EP1397581B1 - Hydraulic play compensation element for a valve gear of an internal combustion engine - Google Patents
Hydraulic play compensation element for a valve gear of an internal combustion engine Download PDFInfo
- Publication number
- EP1397581B1 EP1397581B1 EP02747227A EP02747227A EP1397581B1 EP 1397581 B1 EP1397581 B1 EP 1397581B1 EP 02747227 A EP02747227 A EP 02747227A EP 02747227 A EP02747227 A EP 02747227A EP 1397581 B1 EP1397581 B1 EP 1397581B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- compensation element
- volume
- buffer space
- pressure chamber
- clearance compensation
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 9
- 239000010687 lubricating oil Substances 0.000 claims description 17
- 238000007789 sealing Methods 0.000 claims description 11
- 238000005381 potential energy Methods 0.000 claims description 5
- 239000007788 liquid Substances 0.000 claims description 2
- 238000006073 displacement reaction Methods 0.000 claims 1
- 230000002441 reversible effect Effects 0.000 claims 1
- 230000006835 compression Effects 0.000 description 4
- 238000007906 compression Methods 0.000 description 4
- TZCXTZWJZNENPQ-UHFFFAOYSA-L barium sulfate Chemical compound [Ba+2].[O-]S([O-])(=O)=O TZCXTZWJZNENPQ-UHFFFAOYSA-L 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000001419 dependent effect Effects 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 238000004904 shortening Methods 0.000 description 2
- 230000015556 catabolic process Effects 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000011038 discontinuous diafiltration by volume reduction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000002427 irreversible effect Effects 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
-
- 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
- F01L1/20—Adjusting or compensating clearance
- F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
- F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0031—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of tappet or pushrod length
Definitions
- the invention relates to a hydraulic clearance compensation element for a valve train of an internal combustion engine after Preamble of claim 1.
- Such a clearance compensation element is known from DE 38 00 945.
- the additional, controllable shut-off valve in the connection between the Pressure and supply space thereto under certain engine operating conditions, such as in particular an engine braking operation, a Increasing the clamping length of the clearance compensation element by closing this additional shut-off valve prevent.
- an increase in the clamping length at opened additional shut-off valve by opening the provided in the connection between the pressure and pantry One way valves are used, one between pressure and Reservoir to the one-way valve bridging throttle channel a possible clamping length shortening.
- the invention deals with the problem of a constructive Design of the generic clearance compensation element in which these difficulties do not occur.
- the invention is based on the general idea that between the telescoping components of the Play compensation element given ring gap as the the pressure chamber one-way valve bypassing throttle channel use and pass it over a buffer space whose Volume dependent on the amount of pressure within this room is.
- the dependence is such that the volume below a certain internal pressure a minimum value occupies and becomes larger at an overlying pressure.
- the increase in volume takes place by an enlargement of the Buffer space under construction of a volume increase proportional opposite potential energy. These potential energy causes a volume reduction as soon as within the buffer space, a pressure reduction takes place.
- the construction of a potential energy within a boundary wall the buffer space has the advantage that the in this room with additional shut-off valve closed the clearance compensation element stored liquid volume -
- a buffer space enlargement is exclusive to one Closed additional shut-off valve possible - under Degradation of this energy can drain again.
- Such a drain takes place, for example, already in a closed additional shut-off valve when the clearance compensation element no external clamping force is exposed.
- the oil stored in the buffer space flows through the one-way valve back into the pressure chamber and thereby causes a Einspannavinveriererung. Important is this, however, that between the buffer space and the one-way valve to the Pressure chamber a substantially unthrottled flow path is available.
- the buffer space can be anywhere between the Throttling channel and the one-way valve with the pressure chamber be provided in connection storeroom.
- a particularly advantageous arrangement can be through the Use of an axially displaceable sealing ring within a Annular space between the two nestable Achieve components of the clearance compensation element. there should the ring seal in a radial annular gap extension, which no longer acts as a throttle channel arranged to be able to obtain an effective buffer space size.
- the ring seal from the outside by an axial pressurizing acting spring loaded.
- a clearance compensation element 3 in the bore longitudinal direction slidably inserted.
- the clearance compensation element 3 comprises as a first component a closed on one side Cylinder part 4, in which between a not shown Valve tappet or shaft and an optional provided Compression spring 5 a piston member 6 is slidably held.
- the Compression spring 5 is on the closed bottom part of the cylinder part 4 and on an end wall of the piston part 6 supported, whereby cylinder and piston part 4, 6 in opposite directions of movement are biased so on the one hand the cylinder part 4 with its closed Bottom part of a control cam, not shown, and on the other the piston part 6 on the plunger or stem of the gas exchange valve without play.
- the piston part 6 closes with the cylinder part 4 a Pressure chamber 7, which with lubricating oil from a in the piston part. 6 trained reservoir 8 is filled, which from the housing bore is supplied. This feeder is in the drawing indicated with flow arrows.
- the storage space 8 is in this way constantly with lubricating oil from the lubricating oil circuit of the internal combustion engine acted upon.
- the shut-off valve 11 consists of a valve seat 12, a associated valve ball 13 and the valve ball thirteenth acting springs, namely a first an opening function effecting spring 14 and a second a shutter function causing spring 15.
- the second spring 15 acts the valve ball 13 only indirectly via a control piston 16.
- the location of this control piston 16 is of the Lubricating oil pressure within the storage chamber 8 determined. at completely pending lubricating oil pressure is the shut-off valve 11 open. This corresponds to normal engine operation. at Braking operation of the internal combustion engine becomes the lubricating oil pressure lowered so far that the shut-off valve 11 closes.
- a one-way valve 11 bridging throttle channel Between the pressure chamber 7 and the connecting channel 9 exists a one-way valve 11 bridging throttle channel, the of the annular gap 17 between the cylinder part 4 and the Piston part 6 is present.
- the annular gap 17 opens via a Connecting line 18 in the connecting channel 9.
- a radially sealing ring 20 is provided in the area the transition of the annular gap 7 in the connecting line 18 in an extended annular gap area 19 .
- the radial seal takes place between the piston part 6 on the one hand and the Cylinder part 4 on the other.
- the sealing ring 20 Within the extended Annular gap area 19, the sealing ring 20 is axially displaceable stored. At its axially remote from the pressure chamber 7 End is the sealing ring 20 by a on the piston part 6 supporting compression spring 21 acted upon.
- the compressive forces of the springs 15 and 21, that is the springs the shut-off valve 11 and the sealing ring 20 are such coordinated with each other, that when the shut-off valve is closed 11 flowing out through the annular gap 17 from the pressure chamber 7 Lubricating oil, do not open the valve 11, the sealing ring 20 for Forming a buffer space 22, however, axially by clamping the spring 21 can move.
- lubricating oil can by the potential spring energy, which at an enlarged buffer space 22 acts on the sealing ring 20, with closed shut-off valve 11 through the one-way valve 20 in the pressure chamber. 7 flow back and thereby a desired in certain conditions Effect clamping length enlargement.
- An operating condition, in which such a clamping length enlargement desired may be, for example, if an internal combustion engine in engine braking operation with an open charge exchange valve is turned off. In this case it stands Backlash element in engine standstill under one Clamp length shortening causing bias. From a such condition must be at a start of the engine the clamping length as quickly as possible for this Operation significant greater clamping length can be increased.
- the minimum volume of the buffer space 22 can in extreme cases Be zero.
Description
Die Erfindung betrifft ein hydraulisches Spielausgleichselement für einen Ventiltrieb eines Verbrennungsmotors nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic clearance compensation element for a valve train of an internal combustion engine after Preamble of claim 1.
Ein solches Spielausgleichselement ist aus DE 38 00 945 bekannt. Bei diesem Spielausgleichselement dient das zusätzliche, steuerbare Absperrventil in der Verbindung zwischen dem Druck- und Vorratsraum dazu, bei bestimmten Motorbetriebsbedingungen, wie insbesondere einem Motorbremsbetrieb, ein Vergrößern der Einspannlänge des Spielausgleichselementes durch ein Schließen dieses zusätzlichen Absperrventiles zu verhindern. Während eine Vergrößerung der Einspannlänge bei geöffnetem zusätzlichen Absperrventil durch ein Öffnen des in der Verbindung zwischen Druck- und Vorratsraum vorgesehenen Einwegeventiles erfolgt, dient ein zwischen Druck- und Vorratsraum das Einwegeventil überbrückender Drosselkanal zu einer möglichen Einspannlängenverkürzung. Um bei einem geschlossenen zusätzlichen Absperrventil eine in diesem Zustand irreversible Einspannlängenverkürzung durch aus dem Druckraum über den Drosselkanal abfließende Druckflüssigkeit zu verhindern, muß der Drosselkanal bei geschlossenem zusätzlichem Absperrventil verschlossen sein. Die Art des bei jenem bekannten Spielausgleichselement eingesetzten Drosselkanales, der dort als eine Drosselbohrung ausgebildet ist, sowie die dort gewählte Art, diesen bei geschlossenem zusätzlichen Absperrventil zu verschließen, bereiten im praktischen Betrieb Schwierigkeiten.Such a clearance compensation element is known from DE 38 00 945. In this clearance compensation element, the additional, controllable shut-off valve in the connection between the Pressure and supply space thereto, under certain engine operating conditions, such as in particular an engine braking operation, a Increasing the clamping length of the clearance compensation element by closing this additional shut-off valve prevent. While an increase in the clamping length at opened additional shut-off valve by opening the provided in the connection between the pressure and pantry One way valves are used, one between pressure and Reservoir to the one-way valve bridging throttle channel a possible clamping length shortening. To be closed additional shut-off valve one in this state irreversible Einspannlängenverkürzung by from the Pressure chamber via the throttle channel effluent pressure fluid To prevent the throttle channel must be closed with additional Shut off valve be closed. The nature of the case that known clearance compensation element used throttle channel, there formed as a throttle bore is, as well as the selected there, this closed to close additional shut-off valve, prepare in practical operation difficulties.
Die Erfindung beschäftigt sich mit dem Problem, eine konstruktive Gestaltung des gattungsgemäßen Spielausgleichselementes zu schaffen, bei der diese Schwierigkeiten nicht auftreten.The invention deals with the problem of a constructive Design of the generic clearance compensation element in which these difficulties do not occur.
Eine Lösung dieses Problemes zeigt ein gattungsgemäßes Spielausgleichselement mit den kennzeichnenden Merkmalen des Patentanspruchs 1 auf.A solution to this problem shows a generic Backlash element with the characterizing features of the Patent claim 1.
Zweckmäßige und vorteilhafte Ausgestaltungen sind Gegenstand der Unteransprüche.Appropriate and advantageous embodiments are the subject the dependent claims.
Die Erfindung beruht auf dem allgemeinen Gedanken, den zwischen den ineinander verschiebbaren Bauelementen des Spielausgleichselementes an sich gegebenen Ringspalt als den das Druckraum-Einwegeventil überbrückenden Drosselkanal zu verwenden und diesen über einen Pufferraum zu leiten, dessen Volumen von der Höhe des Druckes innerhalb dieses Raumes abhängig ist. Die Abhängigkeit besteht derart, daß das Volumen unterhalb eines bestimmten Innendruckes einen Minimalwert einnimmt und bei einem darüber liegenden Druck größer wird. The invention is based on the general idea that between the telescoping components of the Play compensation element given ring gap as the the pressure chamber one-way valve bypassing throttle channel use and pass it over a buffer space whose Volume dependent on the amount of pressure within this room is. The dependence is such that the volume below a certain internal pressure a minimum value occupies and becomes larger at an overlying pressure.
Die Volumenvergrößerung erfolgt durch eine Vergrößerung des Pufferraumes unter Aufbau einer der Volumenvergrößerung proportional entgegengerichteten potentiellen Energie. Diese potentielle Energie bewirkt eine Volumenverkleinerung, sobald innerhalb des Pufferraumes ein Druckabbau stattfindet.The increase in volume takes place by an enlargement of the Buffer space under construction of a volume increase proportional opposite potential energy. These potential energy causes a volume reduction as soon as within the buffer space, a pressure reduction takes place.
Der Aufbau einer potentiellen Energie innerhalb einer Begrenzungswand des Pufferraumes bietet den Vorteil, daß das in diesem Raum bei geschlossenem zusätzlichen Absperrventil des Spielausgleichselementes gespeicherte Flüssigkeitsvolumen - eine Pufferraumvergrößerung ist ausschließlich bei einem geschlossenen zusätzlichen Absperrventil möglich - unter Abbau dieser Energie wieder abfließen kann. Ein solches Abfließen erfolgt beispielsweise bereits bei einem geschlossenen zusätzlichen Absperrventil, wenn das Spielausgleichselement keiner äußeren Einspannkraft ausgesetzt ist. Dann fließt das in dem Pufferraum gespeicherte Öl durch das Einwegeventil zurück in den Druckraum und bewirkt dadurch eine Einspannlängenvergrößerung. Wichtig ist hierfür allerdings, daß zwischen dem Pufferraum und dem Einwegeventil an dem Druckraum ein im wesentlichen ungedrosselter Strömungsweg zur Verfügung steht.The construction of a potential energy within a boundary wall the buffer space has the advantage that the in this room with additional shut-off valve closed the clearance compensation element stored liquid volume - A buffer space enlargement is exclusive to one Closed additional shut-off valve possible - under Degradation of this energy can drain again. Such a drain takes place, for example, already in a closed additional shut-off valve when the clearance compensation element no external clamping force is exposed. Then the oil stored in the buffer space flows through the one-way valve back into the pressure chamber and thereby causes a Einspannlängenvergrößerung. Important is this, however, that between the buffer space and the one-way valve to the Pressure chamber a substantially unthrottled flow path is available.
Der Pufferraum kann an einer beliebigen Stelle zwischen dem Drosselkanal und dem über das Einwegeventil mit dem Druckraum in Verbindung bringbaren Vorratsraum vorgesehen sein.The buffer space can be anywhere between the Throttling channel and the one-way valve with the pressure chamber be provided in connection storeroom.
Eine besonders vorteilhafte Anordnung läßt sich durch den Einsatz eines axial verschiebbaren Dichtringes innerhalb eines Ringraumes zwischen den beiden ineinander verschiebbaren Bauteilen des Spielausgleichselementes erreichen. Dabei sollte die Ringdichtung in einer radialen Ringspalterweiterung, die nicht mehr als Drosselkanal wirkt, angeordnet sein, um eine wirksame Pufferraumgröße erhalten zu können. Um in bzw. an der als verstellbare Begrenzungswand dienenden Ringdichtung bei einer Vergrößerung des Pufferraumvolumens die gewünschte potentielle Energie aufbauen zu können, ist die Ringdichtung von außen durch eine axial druckbeaufschlagend wirkende Feder belastet.A particularly advantageous arrangement can be through the Use of an axially displaceable sealing ring within a Annular space between the two nestable Achieve components of the clearance compensation element. there should the ring seal in a radial annular gap extension, which no longer acts as a throttle channel arranged to be able to obtain an effective buffer space size. To serve in or on the as adjustable boundary wall Ring seal at an enlargement of the buffer space volume being able to build the desired potential energy is the ring seal from the outside by an axial pressurizing acting spring loaded.
Ein vorteilhaftes Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt.An advantageous embodiment of the invention is in the drawing shown.
In dieser zeigen
- Fig. 1
- einen Längsschnitt durch ein Spielausgleichselement mit einem Pufferraum in einem Zustand mit geringst möglichem Volumen,
- Fig. 2
- das Spielausgleichselement nach Fig. 1 mit einem Pufferraum in einem Zustand mit einem gegenüber dem Minimalvolumen größeren Volumen.
- Fig. 1
- a longitudinal section through a clearance compensation element with a buffer space in a state with the lowest possible volume,
- Fig. 2
- the lash adjuster according to FIG. 1 with a buffer space in a state with a volume which is larger than the minimum volume.
In einem lediglich angedeuteten Maschinengehäuse 1 eines
nicht näher dargestellten Verbrennungsmotors ist in einer
Gehäusebohrung 2 ein Spielausgleichselement 3 in Bohrungslängsrichtung
verschiebbar eingesetzt. Das Spielausgleichselement
3 umfaßt als erstes Bauteil ein einseitig geschlossenes
Zylinderteil 4, in dem zwischen einem nicht gezeigten
Ventilstößel oder -schaft und einer optional vorgesehenen
Druckfeder 5 ein Kolbenteil 6 verschiebbar gehalten ist. Die
Druckfeder 5 ist an dem geschlossenen Bodenteil des Zylinderteils
4 und an einer stirnseitigen Wandung des Kolbenteils
6 abgestützt, wodurch Zylinder- und Kolbenteil 4, 6 in
entgegengesetzten Bewegungsrichtungen so vorgespannt sind,
daß einerseits das Zylinderteil 4 mit seinem geschlossenen
Bodenteil an einem nicht gezeigten Steuernocken und andererseits
das Kolbenteil 6 am Stößel oder Schaft des Gaswechselventiles
spielfrei anliegt.In a merely indicated machine housing 1 of a
not shown internal combustion engine is in one
Housing bore 2 a
Das Kolbenteil 6 schließt mit dem Zylinderteil 4 einen
Druckraum 7 ein, der mit Schmieröl aus einem im Kolbenteil 6
ausgebildeten Vorratsraum 8 gefüllt ist, das aus der Gehäusebohrung
zugeführt wird. Diese Zuführung ist in der Zeichnung
mit Strömungspfeilen angedeutet. Der Vorratsraum 8 ist
auf diese Weise ständig mit Schmieröl aus dem Schmierölkreislauf
des Verbrennungsmotors beaufschlagt.The
Um ein Rückströmen von Schmieröl aus dem Druckraum 7 in den
Vorratsraum 8 zu verhindern, ist ein zwischen diesen beiden
Räumen vorgesehener Verbindungskanal 9 durch ein druckraumseitig
angeordnetes, federbelastetes Einwegeventil 10 verschließbar.
Bei einem auftretenden Spiel im Ventiltrieb wird
das Kolbenteil 6 von der in dem Druckraum 7 liegenden Druckfeder
5 in Richtung der Stößelanlenkung verschoben. Durch
den dabei im Druckraum 7 auftretenden Druckabfall wird das
Einwegeventil 10 vom Druck des Schmieröls in dem Vorratsraum
8 aufgesteuert und Schmieröl in den Druckraum 7 nachgeschoben.
Ein solches dem Spielausgleich dienendes Aufpumpen des
Spielausgleichselementes 3 ist beispielsweise beim Motorbremsbetrieb
der Brennkraftmaschine unerwünscht. Deshalb ist
in dem Vorratsraum 8 ein zusätzliches Absperrventil 11 vorgesehen,
von dem aus die Nachstellfunktion des Spielausgleichselementes
3 abgeschaltet werden kann, indem die Verbindung
zwischen dem Druckraum 7 und dem Vorratsraum 8 unabhängig
von dem Einwegeventil 10 abgetrennt wird.To a backflow of lubricating oil from the
Das Absperrventil 11 besteht aus einem Ventilsitz 12, einer
zugeordneten Ventilkugel 13 sowie auf die Ventilkugel 13
einwirkenden Federn, nämlich einer ersten eine Öffnungsfunktion
bewirkenden Feder 14 und einer zweiten eine Verschlußfunktion
bewirkenden Feder 15. Die zweite Feder 15 wirkt auf
die Ventilkugel 13 lediglich indirekt über einen Steuerkolben
16. Die Lage dieses Steuerkolbens 16 wird von dem
Schmieröldruck innerhalb der Vorratskammer 8 bestimmt. Bei
vollständig anstehendem Schmieröldruck ist das Absperrventil
11 geöffnet. Dies entspricht dem normalen Motorbetrieb. Bei
Bremsbetrieb des Verbrennungsmotors wird der Schmieröldruck
soweit abgesenkt, daß das Absperrventil 11 schließt.The shut-off
Zwischen dem Druckraum 7 und dem Verbindungskanal 9 existiert
ein das Einwegeventil 11 überbrückender Drosselkanal,
der von dem Ringspalt 17 zwischen dem Zylinderteil 4 und dem
Kolbenteil 6 vorliegt. Der Ringspalt 17 mündet über eine
Verbindungsleitung 18 in den Verbindungskanal 9. In dem Bereich
des Überganges des Ringspaltes 7 in die Verbindungsleitung
18 ist in einem erweiterten Ringspaltbereich 19 ein
radial dichtender Dichtring 20 vorgesehen. Die radiale Dichtung
erfolgt zwischen dem Kolbenteil 6 einerseits und dem
Zylinderteil 4 andererseits. Innerhalb des erweiterten
Ringspaltbereiches 19 ist der Dichtring 20 axial verschiebbar
gelagert. An seinem axial von dem Druckraum 7 abgewandten
Ende ist der Dichtring 20 durch eine sich an dem Kolbenteil
6 abstützende Druckfeder 21 beaufschlagt.Between the
Die Druckkräfte der Federn 15 und 21, das heißt der Federn
des Absperrventiles 11 und des Dichtringes 20 sind derart
aufeinander abgestimmt, daß bei geschlossenem Absperrventil
11 durch den Ringspalt 17 aus dem Druckraum 7 ausströmendes
Schmieröl das Ventil 11 nicht öffnen, den Dichtring 20 zur
Ausbildung eines Pufferraumes 22 dagegen axial durch Spannen
der Feder 21 verschieben kann.The compressive forces of the
In dem Pufferraum 22 gespeichertes Schmieröl kann durch die
potentielle Federenergie, die bei einem vergrößerten Pufferraum
22 auf den Dichtring 20 einwirkt, bei geschlossenem Absperrventil
11 durch das Einwegeventil 20 in den Druckraum 7
zurückströmen und dadurch eine in bestimmten Zuständen gewünschte
Einspannlängenvergrößerung bewirken. Ein Betriebszustand,
in dem eine solche Einspannlängenvergrößerung gewünscht
sein kann, liegt beispielsweise vor, wenn ein Verbrennungsmotor
im Motorbremsbetrieb bei einem geöffneten Ladungswechselventil
abgestellt wird. In diesem Fall steht das
Spielausgleichselement im Motorstillstand unter einer eine
Einspannlängenverkürzung bewirkenden Vorspannung. Aus einem
solchen Zustand muß bei einem Anlassen des Verbrennungsmotors
die Einspannlänge möglichst rasch auf eine für diesen
Betrieb maßgebliche größere Einspannlänge vergrößert werden.
In diesem Fall kann durch Rückführung von Schmieröl aus dem
Pufferraum 22 diese Längenvergrößerung bereits bei noch
nicht durch den Schmieröldruck des Verbrennungsmotors geöffnetem
Absperrventil 11 erfolgen. Dies ist ein besonderer
Vorteil der erfindungsgemäßen Ausbildung eines Spielausgleichselementes.
Im praktischen Betrieb hat sich nämlich
gezeigt, daß es bei einem Anlassen eines Motors einige Zeit
dauert, bis ein ausreichend hoher Schmieröldruck zum Öffnen
des Absperrventiles 11 aufgebaut ist.In the
Das Minimalvolumen des Pufferraumes 22 kann im Extremfall
Null sein.The minimum volume of the
Claims (7)
- A hydraulic clearance compensation element for a valve train of an internal combustion engine, comprising opposite clamping regions and pressurisation by lubricating oil, in whichcharacterised in thata first and a second component (4, 6), each serving as a clamping element, are held so as to be slidable into each other;the two components (4, 6) between themselves enclose a pressure chamber, tight to the outside, comprising a volume which depends on the mutual position of the two components (4, 6);the pressure chamber (7) can be pressurised by lubricating oil which flows through a supply chamber (8) and is subjected to the lubricating oil pressure;the pressure chamber (7) can be connected to the supply chamber (8) via a spring-loaded one-way valve (10) through which liquid can only flow into said pressure chamber (7);in the connection between the pressure chamber (7) and the supply chamber (8) an additional controllable check valve (11) is provided;between the pressure chamber (7) and the controllable check valve (11) a throttling channel is provided which serves as a bypass to the one-way valve (10);
the throttling channel is connected to a buffer space (22) whose volume can be changed, wherein the volume, at an internal pressure of the buffer space (22) which is below a specifiable value, assumes a predetermined minimum value, while when a lubricating oil volume flow is acting on the buffer space (22) above this pressure, said volume increases in a volume-proportional manner while building up a potential energy which is acting towards a reversible volume decrease. - The clearance compensation element according to claim 1,
characterised in that
the buffer space (22) comprises a delimiting wall (20) which can be adjusted against an elastic initial tension, with the position of said delimiting wall (20) determining the size of the volume of the buffer space (22). - The clearance compensation element according to claim 1 or 2,
characterised in that
the flow path situated between the buffer space (22) and the one-way valve (10) of the pressure chamber (7) is non-throttled. - The clearance compensation element according to any one of the preceding claims,
characterised in that
the throttling channel is formed by an annular gap (17) which exists between the components (4, 6) that can be slid into each other and a sealing ring (20) which serves as an adjustable delimiting wall, said annular gap (17) being sealed off towards the outside. - The clearance compensation element according to any one of the preceding claims,
characterised in that
the sealing ring (20) is held so as to be axially slidable and spring loaded in its direction of displacement from outside the sealed annular gap (17), in a way which acts so as to shorten the annular gap. - The clearance compensation element according to any one of the preceding claims,
characterised in that
within the possible sliding path of the sealing ring (20) the annular gap (17) is radially enlarged. - The clearance compensation element according to any one of the preceding claims,
characterised in that
in a position which corresponds to the minimal buffer space volume, the sealing ring (20) rests against an end stop.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10129729A DE10129729A1 (en) | 2001-06-20 | 2001-06-20 | Hydraulic lash adjuster for a valve train of an internal combustion engine |
| DE10129729 | 2001-06-20 | ||
| PCT/DE2002/002248 WO2003001037A1 (en) | 2001-06-20 | 2002-06-20 | Hydraulic play compensation element for a valve gear of an internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1397581A1 EP1397581A1 (en) | 2004-03-17 |
| EP1397581B1 true EP1397581B1 (en) | 2005-08-17 |
Family
ID=7688827
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02747227A Expired - Lifetime EP1397581B1 (en) | 2001-06-20 | 2002-06-20 | Hydraulic play compensation element for a valve gear of an internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US6718923B2 (en) |
| EP (1) | EP1397581B1 (en) |
| DE (2) | DE10129729A1 (en) |
| WO (1) | WO2003001037A1 (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT500679B8 (en) * | 2004-06-16 | 2007-02-15 | Ge Jenbacher Gmbh & Co Ohg | VALVE DRIVE |
| DE102005029831A1 (en) * | 2004-07-23 | 2006-03-16 | Ina-Schaeffler Kg | Hydraulic valve-lash-adjusting element for engine valve train, has valve shutter virtually stationary within piston which is moved relative to shutter to control upper and lower ports in piston |
| US7389757B2 (en) * | 2004-12-29 | 2008-06-24 | Schaeffler Kg | Force-transmitting arrangement for a valve train of an internal-combustion engine |
| US7246584B2 (en) * | 2004-12-29 | 2007-07-24 | Schaeffler Kg | Force-transmitting arrangement for a valve train of an internal-combustion engine |
| DE102006031706A1 (en) * | 2006-07-08 | 2008-01-10 | Daimlerchrysler Ag | Valve play element for compensating for play in an internal combustion engine's valves has a piston assigned with a pressurized space, a reservoir for a hydraulic substance and an adjusting element in the pressurized space |
| DE102007014248A1 (en) * | 2007-03-24 | 2008-09-25 | Schaeffler Kg | Reciprocating internal combustion engine with engine braking device |
| DE102007014250A1 (en) * | 2007-03-24 | 2008-09-25 | Schaeffler Kg | Internal combustion engine with engine brake |
| DE102007051302A1 (en) * | 2007-10-26 | 2009-04-30 | Schaeffler Kg | Reciprocating internal combustion engine with engine brake and additional opening of an exhaust valve |
| GB2503705A (en) * | 2012-07-05 | 2014-01-08 | Eaton Srl | Hydraulic Lash Adjuster and Lost Motion System |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| BR7601046A (en) | 1975-02-18 | 1976-09-14 | Eaton Corp | HYDRAULIC SLACK ADJUSTER FOR VALVE CONTROL OF AN INTERNAL COMBUSTION ENGINE |
| DE2517370A1 (en) | 1975-04-19 | 1976-10-28 | Volkswagenwerk Ag | Hydraulic clearance compensating device for IC engine valves - has hydraulic medium filled pre-chamber sealed with elastic membrane |
| US4407241A (en) * | 1980-12-31 | 1983-10-04 | Cummins Engine Company, Inc. | Expandable hydraulic tappet with a variable exit valve |
| US4462364A (en) | 1981-09-17 | 1984-07-31 | Aisin Seiki Kabushiki Kaisha | Hydraulic lash adjuster |
| JPH01253515A (en) * | 1987-11-19 | 1989-10-09 | Honda Motor Co Ltd | Valve system for internal combustion engine |
| JPH01134018A (en) * | 1987-11-19 | 1989-05-26 | Honda Motor Co Ltd | Valve system for internal combustion engine |
| DE3800945C1 (en) | 1988-01-15 | 1989-02-16 | Daimler-Benz Ag, 7000 Stuttgart, De | |
| US4977867A (en) * | 1989-08-28 | 1990-12-18 | Rhoads Jack L | Self-adjusting variable duration hydraulic lifter |
| DE4324837A1 (en) * | 1993-07-23 | 1995-01-26 | Schaeffler Waelzlager Kg | Device for adjustment of the valve lift and valve timings of an inlet and exhaust valve |
| DE19818893A1 (en) * | 1998-04-28 | 1999-11-04 | Mwp Mahle J Wizemann Pleuco Gm | Hydraulic valve lash adjuster |
| DE10010597A1 (en) | 2000-03-03 | 2001-09-06 | Mahle Ventiltrieb Gmbh | Hydraulic tappet clearance compensation element esp. for gas exchange valve control in IC engines has volume-varying adjuster piston sealed via sliding seal ring |
-
2001
- 2001-06-20 DE DE10129729A patent/DE10129729A1/en not_active Withdrawn
-
2002
- 2002-06-20 EP EP02747227A patent/EP1397581B1/en not_active Expired - Lifetime
- 2002-06-20 DE DE50203966T patent/DE50203966D1/en not_active Expired - Lifetime
- 2002-06-20 WO PCT/DE2002/002248 patent/WO2003001037A1/en active IP Right Grant
- 2002-06-20 US US10/343,724 patent/US6718923B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| EP1397581A1 (en) | 2004-03-17 |
| US6718923B2 (en) | 2004-04-13 |
| DE50203966D1 (en) | 2005-09-22 |
| US20030192498A1 (en) | 2003-10-16 |
| DE10129729A1 (en) | 2003-01-23 |
| WO2003001037A1 (en) | 2003-01-03 |
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