EP1075589A1 - Hydraulic valve-play compensation element - Google Patents
Hydraulic valve-play compensation elementInfo
- Publication number
- EP1075589A1 EP1075589A1 EP99919221A EP99919221A EP1075589A1 EP 1075589 A1 EP1075589 A1 EP 1075589A1 EP 99919221 A EP99919221 A EP 99919221A EP 99919221 A EP99919221 A EP 99919221A EP 1075589 A1 EP1075589 A1 EP 1075589A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- pressure
- cylinder part
- lash adjuster
- piston
- 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
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
- 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
- F01L1/245—Hydraulic tappets
Definitions
- the invention relates to a hydraulic valve lash adjuster (HVA) according to the preamble of claims 1 and 2.
- HVA hydraulic valve lash adjuster
- valve lash adjuster is known from DE-OS 38 19 927.
- There is an additional check valve is provided in a conventional hydraulic valve lash adjuster element, which is to prevent the oil-filled reservoir located in front of the high-pressure chamber from being emptied when the engine is at a standstill.
- this does not prevent the oil filling of the working or high-pressure chamber from decreasing as a result of the leakage oil passing between the cylinder part and the piston part, and the length compensation element correspondingly shortening, as long as the lash adjuster element is loaded by the cam of the camshaft when the valve is at a standstill. This is undesirable in the idle state, since it leads to increased valve play during the subsequent starting process.
- HVA is known from EP 324085.
- the readjusting function of the HVA is to be be switched.
- the HVA has a sealed high-pressure chamber and a capillary overflow hole - through which "leakage oil" can flow out to ensure a decrease in length of the HVA.
- a valve body actuated by a piston is pressed into the valve seat. Both the inlet to the high-pressure chamber and the opening of the capillary overflow bore in the valve seat surface are closed.
- the opening of the capillary overflow bore directly into the seat of the valve is supposed to prevent the pressure in the high-pressure chamber from acting on the valve body as a whole and thus opening the valve.
- the invention is concerned with the problem of creating a hydraulic valve lash compensation element which does not change the set length in the idle state even under the application of high forces.
- This problem is solved by a hydraulic valve lash adjuster according to claim 1 or 2.
- Advantageous further developments are the subject of the dependent claims.
- a conventional valve lash adjuster was used for claim 1, and the valve lash adjuster known from DE-OS 38 19 927 for claim 2.
- the basic idea of the invention is to prevent the leakage oil loss which occurs in hydraulic valve lash compensation elements and is necessary for the function and which occurs between the cylinder part and the piston part when the engine is at a standstill. According to the exemplary embodiment, this takes place in that the leakage oil is introduced into the space which lies between the check valve of the high-pressure space and a second valve. This leads to a self-reinforcing sealing function of the second valve when the engine is stopped. The prerequisite for this is that the leakage oil cannot flow away in any other way. That is why the gap is between Particularly seal the cylinder part and piston part of the play compensation element beyond the overflow bore, e.g. B. by particularly tight play or a special seal.
- Fig. 1 an inventive valve lash adjuster.
- the valve clearance compensation element consists of a cylinder part 1 and a piston part 2, which are braced against one another by a spring 3.
- the relative movement of cylinder part 1 and piston part 2 is limited by a spring ring 8.
- the oil is supplied through the feed bore 19 in the pressure piece 7.
- the spring 3 lies in a high-pressure or working space 20 formed between the cylinder part 1 and the piston part 2, which is formed by a check valve 4 - consisting of a valve closing part 11, a valve spring 12 and a valve cage 13 - is sealed.
- the valve lash adjuster corresponds to the conventional design.
- a second valve 5 which has a valve cage 10 with an integrated valve spring and a closure part 9.
- the closure part 9 can be lifted against the pressure of the valve spring by an actuating piston 6 from the valve seat.
- the actuating piston 6 has a larger effective area for the oil pressure present on its upper side than on its underside.
- the resulting force on the piston 6 is available for the opening function of the valve and is transmitted to the closure part 9 via the surface 16.
- the leakage oil escaping between piston part 2 and actuating piston 6 flows through the relief bore 14 without pressure from the HVA.
- the piston 6 has a bore through which oil can flow from the storage space 19 via the storage space 18 and the space 17 between the valves into the high-pressure space 20.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
The invention relates to a hydraulic valve-play compensation element. The aim is to prevent any change in the length from taking place when the engine is at a standstill. To this end, the leakage oil is guided into the space between the high pressure valve (4) and the valve (5), where it then reinforces the sealing effect of said valve (5). When the engine is in operation, the valve (4) is kept open irrespective of the direction of throughflow by means for producing a defined force, for example a pressure-loaded piston or by electromagnetic means.
Description
Hydraulisches Ventilspielausgleichselement Hydraulic valve lash adjuster
Die Erfindung betrifft ein hydraulisches Ventilspielaus- gleichselement (HVA) nach dem Oberbegriff der Patentansprüche 1 bzw. 2. Bei hydraulischen Spielausgleichselementen erfolgt das Nachstellen bzw. eine Längenzunahme bei vorhandenem Spiel durch den Schmieröldruck, eine Längenabnahme aufgrund eines kleinen Leckageölstroms in Verbindung mit dem das Ausgleichselement zusammenpressenden Nocken der Nockenwelle .The invention relates to a hydraulic valve lash adjuster (HVA) according to the preamble of claims 1 and 2. With hydraulic lash adjusters, the adjustment or length increase takes place with play due to the lubricating oil pressure, a decrease in length due to a small leakage oil flow in connection with the compensation element compressing cam of the camshaft.
Ein derartiges Ventilspielausgleichselement ist aus der DE- OS 38 19 927 bekannt. Dort ist bei einem üblichen hydraulischen Ventilspielausgleichselement ein zusätzliches Rückschlagventil vorgesehen, das bei Motorstillstand eine Entleerung des vor dem Hochdruckraum liegenden ölbefüllten Vorratsraums verhindern soll. Dabei wird jedoch nicht verhindert, daß, solange das Spielausgleichselement bei geöffnetem Ventil im Motorstillstand durch den Nocken der Nokkenwelle belastet ist, die Ölfüllung des Arbeits- bzw. Hochdruckraums infolge des zwischen Zylinderteil und Kolbenteil durchtretenden Leckageöls abnimmt und das Spielausgleichselement dementsprechend seine Länge verkürzt. Dies ist im Ruhezustand unerwünscht, da es beim nachfolgenden Startvorgang zu erhöhtem Ventilspiel führt.Such a valve lash adjuster is known from DE-OS 38 19 927. There is an additional check valve is provided in a conventional hydraulic valve lash adjuster element, which is to prevent the oil-filled reservoir located in front of the high-pressure chamber from being emptied when the engine is at a standstill. However, this does not prevent the oil filling of the working or high-pressure chamber from decreasing as a result of the leakage oil passing between the cylinder part and the piston part, and the length compensation element correspondingly shortening, as long as the lash adjuster element is loaded by the cam of the camshaft when the valve is at a standstill. This is undesirable in the idle state, since it leads to increased valve play during the subsequent starting process.
Ein weiteres HVA ist aus der EP 324085 bekannt. Dort soll im Motorbremsbetrieb die Nachstellfunktion des HVA ausge-
schaltet sein. Hierfür weist das HVA einen abgedichteten Hochdruckraum und eine kapillare Überströmbohrung - über die "Leckageöl" zur Gewährleistung einer Längenabnahme des HVA abströmen kann - auf . Im Motorbremsbetrieb wird ein von einem Kolben betätigter Ventilkörper in den Ventilsitz gedrückt. Dabei wird sowohl der Zulauf zum Hochdruckraum als auch die in der Ventilsitzfläche liegende Öffnung der kapillaren Überströmbohrung verschlossen. Durch die Einmündung der kapillaren Überströmbohrung direkt in die Sitzfläche des Ventils soll vermutlich verhindert werden, daß der im Hochdruckraum wirksame Druck auch auf den Ventilkörper insgesamt einwirkt und so das Ventil öffnet. Ob dieses Ziel erreicht wird, erscheint jedoch unsicher.Another HVA is known from EP 324085. There, the readjusting function of the HVA is to be be switched. For this purpose, the HVA has a sealed high-pressure chamber and a capillary overflow hole - through which "leakage oil" can flow out to ensure a decrease in length of the HVA. In engine braking mode, a valve body actuated by a piston is pressed into the valve seat. Both the inlet to the high-pressure chamber and the opening of the capillary overflow bore in the valve seat surface are closed. The opening of the capillary overflow bore directly into the seat of the valve is supposed to prevent the pressure in the high-pressure chamber from acting on the valve body as a whole and thus opening the valve. However, it seems uncertain whether this goal will be achieved.
Die Erfindung beschäftigt sich mit dem Problem, ein hydraulisches Ventilspielausgleichselement zu schaffen, das im Ruhezustand auch unter hoher Krafteinwirkung die eingestellte Länge nicht verändert. Dieses Problem wird gelöst durch ein hydraulisches Ventilspielausgleichselement nach Anspruch 1 oder 2. Vorteilhafte Weiterbildungen sind Gegenstand der Unteransprüche. Zur Bildung der Gattung wurde für Anspruch 1 ein konventionelles Ventilspielausgleichselement herangezogen, für Anspruch 2 das aus der DE-OS 38 19 927 bekannte Ventilspielausgleichselement .The invention is concerned with the problem of creating a hydraulic valve lash compensation element which does not change the set length in the idle state even under the application of high forces. This problem is solved by a hydraulic valve lash adjuster according to claim 1 or 2. Advantageous further developments are the subject of the dependent claims. To form the genus, a conventional valve lash adjuster was used for claim 1, and the valve lash adjuster known from DE-OS 38 19 927 for claim 2.
Grundgedanke der Erfindung ist es, den bei hydraulischen Ventilspielausgleichselementen vorhandenen, für die Funktion notwendigen Leckageölverlust, der zwischen dem Zylinderteil und dem Kolbenteil auftritt, bei Motorstillstand zu verhindern. Dies erfolgt gemäß Ausführungsbeispiel dadurch, daß das Leckageöl in den Raum eingeleitet wird, der zwischen dem Rückschlagventil des Hochdruckraums und einem zweiten Ventil liegt. Dies führt bei Motorstillstand zu einer selbstverstärkenden Dichtfunktion des zweiten Ventils. Voraussetzung hierfür ist, daß das Leckageöl nicht auf anderem Weg abfließen kann. Deshalb ist der Spalt zwischen
Zylinderteil und Kolbenteil des Spielausgleichselements jenseits der Überströmbohrung besonders abzudichten, z. B. durch besonders enge Spielgebung oder eine besondere Dichtung.The basic idea of the invention is to prevent the leakage oil loss which occurs in hydraulic valve lash compensation elements and is necessary for the function and which occurs between the cylinder part and the piston part when the engine is at a standstill. According to the exemplary embodiment, this takes place in that the leakage oil is introduced into the space which lies between the check valve of the high-pressure space and a second valve. This leads to a self-reinforcing sealing function of the second valve when the engine is stopped. The prerequisite for this is that the leakage oil cannot flow away in any other way. That is why the gap is between Particularly seal the cylinder part and piston part of the play compensation element beyond the overflow bore, e.g. B. by particularly tight play or a special seal.
Da die Spielausgleichsfunktion durch Schaffung eines abgedichteten Raums, aus dem das Leckageöl nicht entweichen kann, behindert würde, muß für den Motorbetrieb gewährleistet werden, daß das Leckageöl entweichen kann. Dies erfolgt erfindungsgemäß dadurch, daß das zweite, versorgungs- seitige Ventil durch einen von einer definierten Kraft betätigten Kolben im Motorbetrieb geöffnet und offengehalten wird.Since the play compensation function would be hindered by the creation of a sealed space from which the leakage oil cannot escape, it must be ensured for the engine operation that the leakage oil can escape. This takes place according to the invention in that the second valve on the supply side is opened and kept open during engine operation by a piston actuated by a defined force.
Durch die Ausbildung des Betätigungskolbens gemäß Anspruch 4 als vom Schmieröl durchströmtes Bauteil läßt sich, verglichen mit dem in der EP 324085 dargestellten HVA, eine platzsparende Ausführung erzielen.By designing the actuating piston as a component through which the lubricating oil flows, a space-saving design can be achieved compared to the HVA shown in EP 324085.
Die Erfindung wird im folgenden anhand eines Ausführungsbeispiels beschrieben. Es zeigt:The invention is described below using an exemplary embodiment. It shows:
Fig. 1 ein erfindungsgemäßes Ventilspielausgleichselement .Fig. 1 an inventive valve lash adjuster.
Das Ventilspielausgleichselement besteht aus einem Zylinderteil 1 und einem Kolbenteil 2 , die durch eine Feder 3 gegeneinander verspannt sind. Dabei ist die Relativbewegung von Zylinderteil 1 und Kolbenteil 2 durch einen Federring 8 begrenzt. Die Ölzufuhr erfolgt durch die Zuleitungsbohrung 19 im Druckstück 7.The valve clearance compensation element consists of a cylinder part 1 and a piston part 2, which are braced against one another by a spring 3. The relative movement of cylinder part 1 and piston part 2 is limited by a spring ring 8. The oil is supplied through the feed bore 19 in the pressure piece 7.
Die Feder 3 liegt in einem zwischen Zylinderteil 1 und Kolbenteil 2 gebildeten Hochdruck- bzw. Arbeitsraum 20, der durch ein Rückschlagventil 4 - bestehend aus einem Ver-
schlußteil 11, einer Ventilfeder 12 und einem Ventilkäfig 13 - abgedichtet ist. Insoweit entspricht das Ventilspielausgleichselement der konventionellen Bauart.The spring 3 lies in a high-pressure or working space 20 formed between the cylinder part 1 and the piston part 2, which is formed by a check valve 4 - consisting of a valve closing part 11, a valve spring 12 and a valve cage 13 - is sealed. In this respect, the valve lash adjuster corresponds to the conventional design.
In Strömungsrichtung vor dem Rückschlagventil 4 liegt ein zweites Ventil 5, das einen Ventilkäfig 10 mit integrierter Ventilfeder und ein Verschlußteil 9 aufweist.In the flow direction upstream of the check valve 4 there is a second valve 5 which has a valve cage 10 with an integrated valve spring and a closure part 9.
Das Verschlußteil 9 kann gegen den Druck der Ventilfeder durch einen Betätigungskolben 6 aus dem Ventilsitz gehoben werden. Der Betätigungskolben 6 weist auf seiner Oberseite eine größere Wirkfläche für den anstehenden Öldruck auf als an seiner Unterseite. Die hieraus resultierende Kraft auf den Kolben 6 steht für die Öffnungsfunktion des Ventils zur Verfügung und wird über die Fläche 16 auf das Verschlußteil 9 übertragen. Das zwischen Kolbenteil 2 und Betätigungskolben 6 entweichende Leckageöl strömt durch die Entlastungsbohrung 14 drucklos aus dem HVA.The closure part 9 can be lifted against the pressure of the valve spring by an actuating piston 6 from the valve seat. The actuating piston 6 has a larger effective area for the oil pressure present on its upper side than on its underside. The resulting force on the piston 6 is available for the opening function of the valve and is transmitted to the closure part 9 via the surface 16. The leakage oil escaping between piston part 2 and actuating piston 6 flows through the relief bore 14 without pressure from the HVA.
Der Kolben 6 weist eine Bohrung auf, über die Öl vom Vorratsraum 19 über den Vorratsraum 18 und den zwischen den Ventilen liegenden Raum 17 in den Hochdruckraum 20 strömen kann.The piston 6 has a bore through which oil can flow from the storage space 19 via the storage space 18 and the space 17 between the valves into the high-pressure space 20.
Das unter bestimmten Umständen wie z. B. bei von der Nokkenwelle betätigtem Ventil auch im Motorstillstand zwischen dem Zylinderteil 1 und dem Kolbenteil 2 abfließende Leckageöl wird über eine Überströmbohrung 21 dem zwischen den Ventilen 4 und 5 liegenden Raum 17 zugeführt und wirkt bei geschlossenem Ventil 5 verstärkend auf dessen Dichtfunktion. Um einen Druckverlust im Raum 17 weitgehend zu verhindern, ist eine Ringdichtung 15 zwischen Zylinderteil 1 und Kolbenteil 2 vorgesehen.
The under certain circumstances such. B. When the valve is actuated by the camshaft even when the engine is at a standstill between the cylinder part 1 and the piston part 2, leakage oil is supplied via an overflow bore 21 to the space 17 between the valves 4 and 5 and, when the valve 5 is closed, has a reinforcing effect on its sealing function. In order to largely prevent a pressure loss in space 17, an annular seal 15 is provided between cylinder part 1 and piston part 2.
Claims
Hydraulisches Ventilspielausgleichselement für einen Verbrennungsmotor mit einem Zylinderteil (1) und einem im Zylinderteil verschiebbaren Kolbenteil (2), wobei Zylinderteil (1) und Kolbenteil (2) gegeneinander durch eine Feder (3) vorgespannt sind und einen Hochdruckraum (20) einschließen, der durch ein hochdruckseitiges Rückschlagventil (4) abgeschlossen ist und wobei im Ringspalt zwischen Kolbenteil (2) und Zylinderteil (1) Leckageöl aus dem Hochdruckraum (20) abfließen kann, gekennzeichnet durch die MerkmaleHydraulic valve lash adjuster for an internal combustion engine with a cylinder part (1) and a piston part (2) displaceable in the cylinder part, the cylinder part (1) and piston part (2) being biased against each other by a spring (3) and enclosing a high-pressure chamber (20) through a non-return valve (4) on the high-pressure side is closed and leakage oil can flow out of the high-pressure chamber (20) in the annular gap between the piston part (2) and the cylinder part (1), characterized by the features
a) das Leckageöl wird in einen bei Motorstillstand durch ein zweites Ventil (5) abgedichteten Raum (17) geführt und verstärkt dort durch Druckaufbau die Dichtwirkung des Ventils (5),a) the leakage oil is led into a space (17) sealed by a second valve (5) when the engine is at a standstill and increases the sealing effect of the valve (5) there by pressure build-up,
b) durch den Druckaufbau im abgedichteten Raum (17) wird ein weiteres Abströmen des Leckageöls aus dem Hochdruckraum (20) weitgehend verhindert .b) the pressure build-up in the sealed space (17) largely prevents the leakage oil from flowing out of the high-pressure space (20).
Hydraulisches Ventilspielausgleichselement für einen Verbrennungsmotor mit einem Zylinderteil (1) und einem im Zylinderteil verschiebbaren Kolbenteil (2), wobei Zylinderteil (1) und Kolbenteil (2) gegeneinander durch eine Feder (3) vorgespannt sind und einen Hochdruckraum (20) einschließen, der durch ein hochdruckseitiges Rückschlagventil (4) abgeschlossen ist, und mit einem zweiten, in Ölzufuhrrichtung vor dem Rückschlagventil (4) liegenden, versorgungsseitigen Ventil (5), wobei das versorgungsseitige Ventil (5) bei Motorstillstand
durch eine Rückstellfeder (10) geschlossen ist, dadurch gekennzeichnet, daß das bei geschlossenem Rückschlagventil (4) aus dem Hochdruckraum (20) abfließende Leckageöl in den Raum (17) zwischen Rückschlagventil (4) und Ventil (5) geführt wird und dort die Dichtwirkung des Ventils (5) im Motorstillstand verstärkt, daß das Ventil (5) im Motorbetrieb durch Mittel zur Erzeugung einer definierten Kraft in Zuströmrichtung geöffnet wird und daß das Ventil (5) im Motorbetrieb unabhängig von der Durchströmungsrichtung des Schmieröls durch die Mittel zur Erzeugung der definierten Kraft in der geöffneten Stellung gehalten ist.Hydraulic valve lash adjuster for an internal combustion engine with a cylinder part (1) and a piston part (2) displaceable in the cylinder part, the cylinder part (1) and piston part (2) being biased against each other by a spring (3) and enclosing a high-pressure chamber (20) through a check valve (4) on the high-pressure side is closed, and with a second supply-side valve (5), which is upstream of the check valve (4) in the oil supply direction, the supply-side valve (5) when the engine is at a standstill is closed by a return spring (10), characterized in that the leakage oil flowing out of the high-pressure chamber (20) when the check valve (4) is closed is guided into the space (17) between the check valve (4) and valve (5) and there the sealing effect of the valve (5) when the engine is at a standstill, that the valve (5) is opened in the motor mode by means of generating a defined force in the inflow direction and that the valve (5) in the motor mode is independent of the direction of flow of the lubricating oil by the means for generating the defined one Force is held in the open position.
3. Hydraulisches Ventilspielausgleichselement nach Anspruch 1 oder 2 , dadurch gekennzeichnet, daß die Kraft zum Öffnen des Ventils (5) eine vom Schmieröldruck erzeugte Kraft eines Betätigungskolbens (6) ist.3. Hydraulic valve lash adjuster according to claim 1 or 2, characterized in that the force for opening the valve (5) is a force generated by the lubricating oil pressure of an actuating piston (6).
4. Hydraulisches Ventilspielausgleichselement nach Anspruch 2 , dadurch gekennzeichne , daß der Schmieröldruck beidseitig des Betätigungskolbens (6) anliegt und die Kraft zum Öffnen des Ventils (5) aufgrund unterschiedlicher Wirkflächen entsteht.4. Hydraulic valve clearance compensation element according to claim 2, characterized in that the lubricating oil pressure is present on both sides of the actuating piston (6) and the force for opening the valve (5) arises due to different active surfaces.
5. Hydraulisches Ventilspielausgleichselement nach Anspruch 3, dadurch gekennzeichnet, daß der Betätigungskolben (6) durchströmt ist.
Hydraulisches Ventilspielausgleichselement nach Anspruch 1, dadurch gekennzeichnet, daß die Kraft zum Öffnen des Ventils (5) eine elektromagnetisch erzeugte Betätigungskraft ist.5. Hydraulic valve lash adjuster according to claim 3, characterized in that the actuating piston (6) is flowed through. Hydraulic valve lash adjuster according to claim 1, characterized in that the force for opening the valve (5) is an electromagnetically generated actuating force.
Hydraulisches Ventilspielausgleichselement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zwischen dem Hochdruckraum (20) und dem zwischen den Ventilen (4) und (5) liegenden Raum eine kapillareHydraulic valve lash adjuster according to one of the preceding claims, characterized in that between the high pressure space (20) and the space between the valves (4) and (5) there is a capillary
Überströmbohrung angeordnet ist.Overflow hole is arranged.
Hydraulisches Ventilspielausgleichselement nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zwischen Zylinderteil (1) und Kolbenteil (2) mindestens ein Dichtring (15) angeordnet ist.
Hydraulic valve lash adjuster according to one of the preceding claims, characterized in that at least one sealing ring (15) is arranged between the cylinder part (1) and the piston part (2).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19818893 | 1998-04-28 | ||
| DE19818893A DE19818893A1 (en) | 1998-04-28 | 1998-04-28 | Hydraulic valve lash adjuster |
| PCT/EP1999/002402 WO1999056007A1 (en) | 1998-04-28 | 1999-04-09 | Hydraulic valve-play compensation element |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1075589A1 true EP1075589A1 (en) | 2001-02-14 |
| EP1075589B1 EP1075589B1 (en) | 2002-07-31 |
Family
ID=7866007
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99919221A Expired - Lifetime EP1075589B1 (en) | 1998-04-28 | 1999-04-09 | Hydraulic valve-play compensation element |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US6318325B1 (en) |
| EP (1) | EP1075589B1 (en) |
| DE (2) | DE19818893A1 (en) |
| WO (1) | WO1999056007A1 (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10012225A1 (en) | 2000-03-14 | 2001-09-20 | Mahle Ventiltrieb Gmbh | Hydraulic play compensation element to control gas exchange valve of internal combustion engine; has opposite clamp areas with moving parts to determine volume of pressure chamber between them |
| DE10031802B4 (en) * | 2000-07-04 | 2007-11-15 | Daimlerchrysler Ag | Hydraulic actuator |
| DE10129729A1 (en) * | 2001-06-20 | 2003-01-23 | Mahle Ventiltrieb Gmbh | Hydraulic lash adjuster for a valve train of an internal combustion engine |
| DE10143012A1 (en) * | 2001-09-03 | 2003-03-20 | Daimler Chrysler Ag | Engine charging valve play compensator has mutually sealed hollow cylinder parts forming pressure space with outwards link via spring-loaded valve |
| DE10231110A1 (en) | 2002-07-10 | 2004-01-29 | Daimlerchrysler Ag | Device for operating a hydraulically operated valve clearance compensation element of an internal combustion engine |
| DE10236492A1 (en) * | 2002-08-09 | 2004-02-19 | Daimlerchrysler Ag | Hydraulic play equalizing element for controlling gas exchange valve has both displaceable parts temporarily lockable to each other |
| US7273026B2 (en) * | 2002-10-18 | 2007-09-25 | Maclean-Fogg Company | Roller follower body |
| US6871622B2 (en) * | 2002-10-18 | 2005-03-29 | Maclean-Fogg Company | Leakdown plunger |
| 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 |
| 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 |
| DE102010018208A1 (en) * | 2010-04-26 | 2011-10-27 | Schaeffler Technologies Gmbh & Co. Kg | Hydraulic valve clearance compensation element for reciprocating internal combustion engines |
| DE102011005575A1 (en) * | 2011-03-15 | 2012-09-20 | Schaeffler Technologies Gmbh & Co. Kg | Valve gear with additional lift in the cam base circle |
| US9109468B2 (en) * | 2012-01-06 | 2015-08-18 | Scuderi Group, Llc | Lost-motion variable valve actuation system |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1236857B (en) | 1963-05-15 | 1967-03-16 | Richard Kuechen | Hydraulic valve lash adjuster for internal combustion engines |
| US4633827A (en) * | 1985-10-07 | 1987-01-06 | Eaton Corporation | Hydraulic lash adjuster with combined reservoir extension and metering system |
| GB2185549B (en) * | 1985-10-15 | 1990-01-24 | Honda Motor Co Ltd | Hydraulic lash adjuster for use in a valve operating mechanism |
| DE3819927A1 (en) * | 1987-06-22 | 1989-01-05 | Volkswagen Ag | Hydraulic valve clearance adjusting element |
| DE3800945C1 (en) * | 1988-01-15 | 1989-02-16 | Daimler-Benz Ag, 7000 Stuttgart, De | |
| JPH01232103A (en) | 1988-03-12 | 1989-09-18 | Mazda Motor Corp | Valve driving device for engine |
| US4977867A (en) * | 1989-08-28 | 1990-12-18 | Rhoads Jack L | Self-adjusting variable duration hydraulic lifter |
| DE4225012C1 (en) * | 1992-07-29 | 1993-07-15 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | Hydraulic actuator for lifting valve with pressurised oil piston - has play compensation piston, located between working piston and valve, and loaded by compression spring |
| DE9318108U1 (en) | 1993-11-26 | 1994-01-20 | INA Wälzlager Schaeffler KG, 91074 Herzogenaurach | Pestle |
-
1998
- 1998-04-28 DE DE19818893A patent/DE19818893A1/en not_active Withdrawn
-
1999
- 1999-04-09 WO PCT/EP1999/002402 patent/WO1999056007A1/en active IP Right Grant
- 1999-04-09 DE DE59902193T patent/DE59902193D1/en not_active Expired - Lifetime
- 1999-04-09 US US09/673,469 patent/US6318325B1/en not_active Expired - Lifetime
- 1999-04-09 EP EP99919221A patent/EP1075589B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
| Title |
|---|
| See references of WO9956007A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| DE19818893A1 (en) | 1999-11-04 |
| US6318325B1 (en) | 2001-11-20 |
| DE59902193D1 (en) | 2002-09-05 |
| EP1075589B1 (en) | 2002-07-31 |
| WO1999056007A1 (en) | 1999-11-04 |
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