Hydraulikmittelreservoir dienenden Niederdruckraum auszubilden, der über eine Drosselöffnung im Gehäusezwischenteil mit dem Mitteldruckraum verbunden ist. Mit Hilfe des Niederdruckraums wird zum einen das während des Startvorgangs der Brennkraftmaschine erforderliche Hydraulikmittelreservoir für den Mitteldruckraum und mithin für den Hochdruckraum erweitert und zum anderen das Risiko eines Ansaugens von Gasblasen weitestgehend beseitigt. Letzteres ergibt sich durch das Gehäusezwischenteil, das den Niederdruckraum vom Mitteldruckraum separiert, so dass während der Stillstandsphase der Brennkraftmaschine und dabei abkühlendem und folglich schrumpfendem Hydraulikmittel die Bildung von Gasblasen im Mitteldruckraum durch Nachsaugen von Hydraulikmittel aus dem Niederdruckraum verhindert wird.To solve this problem, it is proposed in the cited document to form in the upper housing part serving as a hydraulic fluid reservoir low-pressure chamber, which has a throttle opening in the intermediate housing part with the medium-pressure space connected is. With the help of the low-pressure chamber on the one hand during the starting process of the engine required hydraulic fluid reservoir for the medium-pressure space and thus expanded for the high-pressure chamber and on the other hand eliminates the risk of suction of gas bubbles as far as possible. The latter results from the intermediate housing part, which separates the low-pressure chamber from the medium-pressure chamber, so that during the stoppage phase of the internal combustion engine and thereby cooling and thus shrinking hydraulic fluid, the formation of gas bubbles in the medium-pressure space is prevented by suction of hydraulic fluid from the low pressure chamber.

Als nachteilig hat sich jedoch der Aufwand zur Herstellung einer derartigen Drosselöffnung in Form des nur wenige Zehntelmillimeter betragenden Kleinstdurchmessers einer Stufenbohrung durch das Gehäusezwischenteil herausgestellt. Beispielsweise ist im Falle einer spanend hergestellten Bohrung mit hohem Werkzeugverschleiß oder häufigem Werkzeugausfall zu rechnen, während die Herstellung mittels Laserstrahl zu unerwünscht hohen Form- und Querschnittsabweichungen von der Sollgeometrie der Drosselöffnung führt.However, the expense of producing such a throttle opening in the form of the smallest diameter of a stepped bore amounting to only a few tenths of a millimeter has been found to be disadvantageous due to the housing intermediate part. For example, in the case of a machined bore with high tool wear or frequent tool failure to be expected, while the production by means of laser beam leads to undesirably high shape and cross-sectional deviations of the desired geometry of the throttle opening.

Eine weitere Hydraulikeinheit ist aus DE 10 2006 008 676 A1 bekannt.Another hydraulic unit is off DE 10 2006 008 676 A1 known.

Aufgabe der ErfindungObject of the invention

Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, eine Hydraulikeinheit der eingangs genannten Art so fortzubilden, dass die Drosselöffnung zwischen dem Mitteldruckraum und dem Niederdruckraum mit geringem Aufwand und gleichzeitig möglichst präzise herstellbar ist.The present invention is therefore based on the object, a hydraulic unit of the type mentioned in such a way that the throttle opening between the medium-pressure chamber and the low-pressure chamber with little effort and at the same time as precisely produced.

Zusammenfassung der ErfindungSummary of the invention

Die Lösung dieser Aufgabe ergibt sich aus den kennzeichnenden Merkmalen des Anspruchs 1, während vorteilhafte Weiterbildungen und Ausgestaltungen der Erfindung den Unteransprüchen entnehmbar sind. Demnach ist es vorgesehen, dass die Drosselöffnung in einer Gehäusedichtung verläuft, die als separates Bauteil entweder zwischen dem Gehäuseunterteil oder dem Gehäuseoberteil einerseits und dem Gehäusezwischenteil andererseits angeordnet ist, wobei der das Gehäusezwischenteil durchsetzende Abschnitt des Hydraulikmittelkanals drosselarm ausgebildet ist. Die Verlagerung der Drosselöffnung vom Gehäusezwischenteil in die Gehäusedichtung führt zu einem deutlich geringeren Herstellaufwand, da die Drosselöffnung insbesondere durch Stanzen einer ein- oder mehrlagigen Metalldichtung, wie sie als solche im Zylinderkopfbereich von Brennkraftmaschinen häufig Verwendung findet, präzise und kostengünstig herstellbar ist. Gleichzeitig ist das Gehäusezwischenteil infolge dessen nunmehr entfallender Drosselwirkung deutlich kostengünstiger herstellbar.The solution of this problem arises from the characterizing features of claim 1, while advantageous developments and refinements of the invention are the dependent claims can be removed. Accordingly, it is provided that the throttle opening extends in a housing seal, as a separate Component is arranged either between the lower housing part or the upper housing part on the one hand and the intermediate housing part on the other hand, wherein the intermediate portion of the housing passing through portion of the hydraulic fluid channel is formed throttle-poor. The displacement of the throttle opening from the intermediate housing part in the housing seal leads to a significantly lower production costs, since the throttle opening in particular by punching a single or multi-layer metal seal, as it is often used as such in the cylinder head of internal combustion engines, precise and inexpensive to produce. At the same time, the intermediate housing part is significantly less expensive to produce as a result of its now dropping throttle effect.

In Weiterbildung der Erfindung soll die Gehäusedichtung als Flachdichtung ausgebildet sein und eine röhrenförmige Erhebung aufweisen, welche die Drosselöffnung nach Art einer Düse begrenzt. Die düsenartige Geometrie der Drosselöffnung führt zu einer ausgeprägten Viskositätsabhängigkeit des Hydraulikmittelvolumenstroms derart, dass der zu drosselnde Volumenstrom bei tiefen Temperaturen / hochviskosem Hydraulikmittel deutlich kleiner als bei hohen Temperaturen / niedrigviskosem Hydraulikmittel ist. Diese Drosselcharakteristik ist besonders dann von Vorteil, wenn das Gehäuseoberteil mit einem in den Zylinderkopf mündenden Überlauf versehen ist. Dieser dient nicht nur der Entlüftung des Niederdruckraums, sondern auch der Kühlung der Hydraulikeinheit, indem aufgeheiztes Hydraulikmittel via Niederdruckraum in den Zylinderkopf entweichen und mithin in den gekühlten Hydraulikmittelkreislauf der Brennkraftmaschine zurückgeführt werden kann. Hierbei bewirkt die viskositätsabhängige Drosselwirkung eine bedarfsgerechte Spülung der Hydraulikeinheit, die idealerweise dergestalt ist, dass bei heißem Hydraulikmittel eine größtmögliche Spülung und bei kaltem Hydraulikmittel keine Spülung der Hydraulikeinheit erfolgt.In a further development of the invention, the housing seal should be formed as a flat gasket and have a tubular elevation which limits the throttle opening in the manner of a nozzle. The nozzle-like geometry of the throttle opening leads to a pronounced viscosity dependency of the hydraulic fluid volume flow such that the volume flow to be throttled at low temperatures / high-viscosity hydraulic fluid is significantly smaller than at high temperatures / low-viscosity hydraulic fluid. This throttle characteristic is particularly advantageous when the upper housing part is provided with an opening into the cylinder head overflow. This not only serves to vent the low pressure chamber, but also the cooling of the hydraulic unit by escaping heated hydraulic fluid via low pressure chamber in the cylinder head and thus can be returned to the cooled hydraulic fluid circuit of the engine. Here, the viscosity-dependent throttle effect causes a needs-based flushing of the hydraulic unit, which is ideally such that when hot hydraulic fluid flushing the largest possible and cold hydraulic fluid is carried out no rinsing of the hydraulic unit.

Zweckmäßigerweise ist die Gehäusedichtung zwischen dem "Gehäuseunterteil und dem Gehäusezwischenteil angeordnet, und die Erhebung erstreckt sich in eine Durchgangsbohrung im Gehäusezwischenteil. Durch die so orientierte Erhebung können Gasblasen im Mitteldruckraum bestmöglich in den Niederdruckraum entweichen.The housing seal is expediently arranged between the housing lower part and the housing intermediate part, and the elevation extends into a through-bore in the housing intermediate part Gas bubbles in the medium-pressure space can escape in the best possible way into the low-pressure space.

Außerdem kann eine weitere Gehäusedichtung vorgesehen sein, die ebenfalls als separates Bauteil ausgebildet und zwischen dem Gehäuseunterteil und dem Gehäuseoberteil auf der der Gehäusedichtung abgewandten Seite des Gehäusezwischenteils angeordnet ist. Folglich ist die Hydraulikeinheit mittels separater Gehäusedichtungen im Bereich beider Trennfugen am Gehäusezwischenteil zur Umgebung hin abgedichtet.In addition, a further housing seal may be provided, which is likewise designed as a separate component and is arranged between the lower housing part and the upper housing part on the side facing away from the housing seal of the intermediate housing part. Consequently, the hydraulic unit is sealed by means of separate housing seals in the region of both joints on the intermediate housing part to the environment.

Diese Gehäusedichtungen können einerseits dahingehend voneinander verschieden ausgebildet sein, dass der die weitere Gehäusedichtung durchsetzende Abschnitt des Hydraulikmittelkanals drosselarm ausgebildet ist. Mit anderen Worten beschränkt sich die Funktion der weiteren Gehäusedichtung in diesem Fall auf die Abdichtung der Hydraulikeinheit zur Umgebung hin.On the one hand, these housing seals may be formed differently from one another so that the section of the hydraulic fluid channel which passes through the further housing seal is of low-throttle design. In other words, the function of the further housing seal in this case is limited to the sealing of the hydraulic unit to the environment.

Andererseits kann es sich bei der Gehäusedichtung und der weiteren Gehäusedichtung aber auch um Gleichteile handeln. Durch entsprechende Stückzahleffekte sind weiterhin verringerte Herstellkosten zu erwarten. Aufgrund der dann zweifachen Drosselwirkung besteht zudem die Möglichkeit, die Drosselöffnungen mit relativ großem Querschnitt zugunsten weiterhin verbesserter Herstellbarkeit auszuführen.On the other hand, the housing seal and the further housing seal can also be identical parts. Due to corresponding unit-price effects, further reduced production costs are to be expected. Due to the then double throttle effect is also possible to run the throttle openings with a relatively large cross-section in favor of further improved manufacturability.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschreibung und aus den Zeichnungen, in denen Ausführungsbeispiele der Erfindung dargestellt sind. Soweit nicht anders erwähnt, sind dabei gleiche oder funktionsgleiche Merkmale oder Bauteile mit gleichen Bezugszahlen versehen. Es zeigen:

Figur 1
eine schematische Darstellung eines hydraulisch variablen Gaswech- selventiltriebs;
Figur 2
eine erfindungsgemäße Hydraulikeinheit in perspektivischer und teil- weise explodierter Schnittdarstellung;
Figur 3
die Ansicht A gemäß Figur 2 mit zwei voneinander verschiedenen Gehäusedichtungen, wobei die Drosselöffnung blendenartig ausgebil- det ist;
Figur 4
die Ansicht A gemäß Figur 2 mit zwei identischen Gehäusedichtun- gen, wobei die Drosselöffnungen blendenartig ausgebildet sind;
Figur 5
die Ansicht A gemäß Figur 2 mit zwei Gehäusedichtungen, wobei die Drosselöffnung düsenartig und der Durchtritt in der weiteren Gehäu- sedichtung drosselarm ausgebildet sind, und
Figur 5
die Ansicht A gemäß Figur 2 mit zwei Gehäusedichtungen, wobei die Drosselöffnung düsenartig und der Durchtritt in der weiteren Gehäu- sedichtung drosselnd ausgebildet sind.
Further features of the invention will become apparent from the following description and from the drawings, in which embodiments of the invention are shown. Unless otherwise stated, the same or functionally identical features or components are provided with the same reference numbers. Show it:
FIG. 1
a schematic representation of a hydraulically variable gas exchange selventiltriebs;
FIG. 2
a hydraulic unit according to the invention in a perspective and partially exploded sectional view;
FIG. 3
the view A according to FIG. 2 with two mutually different housing seals, wherein the throttle opening is formed like an iris;
FIG. 4
the view A according to FIG. 2 with two identical Gehäusedichtun- gene, wherein the throttle openings are formed like an orifice;
FIG. 5
the view A according to FIG. 2 with two housing seals, wherein the throttle opening nozzle-like and the passage in the further housing seal are formed throttle-poor, and
FIG. 5
the view A according to FIG. 2 with two housing seals, the throttle opening being nozzle-shaped and the passage in the further housing seal being throttled.

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

In Figur 1 ist der prinzipielle Aufbau eines hydraulisch variablen Gaswechselventiltriebs 1 schematisch offenbart. Dargestellt ist ein für das Verständnis der Erfindung wesentlicher Ausschnitt eines Zylinderkopfs 2 einer Brennkraftmaschine mit einem Nocken 3 einer Nockenwelle und einem in Schließrichtung federkraftbeaufschlagten Gaswechselventil 4. Die Variabilität des Gaswechselventiltriebs 1 wird mittels einer zwischen dem Nocken 3 und dem Gaswechselventil 4 angeordneten Hydraulikeinheit 5 erzeugt, die folgende Komponenten umfasst:

  • ■ eine antriebseitige Gebereinheit 6, hier in Form eines vom Nocken 3 angetriebenen Pumpenstößels 7,
  • ■ eine abtriebseitige Nehmereinheit 8, hier in Form eines das Gaswechselventil 4 unmittelbar betätigenden Nehmerkolbens 9,
  • ein ansteuerbares Hydraulikventil 10, hier in Form eines elektromagnetischen 2-2-Wege-Schaltventils,
  • ■ einen zwischen der Gebereinheit 6 und der Nehmereinheit 8 verlaufenden Hochdruckraum 11, aus dem bei geöffnetem Hydraulikventil 10 Hydraulikmittel in einen Mitteldruckraum 12 abströmen kann,
  • ■ ein an den Mitteldruckraum 12 angeschlossener Druckspeicher 13 mit einem federkraftbeaufschlagten Ausgleichskolben 14,
  • ■ ein in Richtung des Mitteldruckraums 12 öffnendes Rückschlagventil 15, über das die Hydraulikeinheit 5 an den Hydraulikmittelkreislauf der Brennkraftmaschine angeschlossen ist, und
  • ■ einen als Hydraulikmittelreservoir dienenden Niederdruckraum 16, der über eine Drosselöffnung 17 in einer den Niederdruckraum 16 vom Mitteldruckraum 12 separierenden Trennwand 18 mit dem Mitteldruckraum 12 verbunden ist.
In FIG. 1 the basic structure of a hydraulically variable gas exchange valve drive 1 is schematically disclosed. Shown is a section of a cylinder head 2 of an internal combustion engine with a cam 3 of a camshaft and a spring-loaded gas exchange valve 4 which is essential for understanding the invention. The variability of the gas exchange valve drive 1 is generated by means of a hydraulic unit 5 arranged between the cam 3 and the gas exchange valve 4. the following components include:
  • A drive-side transmitter unit 6, here in the form of a pump tappet 7 driven by the cam 3,
  • ■ an output side slave unit 8, here in the form of a gas piston valve 4 directly actuated slave piston 9,
  • ■ a controllable hydraulic valve 10, here in the form of an electromagnetic 2-2-way switching valve,
  • ■ a high-pressure space 11 extending between the transmitter unit 6 and the receiver unit 8, from which hydraulic fluid can flow into an intermediate-pressure space 12 when the hydraulic valve 10 is open,
  • ■ a pressure accumulator 13 connected to the medium pressure chamber 12 with a compensating piston 14 which is acted upon by a spring force,
  • ■ in the direction of the medium-pressure chamber 12 opening check valve 15, via which the hydraulic unit 5 is connected to the hydraulic fluid circuit of the internal combustion engine, and
  • ■ a low-pressure space 16 serving as a hydraulic medium reservoir, which is connected to the medium-pressure space 12 via a throttle opening 17 in a partition wall 18 separating the low-pressure space 16 from the medium-pressure space 12.

Die an sich bekannte Funktionsweise des hydraulischen Gaswechselventiltriebs 1 lässt sich dahingehend zusammenfassen, dass der Hochdruckraum 11 zwischen der Gebereinheit 6 und der Nehmereinheit 8 als hydraulisches Gestänge wirkt, wobei das - bei Vernachlässigung von Leckagen - proportional zum Hub des Nockens 3 vom Pumpenstößel 7 verdrängte Hydraulikvolumen in Abhängigkeit des Öffnungszeitpunkts und der Öffnungsdauer des Hydraulikventils 10 in ein erstes, den Nehmerkolben 9 beaufschlagendes Teilvolumen und in ein zweites, in den Mitteldruckraum 12 einschließlich Druckspeicher 13 abströmendes Teilvolumen aufgesplittet wird. Hierdurch sind die Hubübertragung des Pumpenstößels 7 auf den Nehmerkolben 9 und mithin nicht nur die Steuerzeiten, sondern auch die Hubhöhe des Gaswechselventils 4 vollvariabel einstellbar.The known manner of operation of the hydraulic gas exchange valve drive 1 can be summarized to the effect that the high pressure chamber 11 between the transmitter unit 6 and the slave unit 8 acts as a hydraulic linkage, which - neglecting leaks - proportional to the stroke of the cam 3 displaced by the pump plunger 7 hydraulic volume as a function of the opening time and the opening duration of the hydraulic valve 10 in a first, the slave piston 9 acting sub-volume and in a second, in the medium pressure chamber 12 including pressure accumulator 13 effluent partial volume is split. As a result, the stroke transmission of the pump tappet 7 to the slave piston 9 and therefore not only the timing, but also the lifting height of the gas exchange valve 4 are fully variable adjustable.

Die in Figur 2 quer geschnitten dargestellte Hydraulikeinheit 5 für eine 4-Zylinder-Reihenmaschine weist als weiteren wesentlichen Bestandteil ein gemeinsames Hydraulikgehäuse 19 auf, so dass die Hydraulikeinheit 5 als vormontierte und gegebenenfalls bereits mit Hydraulikmittel befüllte Baueinheit in den Zylinderkopf 2 der Brennkraftmaschine montiert werden kann. Das in Sandwichbauweise zusammengesetzte Hydraulikgehäuse 19 besteht aus einem Gehäuseunterteil 20, einem Gehäusezwischenteil 21 und einem Gehäuseoberteil 22. Zur Abdichtung der Trennfuge zwischen Gehäuseunterteil 20 und Gehäusezwischenteil 21 verläuft eine Gehäusedichtung 23, und zur Abdichtung der Trennfuge zwischen Gehäusezwischenteil 21 und Gehäuseoberteil 22 verläuft eine weitere Gehäusedichtung 24. Bei beiden Dichtungen 23, 24 handelt es sich um separate Bauteile in Form von einlagigen Metalldichtungen. Die Gehäuseteile 20, 21, 22 sind an diversen Verschraubungspunkten 25 hydraulisch dichtend miteinander verschraubt. Zum Befestigen der gesamten Hydraulikeinheit 5 im Zylinderkopf 2 der Brennkraftmaschine weist das Gehäuseunterteil 20 separate Verschraubungspunkte 26 auf.In the FIG. 2 Cross-section shown hydraulic unit 5 for a 4-cylinder in-line engine has as a further essential part of a common Hydraulic housing 19, so that the hydraulic unit 5 can be mounted as a preassembled and possibly already filled with hydraulic fluid assembly in the cylinder head 2 of the internal combustion engine. The composite in sandwich construction hydraulic housing 19 consists of a lower housing part 20, a housing intermediate part 21 and a housing upper part 22. To seal the parting line between the housing base 20 and housing intermediate part 21 extends a housing seal 23, and for sealing the parting line between the housing intermediate part 21 and upper housing part 22 extends a further housing seal 24. Both seals 23, 24 are separate components in the form of single-layer metal seals. The housing parts 20, 21, 22 are screwed together hydraulically sealingly at various screwing points 25. For fixing the entire hydraulic unit 5 in the cylinder head 2 of the internal combustion engine, the lower housing part 20 separate Verschraubungspunkte 26 on.

Die vier im Gehäuseunterteil 20 verlaufenden Gebereinheiten 6 umfassen jeweils den in Rückhubrichtung federkraftbeaufschlagten Pumpenstößel 7, der von einem hier nicht dargestellten, nockenbetätigten Schlepphebel angetrieben wird. Die schwenkbewegliche Lagerung der Schlepphebel erfolgt mittels Abstützelementen 27, die ebenfalls im Gehäuseunterteil 20 aufgenommen sind. Vom Gehäusezwischenteil 21 abgehende Bügel 28, dienen als Verliersicherung für die Schlepphebel bei nicht im Zylinderkopf 2 montierter Hydraulikeinheit 5. Diese ist weiterhin so ausgebildet, dass jede der Gebereinheiten 6 mit zwei der im Gehäuseunterteil 20 verlaufenden Nehmereinheiten 8 (siehe Figur 1) zusammenwirkt. Mit anderen Worten wird für jedes Paar gleichwirkender Gaswechselventile 4, d.h. Einlassventile oder Auslassventile eines Zylinders der Brennkraftmaschine, nur ein Nocken 3 und eine Gebereinheit 6 benötigt, wobei das vom Pumpenstößel 7 verdrängte Hydraulikvolumen beide Nehmereinheiten 8 gleichzeitig beaufschlagt.The four transmitter units 6 extending in the housing lower part 20 each include the pump plunger 7, which is spring-loaded in the return stroke direction and which is driven by a cam-operated drag lever, not shown here. The pivotable mounting of the drag levers takes place by means of support elements 27, which are also accommodated in the lower housing part 20. From the intermediate housing part 21 outgoing bracket 28, serve as a captive for the drag lever with not mounted in the cylinder head 2 hydraulic unit 5. This is further designed so that each of the transmitter units 6 with two extending in the housing base 20 slave units 8 (see FIG. 1 ) cooperates. In other words, only one cam 3 and one transmitter unit 6 are required for each pair of identical gas exchange valves 4, ie intake valves or exhaust valves of a cylinder of the internal combustion engine, wherein the hydraulic volume displaced by the pump tappet 7 simultaneously acts on both slave units 8.

Auf der den Gebereinheiten 6 gegenüber liegenden Seite der Hydraulikeinheit 5 sind die jeweils einer Gebereinheit 6 und den beiden Nehmereinheiten 8 zugeordneten Hydraulikventile 10 mit elektrischen Anschlusssteckern 29 zu erkennen. Die im stromlosen Zustand den Mitteldruckraum 12 mit dem Hochdruckraum 11 (siehe Figur 1) verbindenden Hydraulikventile 10 sind auf an sich bekannte und hier nicht näher dargestellte Weise in Ventilaufnahmen im Gehäuseunterteil 20 befestigt. Weiterhin erkennbar ist der an den Mitteldruckraum 12 angeschlossene Druckspeicher 13 mit dem federkraftbeaufschlagten Ausgleichskolben 14.On the side facing the transmitter units 6 side of the hydraulic unit 5, the respective one encoder unit 6 and the two slave units 8 associated hydraulic valves 10 can be seen with electrical connectors 29. In the de-energized state, the medium-pressure chamber 12 with the high-pressure chamber 11 (see FIG. 1 ) connecting hydraulic valves 10 are fixed in a known per se and not shown here in valve receptacles in the housing base 20. Further recognizable is the pressure accumulator 13 connected to the medium-pressure chamber 12 with the compensating piston 14 which is acted on by spring force.

Die jeweils als Hydraulikmittelreservoir für den zugehörigen Mitteldruckraum 12 dienenden Niederdruckräume 16 sind durch Auswölbungen im Gehäuseoberteil 22 gebildet, das im Tiefziehverfahren aus Stahlblech hergestellt ist. Wie es aus Figur 3 als vergrößerte Ansicht A deutlich hervorgeht, sind der Niederdruckraum 16 und der Mitteldruckraum 12 über einen Hydraulikmittelkanal miteinander verbunden, welcher durch die Gehäusedichtungen 23, 24 und das Gehäusezwischenteil 21 verläuft. Als Trennwand 18 gemäß Figur 1 dient die zwischen Gehäuseunterteil 20 und Gehäusezwischenteil 21 eingelegte Gehäusedichtung 23 mit gestanzter Drosselöffnung 17', die einen Durchmesser von etwa 0,4mm aufweist. Die weitere Gehäusedichtung 24 zwischen Gehäusezwischenteil 21 und Gehäuseoberteil 22 unterscheidet sich von der Gehäusedichtung 23 dadurch, dass deren Durchtritt 30 ebenso wie die Durchgangsbohrung 31 im Gehäusezwischenteil 21 ein Vielfaches des Querschnitts der Drosselöffnung 17' hat. Der Durchtritt 30 und die einfach herzustellende Durchgangsbohrung 31 stellen somit drosselarme Abschnitte des Hydraulikmittelkanals dar.Each serving as a hydraulic fluid reservoir for the associated medium-pressure chamber 12 low-pressure spaces 16 are formed by bulges in the upper housing part 22, which is made by deep-drawing of sheet steel. Like it out FIG. 3 as an enlarged view A clearly shows, the low-pressure chamber 16 and the medium-pressure chamber 12 are connected to each other via a hydraulic fluid channel, which extends through the housing seals 23, 24 and the intermediate housing part 21. As a partition 18 according to FIG. 1 is used between the housing base 20 and housing intermediate part 21 inserted housing seal 23 with punched throttle opening 17 ', which has a diameter of about 0.4 mm. The further housing seal 24 between housing intermediate part 21 and housing upper part 22 differs from the housing seal 23 in that its passage 30 as well as the through bore 31 in the housing intermediate part 21 has a multiple of the cross section of the throttle opening 17 '. The passage 30 and the easy-to-produce through-hole 31 thus represent throttle-poor portions of the hydraulic fluid channel.

Eine zu Figur 3 alternative Ausgestaltung der Gehäusedichtungen ist in Figur 4 dargestellt. Die Gehäusedichtung 23 und die weitere Gehäusedichtung 24 sind in diesem Fall als Gleichteile ausgebildet, so dass der das Gehäusezwischenteil 21 durchsetzende und den Niederdruckraum 16 mit dem Mitteldruckraum 12 verbindende Hydraulikmittelkanal zwei drosselnde Abschnitte aufweist. Um dabei eine gleiche Drosselwirkung wie bei dem Ausführungsbeispiel nach Figur 3 zu erzielen, beträgt der Durchmesser der ebenfalls gestanzten Drosselöffnungen 17" deutlich mehr als 0,4mm. Die drosselarme Durchgangsbohrung 31 im Gehäusezwischenteil 21 ist gegenüber dem vorgenannten Ausführungsbeispiel unverändert.One too FIG. 3 alternative embodiment of the housing seals is in FIG. 4 shown. In this case, the housing seal 23 and the further housing seal 24 are designed as identical parts, so that the hydraulic medium channel passing through the intermediate housing part 21 and connecting the low-pressure chamber 16 with the medium-pressure chamber 12 has two throttling sections. In order to the same throttle effect as in the embodiment according to FIG. 3 The diameter of the likewise punched throttle openings 17 "is clearly more than 0.4 mm. The throttle-poor through-bore 31 in the intermediate housing part 21 is unchanged compared to the aforementioned exemplary embodiment.

In den Figuren 5 und 6 sind weitere Ausgestaltungen erfindungsgemäßer Gehäusedichtungen 23 und 24 dargestellt. Im Gegensatz zu den lediglich ausgestanzten Drosselöffnungen 17', 17", deren Länge der vergleichsweise geringen Materialstärke der Gehäusedichtungen 23 und 24 entspricht und deren Drosselcharakteristik folglich derjenigen einer viskositätsunabhängigen Blende ähnelt, wird die Drosselöffnung 17"' durch eine röhrenförmige Erhebung 33 der Gehäusedichtung 23 begrenzt. Die in einem Tiefziehschritt hergestellte und sich mit einem Mehrfachen der Materialstärke der Gehäusedichtung 23 in die Durchgangsbohrung 31 erstreckende Erhebung 33 bewirkt, dass die Drosselöffnung 17"' die Geometrie einer viskositätsabhängigen und hier laminar durchströmten Düse annimmt. Die in den Figuren 5 und 6 gezeigten Ausgestaltungen unterscheiden sich lediglich dadurch, dass die weitere Gehäusedichtung 24 entweder den drosselarmen Durchtritt 30 gemäß Figur 3 oder die mit der Drosselöffnung 17"' in Reihe geschaltete blendenartige Drosselöffnung 17" gemäß Figur 4 aufweist.In the FIGS. 5 and 6 Further embodiments of inventive housing seals 23 and 24 are shown. In contrast to the merely punched out throttle openings 17 ', 17 ", the length of the comparatively small material thickness of the housing seals 23 and 24 corresponds and their throttle characteristic thus resembles that of a viscous iris independent, the throttle opening 17"' limited by a tubular elevation 33 of the housing seal 23 , The elevation 33 produced in a deep-drawing step and extending into the through-bore 31 by a multiple of the material thickness of the housing seal 23 causes the throttle opening 17 "'to assume the geometry of a viscosity-dependent and laminar-flow nozzle FIGS. 5 and 6 Embodiments shown differ only in that the further housing seal 24 according to either the throttle-poor passage 30 FIG. 3 or the orifice-type throttle opening 17 "connected in series with the throttle opening 17"'in FIG FIG. 4 having.

Obwohl in den Figuren 2 und 3 nur ein Hydraulikmittelkanal mit Drosselöffnung 17' gezeigt ist, kann jeder Mitteldruckraum 12 auch über zwei oder mehrere derartiger Hydraulikmittelkanäle an den zugehörigen Niederdruckraum 16 angeschlossen sein. Ebenfalls ist es denkbar, jedem Mitteldruckraum 12 zwei oder mehr voneinander separierte Niederdruckräume 16 zuzuordnen. Dies gilt in entsprechender Weise auch für die alternativen Ausgestaltungen gemäß den Figuren 4 bis 6.Although in the Figures 2 and 3 only one hydraulic fluid channel with throttle opening 17 'is shown, each medium-pressure chamber 12 may also be connected via two or more such hydraulic fluid channels to the associated low-pressure chamber 16. It is also conceivable to associate each of two medium-pressure chambers 12 with two or more low-pressure chambers 16 separated from one another. This applies in a corresponding manner to the alternative embodiments according to the FIGS. 4 to 6 ,

Wie in den Figuren 1 und 2 ersichtlich, können Gasblasen, die während des Betriebs der Brennkraftmaschine über die Drosselöffnung 17 aus dem Mitteldruckraum 12 in den Niederdruckraum 16 gelangen, über eine im Gehäuseoberteil 22 verlaufende und in den Zylinderkopf 2 mündende Entlüftungsöffnung 32 in das Innere des Zylinderkopfs 2 abgeschieden werden. Dies betrifft auch überschüssiges Hydraulikmittel, wobei dann die Entlüftungsöffnung 32 als Überlauf dient.As in the FIGS. 1 and 2 can be gas bubbles, which pass through the throttle opening 17 from the medium-pressure chamber 12 in the low-pressure chamber 16 during operation of the internal combustion engine, via a running in the upper housing part 22 and opening into the cylinder head 2 vent 32 are deposited in the interior of the cylinder head 2. This also applies to excess hydraulic fluid, in which case the vent opening 32 serves as an overflow.

Liste der BezugszahlenList of reference numbers

11
GaswechselventiltriebGas exchange valve train
22
Zylinderkopfcylinder head
33
Nockencam
44
GaswechselventilGas exchange valve
55
Hydraulikeinheithydraulic unit
66
Gebereinheittransmitter unit
77
Pumpenstößelpump plunger
88th
Nehmereinheitreceiver unit
99
Nehmerkolbenslave piston
1010
Hydraulikventilhydraulic valve
1111
HochdruckraumHigh-pressure chamber
1212
MitteldruckraumMedium-pressure chamber
1313
Druckspeicheraccumulator
1414
Ausgleichskolbenbalance piston
1515
Rückschlagventilcheck valve
1616
NiederdruckraumLow-pressure chamber
1717
Drosselöffnungthrottle opening
1818
Trennwandpartition wall
1919
Hydraulikgehäusehydraulic housing
2020
GehäuseunterteilHousing bottom
2121
GehäusezwischenteilIntermediate housing part
2222
GehäuseoberteilHousing top
2323
Gehäusedichtunghousing seal
2424
weitere Gehäusedichtungadditional housing seal
2525
Verschraubungspunktscrew fixing
2626
Verschraubungspunktscrew fixing
2727
Abstützelementsupporting
2828
Bügelhanger
2929
Anschlussstecker des HydraulikventilsConnector of the hydraulic valve
3030
Durchtritt in der weiteren GehäusedichtungPassage in the other housing seal
3131
Durchgangsbohrung im GehäusezwischenteilThrough hole in the intermediate housing part
3232
Entlüftungsöffnungvent
3333
Erhebungsurvey

Claims (7)

  1. Hydraulic unit (5) for a cylinder head (2) of an internal combustion engine having a hydraulically variable gas-exchange valve timing mechanism (1), comprising
    ■ at least one drive-side transmitter unit (6),
    ■ at least one output-side receiver unit (8),
    ■ at least one actuable hydraulic valve (10),
    ■ at least one medium-pressure space (12),
    ■ at least one high-pressure space (11) which is arranged in the transmission direction between the associated transmitter unit (6) and the associated receiver unit (8) and can be connected via the associated hydraulic valve (10) to the associated medium-pressure space (12),
    ■ at least one low-pressure space (16) which is connected via a throttle opening (17, 17', 17'', 17"') to the associated medium-pressure space (12),
    ■ and a hydraulic housing (19) having a lower housing part (20) and an intermediate housing part (21),
    the throttle opening (17, 17', 17", 17"') being part of a hydraulic-medium channel which penetrates the intermediate housing part (21), and the transmitter unit (6), the receiver unit (8), the high-pressure space (11), the hydraulic valve (10) and the medium-pressure space (12) extending in the lower housing part (20), characterized in that the hydraulic housing (19) has an upper housing part (22), the low-pressure space (16) is formed in the upper housing part (22) and serves as hydraulic-medium reservoir, and the throttle opening (17, 17', 17", 17"') extends in a housing seal (23) which is arranged as a separate component either between the lower housing part (20) or the upper housing part (22) on one side and the intermediate housing part (21) on the other side, that section of the hydraulic-medium channel which penetrates the intermediate housing part (21) being configured with a low throttling action.
  2. Hydraulic unit (5) according to Claim 1, characterized in that the housing seal (23) is configured as a flat seal and has a tubular elevation (33) which delimits the throttle opening (17"') in the manner of a nozzle.
  3. Hydraulic unit (5) according to Claim 2, characterized in that the housing seal (23) is arranged between the lower housing part (20) and the intermediate housing part (21), the elevation (33) extending into a through hole (31) in the intermediate housing part (21).
  4. Hydraulic unit (5) according to Claim 1, characterized in that a further housing seal (24) is provided which is arranged as a separate component between the lower housing part (20) and the upper housing part (22) on that side of the intermediate housing part (21) which faces away from the housing seal (23).
  5. Hydraulic unit (5) according to Claim 4, characterized in that the housing seal (23) and the further housing seal (24) are configured differently from one another, that section of the hydraulic-medium channel which penetrates the further housing seal (24) being configured with a low throttling action.
  6. Hydraulic unit (5) according to Claim 4, characterized in that the housing seal (23) and the further seal (24) are identical parts.
  7. Hydraulic unit (5) according to Claim 1, characterized in that the housing seal (23) is a single-layer or multiple-layer metal seal.
EP20100154527 2009-03-05 2010-02-24 Hydraulic unit for a cylinder head of a combustion engine with hydraulically variable gas exchange valve drive Not-in-force EP2226476B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200910011982 DE102009011982A1 (en) 2009-03-05 2009-03-05 Hydraulic unit for a cylinder head of an internal combustion engine with hydraulically variable gas exchange valve drive

Publications (2)

Publication Number Publication Date
EP2226476A1 EP2226476A1 (en) 2010-09-08
EP2226476B1 true EP2226476B1 (en) 2011-12-07

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US (1) US8210140B2 (en)
EP (1) EP2226476B1 (en)
AT (1) ATE536466T1 (en)
DE (1) DE102009011982A1 (en)

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CH705960A1 (en) * 2012-01-04 2013-07-15 Liebherr Machines Bulle Sa Hydraulic system with temperature-dependent hydraulic fluid leakage.
GB2553120B (en) * 2016-08-24 2019-12-25 Jaguar Land Rover Ltd Variable valve lift system with a diffusing system
DE102016219227A1 (en) * 2016-10-05 2018-04-05 Schaeffler Technologies AG & Co. KG Gas exchange valve drive with a damper chamber connected to a pressure chamber via a throttle

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US6439176B1 (en) * 2001-03-05 2002-08-27 Delphi Technologies, Inc. Control system for deactivation of valves in an internal combustion engine
ITTO20010269A1 (en) * 2001-03-23 2002-09-23 Fiat Ricerche INTERNAL COMBUSTION ENGINE, WITH HYDRAULIC VARIABLE VALVE OPERATION SYSTEM, AND MEANS OF COMPENSATION OF VOLUME VARIATIONS
US6644265B2 (en) * 2002-04-09 2003-11-11 Eaton Corporation Electro-hydraulic manifold assembly and method of making same for controlling de-activation of combustion chamber valves in a multicylinder engine
CN100560968C (en) * 2004-08-20 2009-11-18 菲特尔莫古密封系统布莱藤有限公司 The cylinder head protecting casing that is used for cylinder head of internal combustion engine
DE102006008676A1 (en) 2006-02-24 2007-08-30 Schaeffler Kg Cylinder head for internal combustion engine of vehicle, has filling device for initial filling of pressure discharge chamber and/or pressure chamber with hydraulic medium, where device is formed at housing
DE102007054376A1 (en) 2007-11-14 2009-05-20 Schaeffler Kg Hydraulic unit for a cylinder head of an internal combustion engine with hydraulically variable valve train

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US20100224152A1 (en) 2010-09-09
EP2226476A1 (en) 2010-09-08
DE102009011982A1 (en) 2010-09-09
US8210140B2 (en) 2012-07-03
ATE536466T1 (en) 2011-12-15

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