EP1701007B1 - Hydraulic valve lash adjuster - Google Patents
Hydraulic valve lash adjuster Download PDFInfo
- Publication number
- EP1701007B1 EP1701007B1 EP06003003A EP06003003A EP1701007B1 EP 1701007 B1 EP1701007 B1 EP 1701007B1 EP 06003003 A EP06003003 A EP 06003003A EP 06003003 A EP06003003 A EP 06003003A EP 1701007 B1 EP1701007 B1 EP 1701007B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- closing body
- control valve
- pressure space
- 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.)
- Expired - Fee Related
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Classifications
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- 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
- F01L1/255—Hydraulic tappets between cam and rocker arm
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- 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
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- 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
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- 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
- F01L2001/2438—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically with means permitting forced opening of check valve
Definitions
- the invention relates to a hydraulic valve clearance compensation element for the control drive of an internal combustion engine, which is designed as a reverse spring / free-ball element, with a cylindrical housing, guided therein with a sealing clearance cylindrical piston and a control valve which between a low-pressure chamber of the piston and a high-pressure chamber of the Housing is arranged on a piston head and has a closing body, which is in application of a stroke in the closing direction against the action of a control valve spring on an axial bore of the piston head surrounding the valve seat and in the opening direction of a stop surface of a closing body surrounding the valve cap.
- Hydraulic lash adjusters are used to compensate for the play, which forms in the transmission of the cam lift from a camshaft to a gas exchange valve of the internal combustion engine between the transmission elements due to wear or thermal expansion.
- the compensating element By using the compensating element, a low-noise and low-wear operation of the valve train and the greatest possible match of the cam lobe with the stroke of the gas exchange valve should be achieved.
- Such compensating elements each have a control valve designed as a check valve, which has a closing body, for example a ball, and a control valve spring, which acts on the closing body.
- a closing body for example a ball
- a control valve spring which acts on the closing body.
- the closing body is acted upon by the control valve spring in the closing direction.
- the control valve is predominantly closed and it eliminates an idle stroke of the valve clearance compensation element.
- control valve spring acts on the closing body in the opening direction or is completely dispensed with a spring.
- Compensating elements with such a control valve are referred to as free-spring elements because of the reverse arrangement of the control valve spring as reverse-spring elements or in the absence of the spring. These have a positive influence on the thermodynamics, the pollutant emission and the mechanical stress of the internal combustion engine and are therefore increasingly used.
- the control valve in the base circle region of the cam is largely closed due to the spring force of the control valve spring.
- the control valve is kept open in this area by the force of the control valve spring or the free ball element, the closure is not enforced. Since such an element only can be closed by hydrodynamic and hydrostatic forces by the beginning of the cam lobe, flowing from the high pressure chamber to the low pressure chamber lubricating oil flow, the element always has an idle stroke before the start of the valve lift of the gas exchange valve.
- the size of the idle stroke depends on the length of the closing time of the control valve at each engine speed and this in turn depends on the viscosity / density of the lubricating oil, which is known to be used as a hydraulic medium here.
- Closing the control valve of a reverse spring / freeball element requires a so-called critical lubricating oil velocity. This depends on the lubricating oil viscosity and thus on the lubricating oil temperature. At high lubricating oil viscosity / density, i. At low lubricating oil temperature, the critical lubricating oil speed is lower and therefore achieved faster than at low lubricating oil viscosity, ie high lubricating oil temperature. This results in Kaltstärt to a shorter closing time of the control valve and thus to a lower idle stroke than the warm engine. A small idle stroke, however, means a large valve overlap. This results in a large internal exhaust gas recirculation, which causes a troubled, low idle. This can be improved by raising the idle speed, but this is at the expense of pollutant emissions and fuel consumption.
- Reverse spring / free-ball elements of the type mentioned are, for example, from the publications EP 1 298 287 A2 . JP 61-185607 and US 4,054,109 known. They show compensation elements, in which the control valve has a ball as a closing body.
- the closing body is guided in bores. Since lubricating oil for closing the control valve must flow around the closing body, the guide gap can not be chosen arbitrarily small. As a result, the closing body is not ideally guided, which leads to deviations in the closing behavior. On the other hand, a flow around the closing body is necessary in order to define the closing behavior. Here is a significant thermal dependence of the closing behavior is given.
- the invention has for its object to achieve improved guidance of the closing body, so that the closing body can not escape from its trajectory. This should significantly reduce the stroke tolerance.
- the interruptions are formed according to claim 1 of groove-shaped channels, which are incorporated in the located on the axial bore inner surface of the piston crown.
- the closing body has according to claim 2 on its outer surface protruding, the interruptions forming, in the circumferential direction at intervals one behind the other and directed to the valve cap guide ribs.
- the valve cap has according to claim 3 on its inner surface guide ribs, which form the interruptions. The guide ribs are then on the valve cap in the circumferential direction at intervals one behind the other from the closing body down.
- the interruptions may be formed by groove-shaped channels, which are incorporated in the located on the axial bore inner surface of the piston crown.
- a tight guidance of the control valve spring causes that it can not buckle. As a result, spring force tolerances and thus deviations in the closing behavior of the control valve are reduced. Due to the interruptions in the leadership of the control valve spring, the flow of the hydraulic fluid is not hindered, but even improved. However, the interruptions must not extend all the way into the valve seat so that the control valve can reliably seal.
- FIG. 9 illustrated lash adjuster is designed as a hydraulic roller tappet 1.
- This has a rotationally symmetrical housing 2 with a arranged at the bottom, not shown role.
- the housing 2 has a stepped blind hole, which forms a high pressure chamber 3 and in which a hollow cylindrical piston 4 is guided with sealing clearance.
- the piston 4 has a lower piston head 5 and an upper piston head 6. It is divided horizontally into a piston lower part 7 and a piston upper part 9.
- Below the lower piston crown 5 is the high-pressure chamber 3.
- a low-pressure chamber 8 is arranged, which is formed by the interior of the piston 4 and serves as an oil reservoir.
- the high-pressure chamber 3 is connected to the low-pressure chamber 8 through a central axial bore, which is arranged in the lower piston crown 5. It is part of a provided with a control valve spring 10 control valve 11. This extends into the high-pressure chamber 3 below the lower piston crown 5.
- a compression spring 12 is supported in a central recess 13 on the bottom 14 of the high-pressure chamber 3 from. It acts on the piston 4 and thus the entire valve train with its pressure force.
- the upper piston head 6 has on its outer surface 15 a central conical depression 16 for guiding, for example, the spherical end 17 of a push rod, not shown.
- Another central axial bore 18, which is located in the upper piston head 6, establishes the connection of the low-pressure chamber 8 with the lubricating oil supply of the valve drive.
- the closing body 19 of this compensating element is a ball.
- control valve 20 is attached to a piston 21 of a valve lash adjuster.
- a low-pressure chamber 22 is connected via an axial bore 23 with the high-pressure chamber 24 of the compensating element, which is located below the piston crown 25.
- the axial bore 23 is a stepped bore and forms a valve seat 26 for a closure member 27 formed as a ball whose stroke 28 is limited in the direction of the piston 21 there.
- a stop surface 29 of a valve cap 30 which surrounds the closing body 27 and is located with a flange between the piston head 25 and the upper end of a compression spring 31 of the compensating element.
- the closing body 27 is located in a longitudinal section of the axial bore 23 and is guided there on exercise of the stroke 28 on the inner surface of the piston crown 25.
- the surface acting as a guide surface 32 has a plurality of circumferentially successively arranged, extending in the axial direction interruptions, so that there channels 33 are formed, through which hydraulic fluid can flow past the closing body 27. The interruptions are here so on the piston.
- the control valve 20 is first held by a control valve spring 34 in the open position.
- the control valve spring 34 is arranged in the axial bore 23 and is supported at one end on the piston head 25 and at the other end on the closing body 27.
- the compensation element differs according to the FIGS. 3 and 4 essentially only in that the interruptions are not arranged on the piston, but on the closing body 35.
- This is cylindrical and formed with convex curved end faces. He has on its lateral surface as a result of the interruptions projecting guide ribs 36 Guide surfaces 37, which are provided for the system on the closing body 35 surrounding the valve cap 30. Accordingly, the construction of the piston 38 with its axial bore 39, its piston head 40 and its control valve 41 is slightly modified.
- the closing body 42 is also guided by a guide surface 43 of a valve cap 44, wherein the interruptions are arranged here on the valve cap 44.
- a plurality of guide ribs 46 are formed on the inner surface of the valve cap 44.
- FIGS. 7 and 8 an embodiment in which 47 interruptions for the control valve spring 48 are provided on the piston.
- the interruptions are provided on the inner surface of the piston head 50 in this control valve 51.
- On the guide surface 52 for the control valve spring 48 are therefore several circumferentially successively arranged channels 53 for the passage of the hydraulic fluid.
Description
Die Erfindung betrifft ein hydraulisches Ventilspielausgleichselement für den Steuertrieb eines Verbrennungsmotors, welches als Reverse-Spring/Freeball-Element ausgebildet ist, mit einem zylindrischen Gehäuse, einem darin mit Dichtspiel geführten zylindrischen Kolben und einem Steuerventil, welches zwischen einem Niederdruckraum des Kolbens und einem Hochdruckraum des Gehäuses an einem Kolbenboden angeordnet ist und einen Schließkörper aufweist, der bei Ausführung eines Hubes in der Schließrichtung gegen die Wirkung einer Steuerventilfeder an einem eine Axialbohrung des Kolbenbodens umgebenden Ventilsitz und in der Öffnungsrichtung an einer Anschlagfläche einer den Schließkörper umgebenden Ventilkappe anlegbar ist.The invention relates to a hydraulic valve clearance compensation element for the control drive of an internal combustion engine, which is designed as a reverse spring / free-ball element, with a cylindrical housing, guided therein with a sealing clearance cylindrical piston and a control valve which between a low-pressure chamber of the piston and a high-pressure chamber of the Housing is arranged on a piston head and has a closing body, which is in application of a stroke in the closing direction against the action of a control valve spring on an axial bore of the piston head surrounding the valve seat and in the opening direction of a stop surface of a closing body surrounding the valve cap.
Hydraulische Ventilspielausgleichselemente dienen dem Ausgleich des Spiels, das sich bei der Übertragung des Nockenhubs von einer Nockenwelle auf ein Gaswechselventil des Verbrennungsmotors zwischen den Übertragungselementen infolge von Verschleiß oder Wärmedehnung bildet. Durch die Verwendung des Ausgleichselements sollen eine geräusch- und verschleißarme Arbeitsweise des Ventiltriebs und eine größtmögliche Übereinstimmung der Nockenerhebung mit dem Hub des Gaswechselventils erreicht werden.Hydraulic lash adjusters are used to compensate for the play, which forms in the transmission of the cam lift from a camshaft to a gas exchange valve of the internal combustion engine between the transmission elements due to wear or thermal expansion. By using the compensating element, a low-noise and low-wear operation of the valve train and the greatest possible match of the cam lobe with the stroke of the gas exchange valve should be achieved.
Solche Ausgleichselemente besitzen jeweils ein als Rückschlagventil ausgebildetes Steuerventil, das einen Schließkörper, beispielsweise eine Kugel, und eine Steuerventilfeder aufweist, welche den Schließkörper beaufschlagt. Bei der Standardbauweise des Steuerventils ist der Schließkörper von der Steuerventilfeder in Schließrichtung beaufschlagt. Dadurch ist das Steuerventil überwiegend geschlossen und es entfällt ein Leerhub des Ventilspielausgleichselementes. Bei dieser Ausführung besteht die Gefahr des Aufpumpens des Ausgleichselements und der Entstehung eines "negativen Ventilspiels".Such compensating elements each have a control valve designed as a check valve, which has a closing body, for example a ball, and a control valve spring, which acts on the closing body. In the standard construction of the control valve, the closing body is acted upon by the control valve spring in the closing direction. As a result, the control valve is predominantly closed and it eliminates an idle stroke of the valve clearance compensation element. In this embodiment, there is a risk of inflation of the compensating element and the emergence of a "negative valve clearance".
Diese Nachteile werden mit Steuerventilen vermieden, deren Steuerventilfeder den Schließkörper in Öffnungsrichtung beaufschlagt bzw. bei denen ganz auf eine Feder verzichtet wird. Ausgleichselemente mit einem derartigen Steuerventil werden wegen der umgekehrten Anordnung der Steuerventilfeder als Reverse-Spring-Elemente bzw. bei Entfallen der Feder als Freeball-Elemente bezeichnet. Diese üben einen positiven Einfluss auf die Thermodynamik, die Schadstoffemission und die mechanische Beanspruchung des Verbrennungsmotors aus und werden deshalb in zunehmendem Maße eingesetzt.These disadvantages are avoided with control valves, the control valve spring acts on the closing body in the opening direction or is completely dispensed with a spring. Compensating elements with such a control valve are referred to as free-spring elements because of the reverse arrangement of the control valve spring as reverse-spring elements or in the absence of the spring. These have a positive influence on the thermodynamics, the pollutant emission and the mechanical stress of the internal combustion engine and are therefore increasingly used.
Bei der Standardbauweise ist das Steuerventil im Grundkreisbereich des Nockens infolge der Federkraft der Steuerventilfeder überwiegend geschlossen. Bei einem Reverse-Spring-Element wird das Steuerventil in diesem Bereich jedoch durch die Kraft der Steuerventilfeder offen gehalten bzw. beim Freeball-Element wird die Schließung nicht erzwungen. Da ein solches Element erst durch den mit Beginn der Nockenerhebung einsetzenden, vom Hochdruckraum zum Niederdruckraum fließenden Schmierölstrom durch hydrodynamische und hydrostatische Kräfte geschlossen werden kann, besitzt das Element vor Beginn des Ventilhubs des Gaswechselventils immer einen Leerhub. Die Größe des Leerhubs hängt bei jeder Motordrehzahl von der Länge der Schließzeit des Steuerventils und diese hängt wiederum von der Viskosität/Dichte des Schmieröls ab, welches hier bekanntlich als Hydraulikmittel verwendet wird.In the standard construction, the control valve in the base circle region of the cam is largely closed due to the spring force of the control valve spring. In a reverse spring element, however, the control valve is kept open in this area by the force of the control valve spring or the free ball element, the closure is not enforced. Since such an element only can be closed by hydrodynamic and hydrostatic forces by the beginning of the cam lobe, flowing from the high pressure chamber to the low pressure chamber lubricating oil flow, the element always has an idle stroke before the start of the valve lift of the gas exchange valve. The size of the idle stroke depends on the length of the closing time of the control valve at each engine speed and this in turn depends on the viscosity / density of the lubricating oil, which is known to be used as a hydraulic medium here.
Zum Schließen des Steuerventils eines Reverse-Spring/Freeball-Elements ist eine so genannte kritische Schmierölgeschwindigkeit erforderlich. Diese hängt von der Schmierölviskosität und damit von der Schmieröltemperatur ab. Bei hoher Schmierölviskosität/Dichte, d.h. bei niedriger Schmieröltemperatur, ist die kritische Schmierölgeschwindigkeit niedriger und wird deshalb schneller erreicht, als bei niedriger Schmierölviskosität, also hoher Schmieröltemperatur. Das führt beim Kaltstärt zu einer kürzeren Schließzeit des Steuerventils und damit zu einem geringeren Leerhub als bei dem betriebswarmen Motor. Ein kleiner Leerhub bedeutet jedoch eine große Ventilüberschneidung. Diese hat eine große interne Abgasrückführung zur Folge, die einen unruhigen, niedrigen Leerlauf verursacht. Dieser kann durch Anheben der Leerlaufdrehzahl zwar verbessert werden, jedoch geht das zu Lasten der Schadstoffemission und des Kraftstoffverbrauchs.Closing the control valve of a reverse spring / freeball element requires a so-called critical lubricating oil velocity. This depends on the lubricating oil viscosity and thus on the lubricating oil temperature. At high lubricating oil viscosity / density, i. At low lubricating oil temperature, the critical lubricating oil speed is lower and therefore achieved faster than at low lubricating oil viscosity, ie high lubricating oil temperature. This results in Kaltstärt to a shorter closing time of the control valve and thus to a lower idle stroke than the warm engine. A small idle stroke, however, means a large valve overlap. This results in a large internal exhaust gas recirculation, which causes a troubled, low idle. This can be improved by raising the idle speed, but this is at the expense of pollutant emissions and fuel consumption.
Reverse-Spring/Freeball-Elemente der eingangs genannten Art sind beispielsweise aus den Druckschriften
Bei Reverse-Spring/Freeball-Elementen ist also der Schließkörper des Steuerventils im Grundkreis des Nockens offen. Zum Schließen des Steuerventils muss ein Volumenstrom am Schließkörper vorbeifließen, der eine Druckdifferenz am Schließkörper bewirkt, wodurch dieser das Steuerventil schließt. Um die Toleranzen des erzeugten Leerhubs gering zu halten, soll der Hub des Schließkörpers möglichst nicht schwanken. Außerdem wirkt sich ein exzentrischer Spalt zwischen dem Schließkörper und der ihn umgebenden Führungswand negativ auf die Strömung aus, wodurch das Schließverhalten ebenfalls beeinflusst wird.In reverse spring / freeball elements so the closing body of the control valve in the base circle of the cam is open. To close the control valve, a volume flow must flow past the closing body, which causes a pressure difference on the closing body, whereby it closes the control valve. In order to keep the tolerances of the generated Leerhubs small, the stroke of the closing body should not fluctuate as possible. In addition, an eccentric gap between the closing body and the surrounding guide wall negatively affects the flow, whereby the closing behavior is also affected.
Der Erfindung liegt die Aufgabe zugrunde, eine verbesserte Führung des Schließkörpers zu erreichen, so dass der Schließkörper aus seiner Bewegungsbahn nicht ausweichen kann. Dadurch soll die Hubtoleranz deutlich eingeschränkt werden.The invention has for its object to achieve improved guidance of the closing body, so that the closing body can not escape from its trajectory. This should significantly reduce the stroke tolerance.
Diese Aufgabe wird erfindungsgemäß durch die Merkmale der unabhängigen Ansprüche 1,2,3 und 4 gelöst. Im Bereich der Axialbohrung für den Schließkörper ist eine enge Führungsfläche mit Unterbrechungen ausgebildet, welche einen Volumenstrom von Hydraulikmittel zwischen dem Hochdruckraum und dem Niederdruckraum ermöglichen. Damit trotz der besseren Führung das Schließverhalten nicht beeinträchtigt wird, ist der Schließkörper nach der Erfindung also in unterbrochenen Geometrien geführt.This object is achieved by the features of the
Die Unterbrechungen werden gemäß Anspruch 1 von nutförmigen Kanälen gebildet, welche in die an der Axialbohrung befindliche innere Oberfläche des Kolbenbodens eingearbeitet sind.The interruptions are formed according to claim 1 of groove-shaped channels, which are incorporated in the located on the axial bore inner surface of the piston crown.
Der Schließkörper weist gemäß Anspruch 2 an seiner äußeren Oberfläche abstehende, die Unterbrechungen bildende, in Umfangsrichtung in Abständen hintereinander angeordnete und auf die Ventilkappe gerichtete Führungsrippen auf. Die Ventilkappe weist gemäß Anspruch 3 an ihrer inneren Oberfläche Führungsrippen auf, welche die Unterbrechungen bilden. Die Führungsrippen stehen dann an der Ventilkappe in Umfangsrichtung in Abständen hintereinander zu dem Schließkörper hin ab.The closing body has according to
Infolge der Kanäle oder Führungsrippen wird eine gute Führung des Schließkörpers erreicht, wobei durch die Unterbrechungen genügend Hydraulikmittel das Steuerventil passieren kann, so dass sich das Schließverhalten nicht verschlechtert. Wenn die Unterbrechungen, durch die das Hydraulikmittel fließt, sich am Schließkörper selbst befinden, ist dieser sinnvollerweise so ausgeführt, dass er sich um seine Hochachse nicht verkippen kann, damit eine saubere Abdichtung am Ventilsitz des Steuerventils erfolgt.As a result of the channels or guide ribs good guidance of the closing body is achieved, which can pass through the interruptions sufficient hydraulic fluid, the control valve, so that the closing behavior does not deteriorate. If the interruptions through which the hydraulic fluid flows, are on the closing body itself, this is usefully designed so that it can not tilt about its vertical axis, so that a clean seal on the valve seat of the control valve.
Entsprechende Vorteile können erreicht werden, wenn gemäß Anspruch 4 im Bereich der Axialbohrung an einer engen Führungsfläche für die Steuerventilfeder Unterbrechungen vorgesehen sind, welche einen Volumenstrom von Hydraulikmittel zwischen dem Hochdruckraum und dem Niederdruckraum ermöglichen. Dabei können die Unterbrechungen von nutförmigen Kanälen gebildet sein, welche in die an der Axialbohrung befindliche innere Oberfläche des Kolbenbodens eingearbeitet sind.Corresponding advantages can be achieved if according to
Eine enge Führung der Steuerventilfeder bewirkt, dass diese nicht ausknicken kann. Dadurch werden Federkrafttoleranzen und damit Abweichungen im Schließverhalten des Steuerventils verringert. Durch die Unterbrechungen in der Führung der Steuerventilfeder wird die Strömung des Hydraulikmittels nicht behindert, sondern sogar noch verbessert. Die Unterbrechungen dürfen sich jedoch nicht bis in den Ventilsitz erstrecken, damit das Steuerventil sicher abdichten kann.A tight guidance of the control valve spring causes that it can not buckle. As a result, spring force tolerances and thus deviations in the closing behavior of the control valve are reduced. Due to the interruptions in the leadership of the control valve spring, the flow of the hydraulic fluid is not hindered, but even improved. However, the interruptions must not extend all the way into the valve seat so that the control valve can reliably seal.
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im Folgenden näher beschrieben. Es zeigen:
- Figur 1
- den Bereich des Steuerventils eines Reverse-Spring/Freeball-Elementes in einer ersten erfindungsgemäßen Ausführungsform, im Längsschnitt;
Figur 2- den Steuerventilbereich in einem durch den Schließkörper verlaufenden Querschnitt gemäß Linie ||-|| der
Figur 1 ; Figur 3- den Steuerventilbereich in einer zweiten erfindungsgemäßen Ausführungsform, im Längsschnitt;
Figur 4- den Steuerventilbereich in einem durch den Schließkörper verlaufenden Querschnitt gemäß Linie IV- IV der
;Figur 3 Figur 5- den Steuerventilbereich in einer dritten erfindungsgemäßen Ausführungsform, im Längsschnitt;
- Figur 6
- den Steuerventilbereich in einem durch den Schließkörper verlaufenden Querschnitt gemäß Linie VI -
VI der Figur 5 ; Figur 7- den Steuerventilbereich in einer vierten erfindungsgemäßen Ausführungsform, im Längsschnitt;
Figur 8- den Steuerventilbereich in einem durch die Steuerventilfeder verlaufenden Querschnitt gemäß Linie VIII -
VIII der Figur 7 ; - Figur 9
- ein Reverse-Spring/Freeball-Element mit einem herkömmlich geführten Schließkörper des Steuerventils, im Längsschnitt.
- FIG. 1
- the region of the control valve of a reverse spring / freeball element in a first embodiment according to the invention, in longitudinal section;
- FIG. 2
- the control valve area in a through the closing body extending cross section according to line || - || of the
FIG. 1 ; - FIG. 3
- the control valve area in a second embodiment according to the invention, in longitudinal section;
- FIG. 4
- the control valve area in a running through the closing body cross section according to line IV IV of
FIG. 3 ; - FIG. 5
- the control valve area in a third embodiment according to the invention, in longitudinal section;
- FIG. 6
- the control valve area in a running through the closing body cross section according to line VI - VI of
FIG. 5 ; - FIG. 7
- the control valve portion in a fourth embodiment of the invention, in longitudinal section;
- FIG. 8
- the control valve area in a running through the control valve spring cross section according to line VIII - VIII of
FIG. 7 ; - FIG. 9
- a reverse spring / freeball element with a conventionally guided closing body of the control valve, in longitudinal section.
Das in
Der Hochdruckraum 3 ist mit dem Niederdruckraum 8 durch eine zentrale Axialbohrung verbunden, die im unteren Kolbenboden 5 angeordnet ist. Sie ist Teil eines mit einer Steuerventilfeder 10 versehenen Steuerventils 11. Dieses erstreckt sich bis in den Hochdruckraum 3 unterhalb des unteren Kolbenbodens 5. Eine Druckfeder 12 stützt sich in einer zentralen Ausnehmung 13 am Boden 14 des Hochdruckraums 3 ab. Sie beaufschlagt den Kolben 4 und damit den gesamten Ventiltrieb mit ihrer Druckkraft. Der obere Kolbenboden 6 weist an seiner Außenfläche 15 eine zentrale konische Einsenkung 16 zur Führung beispielsweise des kugelförmigen Endes 17 einer nicht dargestellten Stößelstange auf. Eine weitere zentrale Axialbohrung 18, die sich in dem oberen Kolbenboden 6 befindet, stellt die Verbindung des Niederdruckraums 8 mit der Schmierölversorgung des Ventiltriebs her. Der Schließkörper 19 dieses Ausgleichselementes ist eine Kugel.The high-
Das in den
Von dieser Ausführung unterscheidet sich das Ausgleichselement nach den
Bei der ähnlichen Ausführung nach den
Schließlich zeigen die
- 11
- Rollenstößelroller plunger
- 22
- Gehäusecasing
- 33
- HochdruckraumHigh-pressure chamber
- 44
- Kolbenpiston
- 55
- unterer Kolbenbodenlower piston bottom
- 66
- oberer Kolbenbodenupper piston crown
- 77
- KolbenunterteilPiston part
- 88th
- NiederdruckraumLow-pressure chamber
- 99
- KolbenoberteilPiston crown
- 1010
- SteuerventilfederControl valve spring
- 1111
- Steuerventilcontrol valve
- 1212
- Druckfedercompression spring
- 1313
- Ausnehmungrecess
- 1414
- Bodenground
- 1515
- Außenflächeouter surface
- 1616
- konische Einsenkungconical depression
- 1717
- kugelförmiges Endespherical end
- 1818
- Axialbohrungaxial bore
- 1919
- Schließkörperclosing body
- 2020
- Steuerventilcontrol valve
- 2121
- Kolbenpiston
- 2222
- NiederdruckraumLow-pressure chamber
- 2323
- Axialbohrungaxial bore
- 2424
- HochdruckraumHigh-pressure chamber
- 2525
- Kolbenbodenpiston crown
- 2626
- Ventilsitzvalve seat
- 2727
- Schließkörperclosing body
- 2828
- Hubstroke
- 2929
- Anschlagflächestop surface
- 3030
- Ventilkappevalve cap
- 3131
- Druckfedercompression spring
- 3232
- Führungsflächeguide surface
- 3333
- Kanalchannel
- 3434
- SteuerventilfederControl valve spring
- 3535
- Schließkörperclosing body
- 3636
- Führungsrippeguide rib
- 3737
- Führungsflächeguide surface
- 3838
- Kolbenpiston
- 3939
- Axialbohrungaxial bore
- 4040
- Kolbenbodenpiston crown
- 4141
- Steuerventilcontrol valve
- 4242
- Schließkörperclosing body
- 4343
- Führungsflächeguide surface
- 4444
- Ventilkappevalve cap
- 4545
- Steuerventilcontrol valve
- 4646
- Führungsrippeguide rib
- 4747
- Kolbenpiston
- 4848
- SteuerventilfederControl valve spring
- 4949
- Axialbohrungaxial bore
- 5050
- Kolbenbodenpiston crown
- 5151
- Steuerventilcontrol valve
- 5252
- Führungsflächeguide surface
- 5353
- Kanalchannel
Claims (4)
- Hydraulic valve play compensating element for the valve timing gear of an internal combustion engine, which hydraulic valve play compensating element is embodied as a reverse-spring/freeball element, having a cylindrical housing, having a cylindrical piston (21, 38) which is guided in said cylindrical housing with sealing play, and having a control valve (20, 41, 45) which is arranged between a low-pressure space (22) of the piston (21, 38) and a high-pressure space (24) of the housing on a piston head (25, 40) and has a closing body (27, 35, 42) which, as it performs a stroke (28) in the closing direction, can be placed, counter to the action of a control valve spring (34), against a valve seat (26) which surrounds an axial bore (23, 39) of the piston head (25, 40), and in the opening direction, can be placed against a stop face (29) of a valve cap (30, 44) which surrounds the closing body (27, 35, 42), characterized in that, in the region of the axial bore (23, 39) for the closing body (27, 35, 42), a narrow guide face (32, 37, 43) with recesses is formed, which recesses permit a volume flow of hydraulic medium between the high-pressure space (24) and the low-pressure space (22), with the recesses being formed by groove-shaped ducts (33) which are formed in the inner surface, located on the axial bore (23), of the piston head (25).
- Hydraulic valve play compensating element for the valve timing gear of an internal combustion engine, which hydraulic valve play compensating element is embodied as a reverse-spring/freeball element, having a cylindrical housing, having a cylindrical piston (21, 38) which is guided in said cylindrical housing with sealing play, and having a control valve (20, 41, 45) which is arranged between a low-pressure space (22) of the piston (21, 38) and a high-pressure space (24) of the housing on a piston head (25, 40) and has a closing body (27, 35, 42) which, as it performs a stroke (28) in the closing direction, can be placed, counter to the action of a control valve spring (34), against a valve seat (26) which surrounds an axial bore (23, 39) of the piston head (25, 40), and in the opening direction, can be placed against a stop face (29) of a valve cap (30, 44) which surrounds the closing body (27, 35, 42), characterized in that, in the region of the axial bore (23, 39) for the closing body (27, 35, 42), a narrow guide face (32, 37, 43) with recesses is formed, which recesses permit a volume flow of hydraulic medium between the high-pressure space (24) and the low-pressure space (22), with the closing body (35) having guide ribs (36) which project from its outer surface, which form the recesses and which are arranged in succession at intervals in the peripheral direction and which are aligned towards the valve cap (30).
- Hydraulic valve play compensating element for the valve timing gear of an internal combustion engine, which hydraulic valve play compensating element is embodied as a reverse-spring/freeball element, having a cylindrical housing, having a cylindrical piston (21, 38) which is guided in said cylindrical housing with sealing play, and having a control valve (20, 41, 45) which is arranged between a low-pressure space (22) of the piston (21, 38) and a high-pressure space (24) of the housing on a piston head (25, 40) and has a closing body (27, 35, 42) which, as it performs a stroke (28) in the closing direction, can be placed, counter to the action of a control valve spring (34), against a valve seat (26) which surrounds an axial bore (23, 39) of the piston head (25, 40), and in the opening direction, can be placed against a stop face (29) of a valve cap (30, 44) which surrounds the closing body (27, 35, 42), characterized in that, in the region of the axial bore (23, 39) for the closing body (27, 35, 42), a narrow guide face (32, 37, 43) with recesses is formed, which recesses permit a volume flow of hydraulic medium between the high-pressure space (24) and the low-pressure space (22), with the valve cap (44) having, on its inner surface, guide ribs (46) which form the recesses, which are arranged in succession at intervals in the peripheral direction and which project towards the closing body (42).
- Hydraulic valve play compensating element for the valve timing gear of an internal combustion engine, which hydraulic valve play compensating element is embodied as a reverse-spring/freeball element, having a cylindrical housing, having a cylindrical piston (47) which is guided in said cylindrical housing with sealing play, and having a control valve (51) which is arranged between a low-pressure space (22) of the piston (47) and a high-pressure space (24) of the housing on a piston head (50) and has a closing body (27) which, as it performs a stroke (28) in the closing direction, can be placed, counter to the action of a control valve spring (48), against a valve seat (26) which surrounds an axial bore (49) of the piston head (50), and in the opening direction, can be placed against a stop face (29) of a valve cap (30) which surrounds the closing body (27), characterized in that, in the region of the axial bore (49), recesses are provided on a narrow guide face (52) for the control valve spring (48), which recesses permit a volume flow of hydraulic medium between the high-pressure space (24) and the low-pressure space (22), with the recesses being formed by groove-shaped ducts (53) which are formed in the inner surface, located on the axial bore (49), of the piston head (50).
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005010711A DE102005010711A1 (en) | 2005-03-09 | 2005-03-09 | Hydraulic valve clearance compensation element |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1701007A1 EP1701007A1 (en) | 2006-09-13 |
EP1701007B1 true EP1701007B1 (en) | 2008-04-16 |
Family
ID=36609523
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06003003A Expired - Fee Related EP1701007B1 (en) | 2005-03-09 | 2006-02-15 | Hydraulic valve lash adjuster |
Country Status (3)
Country | Link |
---|---|
US (1) | US7328676B2 (en) |
EP (1) | EP1701007B1 (en) |
DE (2) | DE102005010711A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11339688B2 (en) | 2020-01-29 | 2022-05-24 | Borgwarner, Inc. | Variable camshaft timing valve assembly |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070272185A1 (en) * | 2006-05-24 | 2007-11-29 | Schaeffler Kg | Hydraulic lash adjuster for an internal combustion engine |
DE102006048845A1 (en) * | 2006-10-13 | 2008-04-17 | Schaeffler Kg | Hydraulic valve play compensation element for valve gear e.g. for vehicle internal combustion engine, has piston guided in piston housing and piston has low pressure chamber |
DE102006048549A1 (en) * | 2006-10-13 | 2008-04-17 | Schaeffler Kg | Hydraulic valve lash adjuster with Leerhubfunktion for a valve train of an internal combustion engine |
DE102007046829A1 (en) * | 2007-09-29 | 2009-04-02 | Schaeffler Kg | Hydraulic valve clearance compensation element |
US9631522B2 (en) | 2015-01-13 | 2017-04-25 | Caterpillar Inc. | Compact valve bridge assembly having cartridge insert |
US9714587B2 (en) | 2015-01-13 | 2017-07-25 | Caterpillar Inc. | Bridge assembly having motion-limited valve |
US10072535B2 (en) * | 2017-01-10 | 2018-09-11 | Schaeffler Technologies AG & Co. KG | Lash compensator spring end cap |
US10794235B1 (en) | 2019-09-04 | 2020-10-06 | Deere & Company | Automatic lash adjuster for use with high compression internal combustion engines |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH197057A (en) * | 1937-05-19 | 1938-04-15 | Ernst Philipp | Device to prevent the backflow of water from sanitary and other systems into the main line. |
US2790430A (en) * | 1953-04-17 | 1957-04-30 | William P Lowther | Hydraulic valve lifter |
US3219057A (en) * | 1962-07-02 | 1965-11-23 | John G Knowles | Check valves |
US4054109A (en) | 1976-03-31 | 1977-10-18 | General Motors Corporation | Engine with variable valve overlap |
DE2941244C2 (en) * | 1979-10-11 | 1984-09-27 | Lechler Gmbh & Co Kg, 7012 Fellbach | Valve arrangement |
JPS61185607A (en) * | 1985-02-12 | 1986-08-19 | Suzuki Motor Co Ltd | Valve lift varying device for four-cycle engine |
US5183075A (en) * | 1986-04-12 | 1993-02-02 | Stein Guenter | Check valve |
DE19525948A1 (en) * | 1995-07-17 | 1997-01-23 | Schaeffler Waelzlager Kg | Step valve |
US5622147A (en) * | 1996-03-08 | 1997-04-22 | Eaton Corporation | Hydraulic lash adjuster |
US5758613A (en) | 1997-01-30 | 1998-06-02 | Eaton Corporation | Hydraulic lash adjuster and biased normally open check valve system therefor |
DE19739904A1 (en) * | 1997-09-11 | 1999-03-18 | Bosch Gmbh Robert | Check valve, especially for a piston pump |
US5862785A (en) * | 1998-01-26 | 1999-01-26 | Eaton Corporation | Hydraulic lash adjuster and improved oil flow path therefor |
DE102004018457A1 (en) * | 2004-04-16 | 2005-11-17 | Ina-Schaeffler Kg | Hydraulic valve clearance compensation element |
-
2005
- 2005-03-09 DE DE102005010711A patent/DE102005010711A1/en not_active Withdrawn
-
2006
- 2006-02-15 EP EP06003003A patent/EP1701007B1/en not_active Expired - Fee Related
- 2006-02-15 DE DE502006000617T patent/DE502006000617D1/en active Active
- 2006-03-08 US US11/370,633 patent/US7328676B2/en not_active Expired - Fee Related
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11339688B2 (en) | 2020-01-29 | 2022-05-24 | Borgwarner, Inc. | Variable camshaft timing valve assembly |
Also Published As
Publication number | Publication date |
---|---|
US20060201466A1 (en) | 2006-09-14 |
US7328676B2 (en) | 2008-02-12 |
DE102005010711A1 (en) | 2006-09-14 |
DE502006000617D1 (en) | 2008-05-29 |
EP1701007A1 (en) | 2006-09-13 |
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