EP3519683A1 - Internal combustion engine with a hydraulically variable gas exchange valve train - Google Patents

Internal combustion engine with a hydraulically variable gas exchange valve train

Info

Publication number
EP3519683A1
EP3519683A1 EP17787318.9A EP17787318A EP3519683A1 EP 3519683 A1 EP3519683 A1 EP 3519683A1 EP 17787318 A EP17787318 A EP 17787318A EP 3519683 A1 EP3519683 A1 EP 3519683A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
housing
internal combustion
combustion engine
chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP17787318.9A
Other languages
German (de)
French (fr)
Other versions
EP3519683B1 (en
Inventor
Steffen Pfeiffer
Philipp Galster
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP3519683A1 publication Critical patent/EP3519683A1/en
Application granted granted Critical
Publication of EP3519683B1 publication Critical patent/EP3519683B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-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
    • F01L9/12—Valve-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
    • F01L9/14—Valve-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
    • 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
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/06—Valve members or valve-seats with means for guiding or deflecting the medium controlled thereby, e.g. producing a rotary motion of the drawn-in cylinder charge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-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
    • F01L9/12—Valve-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
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-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
    • F01L1/344—Valve-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
    • F01L1/3442—Valve-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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to an internal combustion engine with hydraulically variable gas exchange valve drive, comprising:
  • a hydraulic housing having a pressure chamber, a pressure relief chamber and a venting channel, the pressure chamber, the pressure relief chamber and the venting channel being hydraulically connected to one another,
  • a master piston guided in the hydraulic housing, which is driven on the outside of the housing by a cam and which delimits the pressure chamber on the housing side,
  • the generic DE 10 2013 213 695 A1 shows an internal combustion engine with a fully variable hydraulic valve control. This is formed by a structural unit which is mounted on the cylinder head of the internal combustion engine and whose hydraulic chambers - in the direction of gravity - vent down into the cylinder head.
  • the operational venting of the hydraulic system causes the entrained air bubbles carried by the hydraulic medium in the vicinity of the hydraulic housing and thus prevents air in excessive amount in the pressure chamber and there affects the required for the hydraulic gas exchange valve stiffness keit the hydraulic fluid in an inadmissible height.
  • the vent promotes the leakage of hydraulic fluid from the hydraulic housing when the engine is turned off. Because the cooling and shrinking volume of hydraulic fluid creates negative pressure in the hydraulic raulik basic, which is compensated for ingestion of air via vent channel. During this pressure equalization, gravity will cause the hydraulic chambers to deflate through the guide gap between the slave piston and the hydraulic housing in its vicinity.
  • EP 2 060 754 A2 proposes a hydraulic unit with an additional low-pressure space which communicates with the interior of the cylinder head via a geodetically highly positioned housing opening and via a geodetically deeply positioned throttle point with the pressure relief space for the purpose of venting.
  • the low-pressure chamber is an extended hydraulic reservoir, which supplies the pressure chamber during the starting process of the internal combustion engine with sufficiently air-free hydraulic fluid.
  • venting against the direction of gravity on the upper side of the hydraulic housing requires a cylinder head cover, which seals the cylinder head with the hydraulic housing to the environment, and thus an additional component.
  • the present invention has the object to further develop an internal combustion engine of the type mentioned in that the hydraulic leakage from the hydraulic housing is reduced to such an extent that the hydraulic fluid in the pressure chamber does not fall below a critical for the start process level even after prolonged downtime of the engine ,
  • the venting channel to open in a hydraulic reservoir wherein the channel mouth with respect to the direction of gravity is below the normal level of the hydraulic reservoir.
  • the term ' normal level ' is to be understood as meaning the level which, in the steady state, shortly after switching off the fuel adjusting the hydraulic motor in the hydraulic reservoir, wherein the internal combustion engine is not or at most insignificantly inclined with respect to their installation position.
  • the channel opening "dipping" in the hydraulic medium prevents air from being sucked back into the pressure relief chamber via the venting channel when the internal combustion engine is at a standstill and due to the cooling down of the hydraulic medium volume This condition extends over a sufficiently long period of time and at least until the level, if applicable of the hydraulic reservoir has dropped due to the cooling volume shrinkage of the hydraulic fluid from the hydraulic housing under the channel mouth.
  • the hydraulic reservoir open to the surroundings of the hydraulic housing can be formed either on the hydraulic housing itself or through a local depression or trough shape of a component or section of the cylinder head or of the engine block of the internal combustion engine.
  • the channel mouth with respect to the direction of gravity should run as deep as possible and concretely below the boundary of the pressure chamber from the slave piston.
  • the geodätician height difference between the (retracted in the hydraulic housing) slave piston and the channel mouth directly affects the negative pressure, which forms when the engine and shrinking hydraulic fluid against the environment of the hydraulic housing and counteracts the gravitational leakage of hydraulic fluid from the hydraulic housing.
  • the channel mouth is inclined with respect to the direction of gravity, i. geodetic always below the level of the hydraulic reservoir. This condition assumes that the hydraulic reservoir can be made sufficiently voluminous in view of the temperature and leakage-reducing hydraulic volume in the hydraulic housing.
  • the volume of the hydraulic reservoir is constructively limited such that a drop in the reservoir level below the channel mouth and consequently the suck back of air are unavoidable.
  • the downtime of the internal combustion engine can be significantly extended until it reaches the critical level in the pressure chamber that the vent channel at least locally has a dimensioned so large that air bubbles can ascend therein without pushing the overlying hydraulic or oil column in front of him and to displace into the pressure relief chamber.
  • the cross-section is to be dimensioned so that the air sucked back rises in the stationary oil column, so that the remaining oil column virtually closes the channel mouth again and maintains the leakage-inhibiting negative pressure in the hydraulic housing.
  • the venting channel in the case of an oil having the viscosity index 0W20 and in the case of a circular first pipe section, the venting channel must have a pipe inside diameter of at least 6 mm. Particularly good and robust results were achieved with the tube inner diameter of about 8 mm.
  • the circular shape of the vent channel can have manufacturing advantages. Nevertheless, other cross-sectional shapes are possible, as long as the rising of the air without displacing the overlying oil column is possible.
  • the channel mouth should be formed by a circular second pipe section, which is followed by (abrupt or gradual) reduction of the tube outer diameter of the first pipe section. This structural design of the vent channel with the diameter-stepped pipe sections may be required if the surface of the hydraulic reservoir is too small to accommodate the relatively large diameter of the first pipe section.
  • the venting channel is expediently formed by a venting tube fastened in the hydraulic housing and preferably screwed in, the first and possibly the second tubular section being parts of the venting tube.
  • Figure 1 a the first embodiment with a stepped in diameter vent passage
  • Figure 1 b in an enlarged detail of the channel mouth and the hydraulic reservoir of the first embodiment
  • Figure 2 shows the second embodiment with a comparatively low-lying
  • Figure 3 shows the third embodiment with a permanently immersed in the hydraulic reservoir channel mouth.
  • FIG 1 a shows schematically the essential for understanding the invention section of an internal combustion engine with hydraulically variable Gas
  • Gas Shown is a cylinder head 1 with two similar and spring-loaded in the closing direction gas exchange valves 2 per cylinder and associated cam 3 of a camshaft.
  • the variability of the gas exchange valve drive is generated in a known manner by means of a arranged between the cam 3 and the gas exchange valves 2 hydraulic unit.
  • This comprises a mounted in the cylinder head 1 hydraulic housing 4, in which each cylinder a pressure chamber 5 and a pressure relief chamber 6 formed and a master piston 7 are guided outside the housing is driven by the cam 3 and the housing side limited the pressure chamber 5.
  • two slave pistons 8 are guided per cylinder, which drive the gas exchange valves 2 on the outside of the housing and bound the common pressure chamber 5 on the housing side.
  • An electromagnetic hydraulic valve 9, in this case a normally open 2-2-way valve interrupts in the closed state, the hydraulic connection between the pressure relief chamber 6 and the pressure chamber 5.
  • a portion of the displaced by the master piston 7 hydraulic fluid can flow into the pressure relief chamber 6, without participating in the operation of the slave piston 8 and the associated gas exchange valve 2.
  • a piston pressure accumulator 10 for receiving the displaced hydraulic fluid is connected.
  • the pressure relief chambers 6 are connected via a hydraulic connection, not shown, on the hydraulic housing 4 to the hydraulic circuit, ie the oil circuit of the internal combustion engine.
  • the pressure relief chambers 6 are connected to a common vent channel 1 1 in the hydraulic housing 4, which is hydraulically connected inside the housing via throttle points 12 with the respective pressure relief chamber 6 and outside the housing in a hydraulic reservoir 13 in the interior of the cylinder head 1 opens.
  • the throttle points 12 are geodetic, ie with respect to the symbolized by the arrow of gravity g above the pressure relief chambers 6, and the hydraulic reservoir 13 is located geodetically below the pressure relief chambers 6.
  • the channel mouth 14 of the vent passage 1 1 is not only geodetically below the level 15 of the hydraulic reservoir 13 but also below the boundary 16 of the pressure chamber 5 by the slave piston 8, when they are fully retracted in the hydraulic housing 4 with closed gas exchange valves 2.
  • the pressureless hydraulic reservoir 13, which is pressureless with respect to the internal pressure of the cylinder head 1, is closed by a depression closed in the direction of gravity 17 formed in the cylinder head 1 (see Figure 1 b), in which hydraulic fluid accumulates during operation of the internal combustion engine.
  • the vent channel 1 1 is outside the housing formed by a solid and sealingly screwed in the hydraulic housing 4 vent pipe 18.
  • This has a circular first pipe section 19, whose tube inner diameter is between 8 mm and 9 mm.
  • the first pipe section 19 merges at a diameter step 20 into a circular second pipe section 21 with a pipe inside diameter of approximately 4 mm.
  • the tube outer diameter of the second tube section 21 is correspondingly small and dimensioned such that the second tube section 21 can be introduced into the cavity 17 without collision during assembly of the hydraulic unit into the cylinder head 1.
  • Figure 1 a shows the vented filling state of the hydraulic system shortly after switching off the internal combustion engine.
  • the level 15 of the hydraulic reservoir 13 of the initially defined normal level shows the filling state of the hydraulic system at a much later time at which the hydraulic fluid is completely cooled and its volume is shrunk accordingly.
  • the forming with the reduction in volume in the hydraulic chambers negative pressure causes the suction of hydraulic fluid from the hydraulic reservoir 13 in the pressure relief chambers 6. This air bubbles free after-expiration ends when the level 15 of the hydraulic reservoir 13 geodetically below the channel opening 14 drops. Thereafter, the pressure equalization between the pressure relief chambers 6 and the environment of the hydraulic housing 4 takes place by sucking back of air bubbles 22.
  • the higher oil column between the boundary 16 and the level 15 of the Hydraulikre- reservoir 13 ' causes an increased negative pressure in the hydraulic system in favor of further reduced leakage of the pressure chambers 5 through the guide gap to the slave piston 8.
  • the vent passage 1 1 is in this embodiment by a vent pipe 18 'formed with a uniform diameter, wherein the pipe inner diameter is dimensioned so large in this case that the therein rising air bubbles 22, the standing in the vent pipe 18 ' oil column can happen.
  • the third exemplary embodiment according to FIG. 3 has a hydraulic reservoir 13 " whose volume is so great that the channel mouth 14 is always geodetically below the level 15 of the hydraulic reservoir 13 " .

Abstract

An internal combustion engine having a hydraulically variable gas exchange valve train is proposed, which gas exchange valve train comprises the following: - a hydraulic housing (4) with a pressure chamber (5), a pressure relief chamber (6) and a vent duct (11), wherein the pressure chamber, the pressure relief chamber and the vent duct are connected to one another hydraulically, - a master piston (7) which is guided in the hydraulic housing, is driven on the housing outer side by a cam (3) and delimits the pressure chamber on the housing inner side, - a slave piston (8) which is guided in the hydraulic housing, drives the gas exchange valve (2) on the housing outer side and delimits the pressure chamber on the housing inner side, - and a hydraulic valve (9) which, in the closed state, interrupts the connection between the pressure relief chamber and the pressure chamber. The vent duct is connected hydraulically on the housing inner side via a throttle point (12) to the pressure relief chamber, and opens on the housing outer side below the pressure relief chamber with regard to the direction of gravity. The vent duct is to open into a hydraulic reservoir (13, 13', 13''), wherein the duct opening (14) lies below the normal level of the hydraulic reservoir with regard to the direction of gravity.

Description

Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb  Internal combustion engine with hydraulically variable gas exchange valve drive
Die Erfindung betrifft eine Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb, der Folgendes umfasst: The invention relates to an internal combustion engine with hydraulically variable gas exchange valve drive, comprising:
- ein Hydraulikgehäuse mit einem Druckraum, einem Druckentlastungsraum und einem Entlüftungskanal, wobei der Druckraum, der Druckentlastungsraum und der Entlüftungskanal hydraulisch miteinander verbunden sind, a hydraulic housing having a pressure chamber, a pressure relief chamber and a venting channel, the pressure chamber, the pressure relief chamber and the venting channel being hydraulically connected to one another,
- einen im Hydraulikgehäuse geführten Geberkolben, der gehäuseaußenseitig von einem Nocken angetrieben ist und gehäuseinnenseitig den Druckraum be- grenzt,  a master piston guided in the hydraulic housing, which is driven on the outside of the housing by a cam and which delimits the pressure chamber on the housing side,
- einen im Hydraulikgehäuse geführten Nehmerkolben, der gehäuseaußenseitig das Gaswechselventil antreibt und gehäuseinnenseitig den Druckraum begrenzt,  a slave piston guided in the hydraulic housing, which drives the gas exchange valve outside the housing and delimits the pressure chamber on the housing side,
- und ein Hydraulikventil, das in geschlossenem Zustand die Verbindung zwi- sehen dem Druckentlastungsraum und dem Druckraum unterbricht,  and a hydraulic valve which, in the closed state, interrupts the connection between the pressure relief chamber and the pressure chamber,
wobei der Entlüftungskanal gehäuseinnenseitig über eine Drosselstelle mit dem Druckentlastungsraum hydraulisch verbunden ist und gehäuseaußenseitig bezüglich der Schwerkraftrichtung unterhalb des Druckentlastungsraums mündet. Die gattungsgemäße DE 10 2013 213 695 A1 zeigt eine Brennkraftmaschine mit einer vollvariablen hydraulischen Ventilsteuerung. Diese ist durch eine Baueinheit gebildet, die auf dem Zylinderkopf der Brennkraftmaschine montiert ist und deren Hydraulikräume sich - in Schwerkraftrichtung - nach unten in den Zylinderkopf entlüften. wherein the vent passage is inside the housing hydraulically connected via a throttle point with the pressure relief chamber and outside the housing opens with respect to the direction of gravity below the pressure relief chamber. The generic DE 10 2013 213 695 A1 shows an internal combustion engine with a fully variable hydraulic valve control. This is formed by a structural unit which is mounted on the cylinder head of the internal combustion engine and whose hydraulic chambers - in the direction of gravity - vent down into the cylinder head.
Die betriebliche Entlüftung des Hydrauliksystems bewirkt das Abscheiden der vom Hydraulikmittel mitgeführten Luftblasen in die Umgebung des Hydraulikgehäuses und verhindert damit, dass Luft in übermäßiger Menge in den Druckraum gelangt und dort die für die hydraulische Gaswechselventilbetätigung erforderliche Steif ig- keit des Hydraulikmittels in unzulässiger Höhe beeinträchtigt. Andererseits begünstigt die Entlüftung die Leckage des Hydraulikmittels aus dem Hydraulikgehäuse, wenn die Brennkraftmaschine abgestellt ist. Denn das abkühlende und dabei im Volumen schrumpfende Hydraulikmittel erzeugt Unterdruck in den Hyd- raulikräumen, der über Nachsaugen von Luft via Entlüftungskanal ausgeglichen wird. Während dieses Druckausgleichs sorgt die Schwerkraft dafür, dass sich die Hydraulikräume über die Leckage durch den Führungsspalt zwischen Nehmerkolben und Hydraulikgehäuse in dessen Umgebung entleeren. Somit besteht bei längerer Stillstandszeit der Brennkraftmaschine das erhöhte Risiko, dass sich die Hydraulikräume vollständig entleeren und die im Druckraum befindliche Luft infolge der hohen Kompressibilität den Druckaufbau im Druckraum so beeinträchtigt, dass das für den Startvorgang der Brennkraftmaschine erforderliche Öffnen des Gaswechselventils verhindert wird. The operational venting of the hydraulic system causes the entrained air bubbles carried by the hydraulic medium in the vicinity of the hydraulic housing and thus prevents air in excessive amount in the pressure chamber and there affects the required for the hydraulic gas exchange valve stiffness keit the hydraulic fluid in an inadmissible height. On the other hand, the vent promotes the leakage of hydraulic fluid from the hydraulic housing when the engine is turned off. Because the cooling and shrinking volume of hydraulic fluid creates negative pressure in the hydraulic raulikräumen, which is compensated for ingestion of air via vent channel. During this pressure equalization, gravity will cause the hydraulic chambers to deflate through the guide gap between the slave piston and the hydraulic housing in its vicinity. Thus, with prolonged downtime of the internal combustion engine, the increased risk that completely empty the hydraulic chambers and the air in the pressure chamber due to the high compressibility of the pressure build-up in the pressure chamber affected so that the required for the starting process of the engine opening of the gas exchange valve is prevented.
In der EP 2 060 754 A2 ist eine Hydraulikeinheit mit einem zusätzlichen Niederdruckraum vorgeschlagen, der zwecks Entlüftung über eine geodätisch hoch positionierte Gehäuseöffnung mit dem Inneren des Zylinderkopfs und über eine geodätisch tief positionierte Drosselstelle mit dem Druckentlastungsraum kommuni- ziert. Der Niederdruckraum stellt ein erweitertes Hydraulikreservoir dar, das den Druckraum während des Startvorgangs der Brennkraftmaschine mit hinreichend luftfreiem Hydraulikmittel versorgt. Die nicht gattungsgemäße, d.h. entgegen der Schwerkraftrichtung auf der Oberseite des Hydraulikgehäuses mündende Entlüftung erfordert jedoch einen Zylinderkopfdeckel, der den Zylinderkopf mit dem Hyd- raulikgehäuse zur Umgebung hin abdichtet, und mithin ein zusätzliches Bauteil. EP 2 060 754 A2 proposes a hydraulic unit with an additional low-pressure space which communicates with the interior of the cylinder head via a geodetically highly positioned housing opening and via a geodetically deeply positioned throttle point with the pressure relief space for the purpose of venting. The low-pressure chamber is an extended hydraulic reservoir, which supplies the pressure chamber during the starting process of the internal combustion engine with sufficiently air-free hydraulic fluid. The non-generic, i. However, venting against the direction of gravity on the upper side of the hydraulic housing requires a cylinder head cover, which seals the cylinder head with the hydraulic housing to the environment, and thus an additional component.
Der vorliegenden Erfindung liegt die Aufgabe zugrunde, eine Brennkraftmaschine der eingangs genannten Art dahingehend fortzubilden, dass die Hydraulikleckage aus dem Hydraulikgehäuse auf ein solches Maß reduziert wird, dass das im Druckraum befindliche Hydraulikmittel auch nach längerer Stillstandszeit der Brennkraftmaschine einen für deren Startvorgang kritischen Füllstand nicht unterschreitet. The present invention has the object to further develop an internal combustion engine of the type mentioned in that the hydraulic leakage from the hydraulic housing is reduced to such an extent that the hydraulic fluid in the pressure chamber does not fall below a critical for the start process level even after prolonged downtime of the engine ,
Die Lösung dieser Aufgabe ergibt sich aus den Merkmalen des Anspruchs 1 . Demnach soll der Entlüftungskanal in einem Hydraulikreservoir münden, wobei die Kanalmündung bezüglich der Schwerkraftrichtung unterhalb des Normalpegels des Hydraulikreservoirs liegt. Unter dem Begriff ' Normalpegel ' ist der Füllstand zu verstehen, der sich im stationären Zustand kurz nach dem Abstellen der Brenn- kraftmaschine im Hydraulikreservoir einstellt, wobei die Brennkraftmaschine gegenüber ihrer Einbauposition nicht oder allenfalls unwesentlich geneigt ist. Die im Hydraulikmittel„eintauchende" Kanalmündung verhindert es, dass bei stillstehender Brennkraftmaschine und infolge der Abkühlung schrumpfendem Hydraulikmit- telvolumen Luft über den Entlüftungskanal in den Druckentlastungsraum zurückgesaugt wird. Dieser Zustand erstreckt sich über einen ausreichend langen Zeitraum und zumindest so lange, bis gegebenenfalls der Pegel des Hydraulikreservoirs infolge der abkühlbedingten Volumenschrumpfung des Hydraulikmittels aus dem Hydraulikgehäuse unter die Kanalmündung gesunken ist. The solution to this problem arises from the features of claim 1. Accordingly, the venting channel to open in a hydraulic reservoir, wherein the channel mouth with respect to the direction of gravity is below the normal level of the hydraulic reservoir. The term ' normal level ' is to be understood as meaning the level which, in the steady state, shortly after switching off the fuel adjusting the hydraulic motor in the hydraulic reservoir, wherein the internal combustion engine is not or at most insignificantly inclined with respect to their installation position. The channel opening "dipping" in the hydraulic medium prevents air from being sucked back into the pressure relief chamber via the venting channel when the internal combustion engine is at a standstill and due to the cooling down of the hydraulic medium volume This condition extends over a sufficiently long period of time and at least until the level, if applicable of the hydraulic reservoir has dropped due to the cooling volume shrinkage of the hydraulic fluid from the hydraulic housing under the channel mouth.
Das zur Umgebung des Hydraulikgehäuses hin offene Hydraulikreservoir kann entweder am Hydraulikgehäuse selbst oder durch eine lokale Mulden- oder Wannenform eines Bauteils oder Abschnitts des Zylinderkopfs oder des Motorblocks der Brennkraftmaschine gebildet sein. The hydraulic reservoir open to the surroundings of the hydraulic housing can be formed either on the hydraulic housing itself or through a local depression or trough shape of a component or section of the cylinder head or of the engine block of the internal combustion engine.
Vorteilhafte Weiterbildungen und Ausgestaltungen der Erfindung sind den Unteransprüchen entnehmbar. Demnach soll bei geschlossenem Gaswechselventil die Kanalmündung bezüglich der Schwerkraftrichtung möglichst tief und konkret unterhalb der Begrenzung des Druckraums vom Nehmerkolben verlaufen. Die geo- dätische Höhendifferenz zwischen dem (im Hydraulikgehäuse eingefahrenen) Nehmerkolben und der Kanalmündung beeinflusst unmittelbar den Unterdruck, der sich bei abgestellter Brennkraftmaschine und schrumpfendem Hydraulikmittel gegenüber der Umgebung des Hydraulikgehäuses bildet und der schwerkraftbedingten Leckage des Hydraulikmittels aus dem Hydraulikgehäuse entgegenwirkt. Advantageous developments and refinements of the invention can be taken from the subclaims. Accordingly, when the gas exchange valve is closed, the channel mouth with respect to the direction of gravity should run as deep as possible and concretely below the boundary of the pressure chamber from the slave piston. The geodätische height difference between the (retracted in the hydraulic housing) slave piston and the channel mouth directly affects the negative pressure, which forms when the engine and shrinking hydraulic fluid against the environment of the hydraulic housing and counteracts the gravitational leakage of hydraulic fluid from the hydraulic housing.
Aus den zuvor erläuterten Gründen ist es besonders vorteilhaft, wenn die Kanalmündung bezüglich der Schwerkraftrichtung, d.h. geodätisch stets unterhalb des Pegels des Hydraulikreservoirs liegt. Dieser Zustand setzt voraus, dass das Hydraulikreservoir im Hinblick auf das temperatur- und leckagebedingt abnehmende Hydraulikvolumen im Hydraulikgehäuse hinreichend voluminös ausgeführt werden kann. For the reasons explained above, it is particularly advantageous if the channel mouth is inclined with respect to the direction of gravity, i. geodetic always below the level of the hydraulic reservoir. This condition assumes that the hydraulic reservoir can be made sufficiently voluminous in view of the temperature and leakage-reducing hydraulic volume in the hydraulic housing.
Demgegenüber ist es eher wahrscheinlich, dass das Volumen des Hydraulikreser- voirs konstruktiv derart beschränkt ist, dass ein Absinken des Reservoirpegels unter die Kanalmündung und folglich das Rücksaugen von Luft nicht vermeidbar sind. Dennoch kann die Stillstandszeit der Brennkraftmaschine bis zum Erreichen des kritischen Füllstands im Druckraum signifikant dadurch verlängert werden, dass der Entlüftungskanal zumindest lokal einen so dimensionierten Querschnitt hat, dass darin Luftblasen aufsteigen können, ohne die darüber liegende Hydraulik- oder Ölsäule vor sich her zu schieben und in den Druckentlastungsraum zu verdrängen. Vielmehr ist der Querschnitt so zu bemessen, dass die rückgesaugte Luft in der stehenden Ölsäule aufsteigt, so dass die verbleibende Ölsäule die Ka- nalmündung quasi wieder verschließt und den Leckage hemmenden Unterdruck im Hydraulikgehäuse aufrecht erhält. Diesbezügliche Versuche der Anmelderin haben gezeigt, dass der Entlüftungskanal im Falle eines Öls mit dem Viskositätsindex 0W20 und im Falle eines kreisförmigen ersten Rohrabschnitts einen Rohr- Innendurchmesser von wenigstens 6 mm haben muss. Besonders gute und robus- te Ergebnisse wurden mit dem Rohr-Innendurchmesser von ca. 8 mm erzielt. Die Kreisform des Entlüftungskanals kann fertigungstechnische Vorteile haben. Dennoch sind andere Querschnittsformen möglich, solange das Aufsteigen der Luft ohne Verdrängen der darüber liegenden Ölsäule möglich ist. Weiterhin soll die Kanalmündung durch einen kreisförmigen zweiten Rohrabschnitt gebildet sein, der sich unter (abrupter oder allmählicher) Verkleinerung des Rohr- Außendurchmessers an den ersten Rohrabschnitt anschließt. Diese konstruktive Ausgestaltung des Entlüftungskanals mit den im Durchmesser gestuften Rohrabschnitten kann erforderlich sein, falls die Oberfläche des Hydraulikreservoirs zu klein ist, um den relativ großen Durchmesser des ersten Rohrabschnitts aufzunehmen. In contrast, it is more likely that the volume of the hydraulic reservoir is constructively limited such that a drop in the reservoir level below the channel mouth and consequently the suck back of air are unavoidable. Nevertheless, the downtime of the internal combustion engine can be significantly extended until it reaches the critical level in the pressure chamber that the vent channel at least locally has a dimensioned so large that air bubbles can ascend therein without pushing the overlying hydraulic or oil column in front of him and to displace into the pressure relief chamber. Rather, the cross-section is to be dimensioned so that the air sucked back rises in the stationary oil column, so that the remaining oil column virtually closes the channel mouth again and maintains the leakage-inhibiting negative pressure in the hydraulic housing. Applicant's related tests have shown that in the case of an oil having the viscosity index 0W20 and in the case of a circular first pipe section, the venting channel must have a pipe inside diameter of at least 6 mm. Particularly good and robust results were achieved with the tube inner diameter of about 8 mm. The circular shape of the vent channel can have manufacturing advantages. Nevertheless, other cross-sectional shapes are possible, as long as the rising of the air without displacing the overlying oil column is possible. Furthermore, the channel mouth should be formed by a circular second pipe section, which is followed by (abrupt or gradual) reduction of the tube outer diameter of the first pipe section. This structural design of the vent channel with the diameter-stepped pipe sections may be required if the surface of the hydraulic reservoir is too small to accommodate the relatively large diameter of the first pipe section.
Der Entlüftungskanal ist zweckmäßigerweise durch ein im Hydraulikgehäuse befestigtes und vorzugsweise eingeschraubtes Entlüftungsrohr gebildet, wobei der erste und gegebenenfalls der zweite Rohrabschnitt Teile des Entlüftungsrohrs sind. The venting channel is expediently formed by a venting tube fastened in the hydraulic housing and preferably screwed in, the first and possibly the second tubular section being parts of the venting tube.
Weitere Merkmale der Erfindung ergeben sich aus der nachfolgenden Beschrei- bung und aus den Zeichnungen, in denen drei Ausführungsbeispiele der Erfindung schematisch dargestellt sind. Soweit nicht anders erwähnt, sind dabei gleiche oder funktionsgleiche Merkmale oder Bauteile mit gleichen Bezugszahlen versehen. Es zeigen: Further features of the invention will become apparent from the following description. tion and from the drawings, in which three embodiments of the invention are shown schematically. Unless otherwise stated, the same or functionally identical features or components are provided with the same reference numbers. Show it:
Figur 1 a das erste Ausführungsbeispiel mit einem im Durchmesser gestuften Entlüftungskanal; Figure 1 a, the first embodiment with a stepped in diameter vent passage;
Figur 1 b in vergrößerter Einzelheit die Kanalmündung und das Hydraulikreservoir des ersten Ausführungsbeispiels; Figure 1 b in an enlarged detail of the channel mouth and the hydraulic reservoir of the first embodiment;
Figur 2 das zweite Ausführungsbeispiel mit einem vergleichsweise tief liegenden Figure 2 shows the second embodiment with a comparatively low-lying
Hydraulikreservoir; Figur 3 das dritte Ausführungsbeispiel mit einer permanent im Hydraulikreservoir eintauchenden Kanalmündung.  Hydraulic reservoir; Figure 3 shows the third embodiment with a permanently immersed in the hydraulic reservoir channel mouth.
Figur 1 a zeigt schematisch den für das Verständnis der Erfindung wesentlichen Ausschnitt einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventil- trieb. Dargestellt ist ein Zylinderkopf 1 mit zwei gleichartigen und in Schließrichtung federkraftbeaufschlagten Gaswechselventilen 2 pro Zylinder und zugehörigen Nocken 3 einer Nockenwelle. Die Variabilität des Gaswechselventiltriebs wird auf bekannte Weise mittels einer zwischen den Nocken 3 und den Gaswechselventilen 2 angeordneten Hydraulikeinheit erzeugt. Diese umfasst ein im Zylinderkopf 1 befestigtes Hydraulikgehäuse 4, in dem je Zylinder ein Druckraum 5 und ein Druckentlastungsraum 6 ausgebildet sowie ein Geberkolben 7 geführt sind, der ge- häuseaußenseitig vom Nocken 3 angetrieben ist und gehäuseinnenseitig den Druckraum 5 begrenzt. Weiterhin sind im Hydraulikgehäuse 4 zwei Nehmerkolben 8 je Zylinder geführt, die gehäuseaußenseitig die Gaswechselventile 2 antreiben und gehäuseinnenseitig den gemeinsamen Druckraum 5 begrenzen. Ein elektromagnetisches Hydraulikventil 9, vorliegend ein stromlos geöffnetes 2-2 -Wegeventil unterbricht in geschlossenem Zustand die hydraulische Verbindung zwischen dem Druckentlastungsraum 6 und dem Druckraum 5. Im geöffneten Zustand des Hyd- raulikventils 9 kann ein Teil des vom Geberkolben 7 verdrängten Hydraulikmittels in den Druckentlastungsraum 6 abströmen, ohne an der Betätigung des Nehmerkolbens 8 und des zugehörigen Gaswechselventils 2 teilzunehmen. An jedem Druckentlastungsraum 6 ist ein Kolbendruckspeicher 10 zur Aufnahme des ver- drängten Hydraulikmittels angeschlossen. Die Druckentlastungsräume 6 sind über einen nicht dargestellten Hydraulikanschluss am Hydraulikgehäuse 4 mit dem Hydraulikkreislauf, d.h. dem Ölkreislauf der Brennkraftmaschine verbunden. Figure 1 a shows schematically the essential for understanding the invention section of an internal combustion engine with hydraulically variable Gaswechselventil- drive. Shown is a cylinder head 1 with two similar and spring-loaded in the closing direction gas exchange valves 2 per cylinder and associated cam 3 of a camshaft. The variability of the gas exchange valve drive is generated in a known manner by means of a arranged between the cam 3 and the gas exchange valves 2 hydraulic unit. This comprises a mounted in the cylinder head 1 hydraulic housing 4, in which each cylinder a pressure chamber 5 and a pressure relief chamber 6 formed and a master piston 7 are guided outside the housing is driven by the cam 3 and the housing side limited the pressure chamber 5. Furthermore, in the hydraulic housing 4, two slave pistons 8 are guided per cylinder, which drive the gas exchange valves 2 on the outside of the housing and bound the common pressure chamber 5 on the housing side. An electromagnetic hydraulic valve 9, in this case a normally open 2-2-way valve interrupts in the closed state, the hydraulic connection between the pressure relief chamber 6 and the pressure chamber 5. In the open state of the hydraulic Raulikventils 9, a portion of the displaced by the master piston 7 hydraulic fluid can flow into the pressure relief chamber 6, without participating in the operation of the slave piston 8 and the associated gas exchange valve 2. At each pressure relief chamber 6, a piston pressure accumulator 10 for receiving the displaced hydraulic fluid is connected. The pressure relief chambers 6 are connected via a hydraulic connection, not shown, on the hydraulic housing 4 to the hydraulic circuit, ie the oil circuit of the internal combustion engine.
Die an sich bekannte Funktionsweise des hydraulischen Gaswechselventiltriebs lässt sich dahingehend zusammenfassen, dass der Druckraum 5 zwischen dem Geberkolben 7 und den Nehmerkolben 8 als hydraulisches Gestänge wirkt. Dabei wird das - bei Vernachlässigung von Leckagen - proportional zum Hub des Nockens 3 vom Geberkolben 7 verdrängte Hydraulikmittel in Abhängigkeit des Öffnungszeitpunkts und der Öffnungsdauer des Hydraulikventils 9 in ein erstes, die Nehmerkolben 8 beaufschlagendes Teilvolumen und in ein zweites, in den Druckentlastungsraum 6 einschließlich Kolbendruckspeicher 10 abströmendes Teilvolumen aufgeteilt. Hierdurch sind die Hubübertragung des Geberkolbens 7 auf die Nehmerkolben 8 und mithin nicht nur die Steuerzeiten, sondern auch die Hubhöhe der Gaswechselventile 2 vollvariabel einstellbar. The known manner of operation of the hydraulic gas exchange valve drive can be summarized to the effect that the pressure chamber 5 between the master piston 7 and the slave piston 8 acts as a hydraulic linkage. In this case, the negligible leakage - proportional to the stroke of the cam 3 displaced by the master piston 7 hydraulic fluid in response to the opening time and the opening duration of the hydraulic valve 9 in a first, the slave piston 8 acting subvolume and in a second, in the pressure relief chamber 6 including piston pressure accumulator Divided 10 outflowing subvolume. As a result, the stroke transmission of the master piston 7 to the slave piston 8 and therefore not only the timing, but also the lifting height of the gas exchange valves 2 are fully variable adjustable.
Die Druckentlastungsräume 6 sind an einen gemeinsamen Entlüftungskanal 1 1 im Hydraulikgehäuse 4 angeschlossen, der gehäuseinnenseitig über Drosselstellen 12 mit dem jeweiligen Druckentlastungsraum 6 hydraulisch verbunden ist und ge- häuseaußenseitig in einem Hydraulikreservoir 13 im Inneren des Zylinderkopfs 1 mündet. Die Drosselstellen 12 liegen geodätisch, d.h. bezüglich der durch den Pfeil symbolisierten Richtung der Schwerkraft g oberhalb der Druckentlastungsräume 6, und das Hydraulikreservoir 13 liegt geodätisch unterhalb der Druckentlastungsräume 6. Die Kanalmündung 14 des Entlüftungskanals 1 1 liegt geodätisch nicht nur unterhalb des Pegels 15 des Hydraulikreservoirs 13 sondern auch unter- halb der Begrenzung 16 des Druckraums 5 durch die Nehmerkolben 8, wenn diese bei geschlossenen Gaswechselventilen 2 vollständig im Hydraulikgehäuse 4 eingefahren sind. Das gegenüber dem Innendruck des Zylinderkopfs 1 drucklose Hydraulikreservoir 13 ist durch eine in Schwerkraftrichtung geschlossene Mulde 17 im Zylinderkopf 1 gebildet (s. Figur 1 b), in der sich während des Betriebs der Brennkraftmaschine Hydraulikmittel ansammelt. The pressure relief chambers 6 are connected to a common vent channel 1 1 in the hydraulic housing 4, which is hydraulically connected inside the housing via throttle points 12 with the respective pressure relief chamber 6 and outside the housing in a hydraulic reservoir 13 in the interior of the cylinder head 1 opens. The throttle points 12 are geodetic, ie with respect to the symbolized by the arrow of gravity g above the pressure relief chambers 6, and the hydraulic reservoir 13 is located geodetically below the pressure relief chambers 6. The channel mouth 14 of the vent passage 1 1 is not only geodetically below the level 15 of the hydraulic reservoir 13 but also below the boundary 16 of the pressure chamber 5 by the slave piston 8, when they are fully retracted in the hydraulic housing 4 with closed gas exchange valves 2. The pressureless hydraulic reservoir 13, which is pressureless with respect to the internal pressure of the cylinder head 1, is closed by a depression closed in the direction of gravity 17 formed in the cylinder head 1 (see Figure 1 b), in which hydraulic fluid accumulates during operation of the internal combustion engine.
Der Entlüftungskanal 1 1 ist gehäuseaußenseitig durch ein im Hydraulikgehäuse 4 fest und dichtend eingeschraubtes Entlüftungsrohr 18 gebildet. Dieses hat einen kreisförmigen ersten Rohrabschnitt 19, dessen Rohr-Innendurchmesser zwischen 8 mm und 9 mm beträgt. Der erste Rohrabschnitt 19 geht an einer Durchmesserstufe 20 in einen kreisförmigen zweiten Rohrabschnitt 21 mit einem Rohr- Innendurchmesser von ca. 4 mm über. Der Rohr-Außendurchmesser des zweiten Rohrabschnitts 21 ist dementsprechend klein und so dimensioniert, dass der zweite Rohrabschnitt 21 bei der Montage der Hydraulikeinheit in den Zylinderkopf 1 kollisionsfrei in die Mulde 17 einführbar ist. The vent channel 1 1 is outside the housing formed by a solid and sealingly screwed in the hydraulic housing 4 vent pipe 18. This has a circular first pipe section 19, whose tube inner diameter is between 8 mm and 9 mm. The first pipe section 19 merges at a diameter step 20 into a circular second pipe section 21 with a pipe inside diameter of approximately 4 mm. The tube outer diameter of the second tube section 21 is correspondingly small and dimensioned such that the second tube section 21 can be introduced into the cavity 17 without collision during assembly of the hydraulic unit into the cylinder head 1.
Figur 1 a zeigt den entlüfteten Füllzustand des Hydrauliksystems kurz nach dem Abstellen der Brennkraftmaschine. Dabei ist der Pegel 15 des Hydraulikreservoirs 13 der eingangs definierte Normalpegel. Die Einzelheit gemäß Figur 1 b zeigt den Füllzustand des Hydrauliksystems zu einem deutlich späteren Zeitpunkt, an dem das Hydraulikmittel vollständig abgekühlt und dessen Volumen dementsprechend geschrumpft ist. Der sich mit der Volumenverkleinerung in den Hydraulikräumen bildende Unterdruck bewirkt das Nachsaugen von Hydraulikmittel aus dem Hydraulikreservoir 13 in die Druckentlastungsräume 6. Dieses luftblasenfreie Nachsaugen endet dann, wenn der Pegel 15 des Hydraulikreservoirs 13 geodätisch unter die Kanalmündung 14 sinkt. Danach erfolgt der Druckausgleich zwischen den Druckentlastungsräumen 6 und der Umgebung des Hydraulikgehäuses 4 durch Rücksaugen von Luftblasen 22. Der im Verhältnis zur Luftblasengröße deutlich größere Rohr-Innendurchmesser des ersten Rohrabschnitts 19 ermöglicht es, dass die Luftblasen 22 durch die darin stehende Ölsäule hindurch nach oben wandern können, wobei sich die Ölsäule nach dem Passieren der Luftblasen 22 wieder schließt. Hierdurch wird ein Unterdruck aufrechterhalten, der die hydrauli- sehe Leckage durch den Führungsspalt zwischen den Nehmerkolben 8 und dem Hydraulikgehäuse 4 in den Zylinderkopf 1 hemmt und damit - zusätzlich zum Volumenausgleich aus dem Hydraulikreservoir 13 - das kritische Entleeren des Druckraums 5 verzögert. Bei dem in Figur 2 dargestellten zweiten Ausführungsbeispiel liegt das Hydraulikreservoir 13' geodätisch deutlich tiefer als beim ersten Ausführungsbeispiel. Die höhere Ölsäule zwischen der Begrenzung 16 und dem Pegel 15 des Hydraulikre- servoirs 13' bewirkt einen erhöhten Unterdruck im Hydrauliksystem zugunsten der weiter verringerten Leckage der Druckräume 5 durch den Führungsspalt um die Nehmerkolben 8. Der Entlüftungskanal 1 1 ist bei dieser Ausführung durch ein Entlüftungsrohr 18' mit gleichmäßigem Durchmesser gebildet, wobei der Rohr- Innendurchmesser auch in diesem Fall so groß bemessen ist, dass die darin auf- steigenden Luftblasen 22 die im Entlüftungsrohr 18' stehende Ölsäule passieren können. Figure 1 a shows the vented filling state of the hydraulic system shortly after switching off the internal combustion engine. In this case, the level 15 of the hydraulic reservoir 13 of the initially defined normal level. The detail according to Figure 1 b shows the filling state of the hydraulic system at a much later time at which the hydraulic fluid is completely cooled and its volume is shrunk accordingly. The forming with the reduction in volume in the hydraulic chambers negative pressure causes the suction of hydraulic fluid from the hydraulic reservoir 13 in the pressure relief chambers 6. This air bubbles free after-expiration ends when the level 15 of the hydraulic reservoir 13 geodetically below the channel opening 14 drops. Thereafter, the pressure equalization between the pressure relief chambers 6 and the environment of the hydraulic housing 4 takes place by sucking back of air bubbles 22. The larger in relation to the bubble size tube inner diameter of the first pipe section 19 allows the air bubbles 22 through the standing therein oil column pass upwards can, with the oil column after passing through the air bubbles 22 closes again. In this way, a negative pressure is maintained, which inhibits the hydraulic leak through the guide gap between the slave piston 8 and the hydraulic housing 4 in the cylinder head 1 and thus - in addition to the volume compensation from the hydraulic reservoir 13 - delays the critical emptying of the pressure chamber 5. In the second embodiment shown in Figure 2, the hydraulic reservoir 13 'is geodetically significantly lower than in the first embodiment. The higher oil column between the boundary 16 and the level 15 of the Hydraulikre- reservoir 13 ' causes an increased negative pressure in the hydraulic system in favor of further reduced leakage of the pressure chambers 5 through the guide gap to the slave piston 8. The vent passage 1 1 is in this embodiment by a vent pipe 18 'formed with a uniform diameter, wherein the pipe inner diameter is dimensioned so large in this case that the therein rising air bubbles 22, the standing in the vent pipe 18 ' oil column can happen.
Das dritte Ausführungsbeispiel gemäß Figur 3 hat ein Hydraulikreservoir 13", dessen Volumen so groß ist, dass die Kanalmündung 14 geodätisch stets unter- halb des Pegels 15 des Hydraulikreservoirs 13" liegt. The third exemplary embodiment according to FIG. 3 has a hydraulic reservoir 13 " whose volume is so great that the channel mouth 14 is always geodetically below the level 15 of the hydraulic reservoir 13 " .
Liste der Bezugszahlen List of reference numbers
1 Zylinderkopf 1 cylinder head
2 Gaswechselventil  2 gas exchange valve
3 Nocken  3 cams
4 Hydraulikgehäuse  4 hydraulic housings
5 Druckraum  5 pressure chamber
6 Druckentlastungsraum  6 pressure relief room
7 Geberkolben  7 master piston
8 Nehmerkolben  8 slave pistons
9 Hydraulikventil  9 hydraulic valve
10 Kolbendruckspeicher  10 piston pressure accumulator
1 1 Entlüftungskanal  1 1 venting channel
12 Drosselstelle  12 throttle point
13 Hydraulikreservoir  13 hydraulic reservoir
14 Kanalmündung  14 canal mouth
15 Pegel Begrenzung 15 levels limit
Mulde trough
Entlüftungsrohr erster Rohrabschnitt Durchmesserstufe zweiter Rohrabschnitt Luftblase Bleed pipe first pipe section Diameter stage second pipe section Air bubble

Claims

Patentansprüche claims
Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb, der Folgendes umfasst: Internal combustion engine with hydraulically variable gas exchange valve train, comprising:
- ein Hydraulikgehäuse (4) mit einem Druckraum (5), einem Druckentlastungsraum (6) und einem Entlüftungskanal (1 1 ), wobei der Druckraum (5), der Druckentlastungsraum (6) und der Entlüftungskanal (1 1 ) hydraulisch miteinander verbunden sind,  - A hydraulic housing (4) having a pressure chamber (5), a pressure relief chamber (6) and a venting channel (1 1), wherein the pressure chamber (5), the pressure relief chamber (6) and the venting channel (1 1) are hydraulically connected to each other,
- einen im Hydraulikgehäuse (4) geführten Geberkolben (7), der gehäuseau- ßenseitig von einem Nocken (3) angetrieben ist und gehäuseinnenseitig den Druckraum (5) begrenzt,  a master piston (7) guided in the hydraulic housing (4), which is externally driven on the housing side by a cam (3) and delimits the pressure chamber (5) on the housing side;
- einen im Hydraulikgehäuse (4) geführten Nehmerkolben (8), der gehäuse- außenseitig das Gaswechselventil (2) antreibt und gehäuseinnenseitig den Druckraum (5) begrenzt,  - A in the hydraulic housing (4) guided slave piston (8), the outside of the housing drives the gas exchange valve (2) and the housing inside the pressure chamber (5) limited,
- und ein Hydraulikventil (9), das in geschlossenem Zustand die Verbindung zwischen dem Druckentlastungsraum (6) und dem Druckraum (5) unterbricht,  - And a hydraulic valve (9) which interrupts the connection between the pressure relief chamber (6) and the pressure chamber (5) in the closed state,
wobei der Entlüftungskanal (1 1 ) gehäuseinnenseitig über eine Drosselstelle (12) mit dem Druckentlastungsraum (6) hydraulisch verbunden ist und gehäu- seaußenseitig bezüglich der Schwerkraftrichtung unterhalb des Druckentlastungsraums (6) mündet, dadurch gekennzeichnet, dass der Entlüftungskanal (1 1 ) in einem Hydraulikreservoir (13, 13', 13") mündet, wobei die Kanalmündung (14) bezüglich der Schwerkraftrichtung unterhalb des Normalpegels des Hydraulikreservoirs (13, 13', 13") liegt. wherein the vent channel (1 1) is hydraulically connected inside the housing via a throttle point (12) to the pressure relief space (6) and opens out on the outside of the housing with respect to the direction of gravity below the pressure relief space (6), characterized in that the venting channel (1 1) in one Hydraulic reservoir (13, 13 ' , 13 " ) opens, wherein the channel mouth (14) with respect to the direction of gravity below the normal level of the hydraulic reservoir (13, 13 ' , 13 " ).
Brennkraftmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass bei geschlossenem Gaswechselventil (2) die Kanalmündung (14) bezüglich der Schwerkraftrichtung unterhalb der Begrenzung (16) des Druckraums (5) vom Nehmerkolben (8) verläuft. Internal combustion engine according to claim 1, characterized in that when the gas exchange valve (2) is closed, the channel mouth (14) extends below the boundary (16) of the pressure chamber (5) from the slave piston (8) with respect to the direction of gravity.
Brennkraftmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Kanalmündung (14) bezüglich der Schwerkraftrichtung stets unterhalb des Pegels (15) des Hydraulikreservoirs (13") liegt. Brennkraftmaschine nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Entlüftungskanal (1 1 ) einen kreisförmigen ersten Rohrabschnitt (19) hat, dessen Rohr-Innendurchmesser mindestens 6 mm beträgt. Internal combustion engine according to claim 1 or 2, characterized in that the channel mouth (14) with respect to the direction of gravity is always below the level (15) of the hydraulic reservoir (13 " ). Internal combustion engine according to one of the preceding claims, characterized in that the venting channel (1 1) has a circular first tube section (19) whose tube inner diameter is at least 6 mm.
Brennkraftmaschine nach Anspruch 4, dadurch gekennzeichnet, dass die Kanalmündung (14) durch einen kreisförmigen zweiten Rohrabschnitt (21 ) gebildet ist, der sich unter Verkleinerung des Rohr-Außendurchmessers an den ersten Rohrabschnitt (19) anschließt. Internal combustion engine according to claim 4, characterized in that the channel mouth (14) by a circular second pipe section (21) is formed, which adjoins the first pipe section (19) while reducing the tube outer diameter.
Brennkraftmaschine nach Anspruch 4 oder 5, dadurch gekennzeichnet, dass der erste Rohrabschnitt (19) Teil eines im Hydraulikgehäuse (4) befestigten Entlüftungsrohrs (18) ist. Internal combustion engine according to claim 4 or 5, characterized in that the first pipe section (19) is part of a in the hydraulic housing (4) attached to the vent pipe (18).
Brennkraftmaschine nach Anspruch 6, dadurch gekennzeichnet, dass das Entlüftungsrohr (18) im Hydraulikgehäuse (4) eingeschraubt ist. Internal combustion engine according to claim 6, characterized in that the vent pipe (18) in the hydraulic housing (4) is screwed.
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US20190211718A1 (en) 2019-07-11
WO2018059627A1 (en) 2018-04-05
DE102016218918A1 (en) 2018-03-29
EP3519683B1 (en) 2020-09-02
US10900389B2 (en) 2021-01-26
CN109715911A (en) 2019-05-03
CN109715911B (en) 2021-10-12
DE102016218918B4 (en) 2018-09-13

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