EP2564038B1 - Hydraulic valve play compensating element for reciprocating-piston internal combustion engines - Google Patents

Hydraulic valve play compensating element for reciprocating-piston internal combustion engines Download PDF

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Publication number
EP2564038B1
EP2564038B1 EP11715902.0A EP11715902A EP2564038B1 EP 2564038 B1 EP2564038 B1 EP 2564038B1 EP 11715902 A EP11715902 A EP 11715902A EP 2564038 B1 EP2564038 B1 EP 2564038B1
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EP
European Patent Office
Prior art keywords
valve
internal combustion
reciprocating
combustion engine
piston internal
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EP11715902.0A
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German (de)
French (fr)
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EP2564038A2 (en
Inventor
Peter Sailer
Oliver Schnell
Oliver Witter
Klaus Tietzel
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Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP2564038A2 publication Critical patent/EP2564038A2/en
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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
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/2411—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the valve stem and rocker arm
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • Reciprocating internal combustion engine according to the four-stroke method with a crankcase and at least one cylinder arranged therein, in which a piston is guided by a crankshaft, with at least one cylinder head closing the cylinder whose inlet and outlet ports of at least one each loaded with a valve spring Ein - And exhaust valve are controlled, which are actuated by driven by a camshaft transmission elements, and with a hydraulic valve clearance compensation element, which is installed in at least one of the transmission elements or in a transmission member between the camshaft and at least one inlet and / or exhaust valve and a Working piston, a cylinder housing cooperating with the working piston, a return spring installed therebetween and a non-return valve delimiting a high pressure chamber, the valve closing body of which corresponds to a valve seat on the working piston.
  • Reciprocating internal combustion engines with hydraulic valve clearance compensation elements are well known. You have the problem that, depending on the speed of the reciprocating internal combustion engine and lifting height of the cam, the high-pressure chamber of the valve clearance compensation elements can not fill sufficiently, so that a decrease in the hydraulic valve clearance compensation element may occur, resulting in increased or unduly high clearance in the valve train. On the other hand, it is also possible that inflates the hydraulic valve clearance compensation element too much, so that the permissible valve clearance is exceeded.
  • the problems are particularly significant when the hydraulic valve clearance compensation elements brake control devices or exhaust gas recirculation devices are used on the reciprocating internal combustion engine, wherein in the region of the base circle of the cam additional elevations are provided.
  • the object of the invention is therefore to eliminate the disadvantages of the measures described on hydraulic valve clearance compensation elements, in particular to the effect that both during normal operation, especially in larger engines for commercial vehicles, as well as in operation with additional opening of the gas exchange valves for decompression or exhaust gas recirculation no Decrease of the hydraulic valve clearance compensation elements occurs. This should be presented with simple means.
  • valve closing body has a partial spherical surface in the region of the valve seat and that the ratio of the diameter of the working piston (8) to twice the radius of the partial spherical surface (13) ⁇ 2.
  • valve seat or the valve closing body in the region of the valve seat has a large opening without the overall dimensions of the valve closing body are disproportionately large. This results in a sufficient and rapid filling of the high-pressure chamber, whereby a drop in the hydraulic valve clearance compensation element is prevented, even if additional surveys on the cam shorten the filling time significantly.
  • the valve closing body Following the partial spherical surface, the valve closing body has a cylindrical lateral surface which extends from the edge of the spherical surface.
  • a lightweight valve closing body is provided, which has a much lower mass, in contrast to conventional designed as a ball valve closing bodies, although the valve seat diameter is large.
  • valve closing body has a pin following the cylindrical surface, wherein the pin is enclosed by a valve closing spring, which is further supported in an opening of a valve cap.
  • a bore preferably a stepped bore, is provided, so that the high-pressure chamber can also fill along the valve closing spring, the pin and the stepped bore.
  • a blind hole be provided in the region of the partial spherical surface at the end of the valve closing body facing away from the journal. Through the blind hole, the mass of the valve closing body is further reduced and increases the oil reservoir.
  • the blind hole also serves as a collecting bag for contamination in the oil.
  • the radius of the closing spherical surface is greater than or equal to 2.5 mm.
  • the valve seat diameter is greater than or equal to 5.0 mm, wherein the diameter of the valve closing body is greater than or equal to 7.5 mm. This ensures that a complete filling of the high-pressure chamber takes place, even with intermediate surveys in the region of the base circle of the cams.
  • the valve cap is advantageously designed with a stepped inner diameter, wherein the large diameter of the circumferential surface of the valve closing body and the smaller diameter enclose the valve closing spring.
  • beads and openings are provided on the valve cap in the region of the large diameter, ranging from the high pressure chamber to the valve seat, to effect a sufficient and rapid filling of the high-pressure chamber.
  • 1 denotes a rocker arm which is pivotally mounted on a rocker shaft 2.
  • the rocker arm 1 is connected via a roller 3 with a cam 4 of a reciprocating internal combustion engine in operative connection.
  • the cam is part of a camshaft, which is designed for a reciprocating internal combustion engine for commercial vehicle and / or car use.
  • a generally designated 5 hydraulic valve clearance compensation element is installed, which is supplied via a channel with oil from the reciprocating internal combustion engine and / or another oil supply unit.
  • the hydraulic valve clearance compensation element 5 has a cylinder housing 7, which is displaceably guided in the rocker arm 1.
  • a working piston 8 is installed, the outward movement is limited in the cylinder housing 7 by a spring ring.
  • the working piston 8 is supported, as in FIG. 1 shown, attached to a fixed in the rocker arm 1 end plate 9.
  • a valve seat 11 connects to which a valve closing body 12 is associated.
  • the valve closing body 12 has a partial spherical surface 13, which merges into a cylindrical lateral surface 14. Following the cylindrical surface 14, a pin 15 is formed on the valve closing body 12, which is enclosed by a valve closing spring 16.
  • the valve closing spring 16 is further supported on a valve cap 17, which is firmly inserted in the working piston, for example, pressed, is. Between the valve cap 17 and the cylinder housing 7, a return spring 18 is installed, which acts on the working piston from the cylinder housing 7 away.
  • the space around the return spring 18 is formed as a high pressure chamber 19, which is dominated by the valve closing body 12, which prevents compression of the high-pressure chamber.
  • beads 20 and openings 21 are provided, which ensure rapid filling of the high-pressure chamber 19 from the storage space 10.
  • a blind hole 22 is incorporated, whereby the mass of the valve closing body is reduced, at the same time the storage space 10 is increased and a collecting bag is formed in the contaminants of the oil can be deposited.
  • the ratio of the diameter of the working piston to the diameter of the valve closing body, which is usually formed as a ball is above 3.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Gebiet der ErfindungField of the invention

Hubkolbenbrennkraftmaschine nach dem Vier-Takt-Verfahren mit einem Kurbelgehäuse und zumindest einem darin angeordneten Zylinder, in dem ein Kolben von einer Kurbelwelle geführt ist, mit zumindest einem den Zylinder verschließenden Zylinderkopf, dessen Ein- und Auslasskanäle von zumindest je einem mit einer Ventilfeder belasteten Ein- und Auslassventil beherrscht sind, die durch von einer Nockenwelle angetriebene Übertragungselemente betätigbar sind, und mit einem hydraulischen Ventilspiel-Ausgleichselement, das in zumindest eines der Übertragungselemente oder in ein im Übertragungselement eingebautes Bauteil zwischen Nockenwelle und zumindest einem Einund/oder Auslassventil eingebaut ist und einen Arbeitskolben, ein mit dem Arbeitskolben zusammenwirkendes Zylindergehäuse, eine dazwischen eingebaute Rückstellfeder und ein einen Hochdruckraum begrenzendes Rückschlagventil aufweist, dessen Ventilschließkörper mit einem Ventilsitz am Arbeitskolben korrespondiert.Reciprocating internal combustion engine according to the four-stroke method with a crankcase and at least one cylinder arranged therein, in which a piston is guided by a crankshaft, with at least one cylinder head closing the cylinder whose inlet and outlet ports of at least one each loaded with a valve spring Ein - And exhaust valve are controlled, which are actuated by driven by a camshaft transmission elements, and with a hydraulic valve clearance compensation element, which is installed in at least one of the transmission elements or in a transmission member between the camshaft and at least one inlet and / or exhaust valve and a Working piston, a cylinder housing cooperating with the working piston, a return spring installed therebetween and a non-return valve delimiting a high pressure chamber, the valve closing body of which corresponds to a valve seat on the working piston.

Hintergrund der ErfindungBackground of the invention

Hubkolbenbrennkraftmaschinen mit hydraulischen Ventilspiel-Ausgleichselementen nach dem Gattungsbegriff sind allgemein bekannt.
Sie haben das Problem, dass je nach Drehzahl der Hubkolbenbrennkraftmaschine und Hubhöhe der Nocken der Hochdruckraum der Ventilspiel-Ausgleichselemente sich nicht ausreichend füllen kann, so dass ein Absinken des hydraulischen Ventilspiel-Ausgleichselements auftreten kann, was zu erhöhtem oder unzulässig hohem Spiel in dem Ventiltrieb führt.
Andererseits ist es auch möglich, dass sich das hydraulische Ventilspiel-Ausgleichselement zu sehr aufpumpt, so dass das zulässige Ventilspiel unterschritten wird.Reciprocating internal combustion engines with hydraulic valve clearance compensation elements according to the preamble are well known.
You have the problem that, depending on the speed of the reciprocating internal combustion engine and lifting height of the cam, the high-pressure chamber of the valve clearance compensation elements can not fill sufficiently, so that a decrease in the hydraulic valve clearance compensation element may occur, resulting in increased or unduly high clearance in the valve train.
On the other hand, it is also possible that inflates the hydraulic valve clearance compensation element too much, so that the permissible valve clearance is exceeded.

Es ist bekannt, DE- 10 2007 014 248 A1 , am hydraulischen Ventilspiel-Ausgleichselement Anschlag- oder Klemmvorrichtungen vorzusehen, die extern betätigt werden und sowohl ein Aufpumpen als auch ein Absinken des hydraulischen Ventilspiel-Ausgleichselements verhindern. Derartige Anschlag-oder Klemmvorrichtungen sind baulich sehr aufwendig und kostenintensiv.It is known, DE-10 2007 014 248 A1 to provide on the hydraulic valve clearance compensation element stop or clamping devices which are actuated externally and prevent both a pumping and a lowering of the hydraulic valve clearance compensation element. Such stop or clamping devices are structurally very expensive and expensive.

Die Probleme sind besonders bedeutsam, wenn zu den hydraulischen Ventilspiel-Ausgleichselementen Bremssteuereinrichtungen oder Abgasrückführeinrichtungen an der Hubkolbenbrennkraftmaschine eingesetzt werden, wobei im Bereich des Grundkreises der Nocken Zusatzerhebungen vorgesehen sind.The problems are particularly significant when the hydraulic valve clearance compensation elements brake control devices or exhaust gas recirculation devices are used on the reciprocating internal combustion engine, wherein in the region of the base circle of the cam additional elevations are provided.

Aufgabe der ErfindungObject of the invention

Aufgabe der Erfindung ist es daher, die Nachteile der beschriebenen Maßnahmen an hydraulischen Ventilspiel-Ausgleichselementen zu beheben, insbesondere dahingehend, dass sowohl beim Normalbetrieb, insbesondere bei größeren Motoren für Nutzfahrzeuge, als auch beim Betrieb mit zusätzlichem Öffnen der Gaswechselventile zu Dekompressions- oder Abgasrückführzwecken kein Absinken der hydraulischen Ventilspiel-Ausgleichselemente auftritt. Dies soll mit einfachen Mitteln dargestellt werden.The object of the invention is therefore to eliminate the disadvantages of the measures described on hydraulic valve clearance compensation elements, in particular to the effect that both during normal operation, especially in larger engines for commercial vehicles, as well as in operation with additional opening of the gas exchange valves for decompression or exhaust gas recirculation no Decrease of the hydraulic valve clearance compensation elements occurs. This should be presented with simple means.

Zusammenfassung der ErfindungSummary of the invention

Die Aufgabe der Erfindung wird dadurch gelöst, dass der Ventilschließkörper eine partielle Kugeloberfläche im Bereich des Ventilsitzes aufweist und dass das Verhältnis des Durchmessers des Arbeitskolbens (8) zum doppelten Radius der partiellen Kugeloberfläche (13) ≤ 2 ist.The object of the invention is achieved in that the valve closing body has a partial spherical surface in the region of the valve seat and that the ratio of the diameter of the working piston (8) to twice the radius of the partial spherical surface (13) ≤ 2.

Dadurch wird erreicht, dass der Ventilsitz bzw. der Ventilschließkörper im Bereich des Ventilsitzes eine große Öffnung aufweist, ohne dass die Gesamtabmessungen des Ventilschließkörpers unverhältnismäßig groß sind. Dadurch erfolgt ein hinreichendes und schnelles Befüllen des Hochdruckraumes, wodurch ein Absinken des hydraulischen Ventilspiel-Ausgleichselement verhindert wird, dies auch dann, wenn Zusatzerhebungen am Nocken die Füllzeit wesentlich verkürzen.This ensures that the valve seat or the valve closing body in the region of the valve seat has a large opening without the overall dimensions of the valve closing body are disproportionately large. This results in a sufficient and rapid filling of the high-pressure chamber, whereby a drop in the hydraulic valve clearance compensation element is prevented, even if additional surveys on the cam shorten the filling time significantly.

Der Ventilschließkörper weist im Anschluss an die partielle Kugeloberfläche eine zylindrische Mantelfläche auf, die vom Rand der Kugeloberfläche ausgeht. Dadurch wird ein leichter Ventilschließkörper zur Verfügung gestellt, der im Gegensatz zu üblichen als Kugel ausgebildeten Ventilschließkörpern eine wesentlich geringere Masse aufweist, obwohl der Ventilsitzdurchmesser groß ist.Following the partial spherical surface, the valve closing body has a cylindrical lateral surface which extends from the edge of the spherical surface. As a result, a lightweight valve closing body is provided, which has a much lower mass, in contrast to conventional designed as a ball valve closing bodies, although the valve seat diameter is large.

In weiterer Ausgestaltung der Erfindung wird vorgeschlagen, dass der Ventilschließkörper im Anschluss an die zylindrische Mantelfläche einen Zapfen aufweist, wobei der Zapfen von einer Ventilschließfeder umschlossen ist, die sich weiterhin in einer Öffnung einer Ventilkappe abstützt. Dadurch wird eine zusätzliche Führung des Ventilschließkörpers erreicht.In a further embodiment of the invention it is proposed that the valve closing body has a pin following the cylindrical surface, wherein the pin is enclosed by a valve closing spring, which is further supported in an opening of a valve cap. As a result, an additional guidance of the valve closing body is achieved.

Im Anschluss an die Öffnung in der Ventilkappe ist eine Bohrung, vorzugsweise eine Stufenbohrung, vorgesehen, so dass sich der Hochdruckraum auch entlang der Ventilschließfeder, des Zapfens und der Stufenbohrung füllen kann.Subsequent to the opening in the valve cap, a bore, preferably a stepped bore, is provided, so that the high-pressure chamber can also fill along the valve closing spring, the pin and the stepped bore.

Weiterhin wird vorgeschlagen, dass an dem dem Zapfen abgewandten Ende des Ventilschließkörpers im Bereich der partiellen Kugeloberfläche ein Sackloch vorgesehen ist. Durch das Sackloch wird die Masse des Ventilschließkörpers weiter reduziert und der Ölvorratsraum vergrößert. Das Sackloch dient auch als Auffangtasche für Kontaminationen im Öl.Furthermore, it is proposed that a blind hole be provided in the region of the partial spherical surface at the end of the valve closing body facing away from the journal. Through the blind hole, the mass of the valve closing body is further reduced and increases the oil reservoir. The blind hole also serves as a collecting bag for contamination in the oil.

In weiterer Ausgestaltung der Erfindung wird vorgeschlagen, dass der Radius der schließenden Kugeloberfläche größer oder gleich 2,5 mm ist.In a further embodiment of the invention, it is proposed that the radius of the closing spherical surface is greater than or equal to 2.5 mm.

Der Ventilsitzdurchmesser ist dabei größer oder gleich 5,0 mm, wobei der Durchmesser des Ventilschließkörpers größer oder gleich 7,5 mm ist. Dadurch wird sichergestellt, dass eine vollständige Füllung des Hochdruckraumes erfolgt, auch bei Zwischenerhebungen im Bereich des Grundkreises der Nocken.The valve seat diameter is greater than or equal to 5.0 mm, wherein the diameter of the valve closing body is greater than or equal to 7.5 mm. This ensures that a complete filling of the high-pressure chamber takes place, even with intermediate surveys in the region of the base circle of the cams.

Dies beruht darauf, dass der Durchmesser des Arbeitskolbens und der Öffnungsquerschnitt der Rückschlagventils für die Funktionsweise des hydraulischen Ventilspiel-Ausgleichselements von besonderer Bedeutung sind.This is due to the fact that the diameter of the working piston and the opening cross section of the check valve for the operation of the hydraulic valve clearance compensation element are of particular importance.

Die Ventilkappe ist in vorteilhafter Weise mit gestuftem Innendurchmesser ausgeführt, wobei der große Durchmesser die Mantelfläche des Ventilschließkörpers und der kleinere Durchmesser die Ventilschließfeder umschließen.The valve cap is advantageously designed with a stepped inner diameter, wherein the large diameter of the circumferential surface of the valve closing body and the smaller diameter enclose the valve closing spring.

Dabei sind an der Ventilkappe im Bereich des großen Durchmessers Sicken und Öffnungen vorgesehen, die vom Hochdruckraum bis zum Ventilsitz reichen, um ein ausreichendes und schnelles Füllen des Hochdruckraumes zu bewirken.In this case, beads and openings are provided on the valve cap in the region of the large diameter, ranging from the high pressure chamber to the valve seat, to effect a sufficient and rapid filling of the high-pressure chamber.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Zur weiteren Erläuterung der Erfindung wird auf die Zeichnungen verwiesen, in denen ein Ausführungsbeispiel der Erfindung vereinfacht dargestellt ist.
Es zeigen:

  • Figur 1: einen Schnitt durch einen als Übertragungselement ausgebildeten Kipphebel mit hydraulischem Ventilspiel-Ausgleichselement, der über eine Rolle mit einem Nocken einer Nockenwelle in Verbindung steht und
  • Figur 2: einen Schnitt durch das hydraulische Ventilspiel-Ausgleichselement in vergrößertem Maßstab.
For further explanation of the invention reference is made to the drawings, in which an embodiment of the invention is shown in simplified form.
Show it:
  • FIG. 1 a section through a transmission element designed as a rocker arm with hydraulic valve clearance compensation element, which is connected via a roller with a cam of a camshaft and
  • FIG. 2 a section through the hydraulic valve clearance compensation element in an enlarged scale.

Detaillierte Beschreibung der ZeichnungenDetailed description of the drawings

In den Figuren 1 und 2 ist, soweit im Einzelnen dargestellt, mit 1 ein Kipphebel bezeichnet, der auf einer Kipphebelachse 2 schwenkbar gelagert ist. Der Kipphebel 1 steht über eine Rolle 3 mit einem Nocken 4 einer Hubkolbenbrennkraftmaschine in Wirkverbindung. Der Nocken ist Bestandteil einer Nockenwelle, die zu einer Hubkolbenbrennkraftmaschine für den Nutzfahrzeug- und/oder PKW-einsatz ausgelegt ist.In the Figures 1 and 2 is, as far as shown in detail, 1 denotes a rocker arm which is pivotally mounted on a rocker shaft 2. The rocker arm 1 is connected via a roller 3 with a cam 4 of a reciprocating internal combustion engine in operative connection. The cam is part of a camshaft, which is designed for a reciprocating internal combustion engine for commercial vehicle and / or car use.

An dem freien Ende des Kipphebels 1 ist ein allgemein mit 5 bezeichnetes hydraulisches Ventilspiel-Ausgleichselement eingebaut, das über einen Kanal mit Öl von der Hubkolbenbrennkraftmaschine und/oder einer anderen Ölversorgungseinheit versorgt wird.At the free end of the rocker arm 1, a generally designated 5 hydraulic valve clearance compensation element is installed, which is supplied via a channel with oil from the reciprocating internal combustion engine and / or another oil supply unit.

Das hydraulische Ventilspiel-Ausgleichselement 5 weist ein Zylindergehäuse 7 auf, das verschiebbar im Kipphebel 1 geführt ist. Im Zylindergehäuse 7 ist ein Arbeitskolben 8 eingebaut, dessen Auswärtsbewegung im Zylindergehäuse 7 durch einen Federring begrenzt ist. Der Arbeitskolben 8 stützt sich, wie in Figur 1 dargestellt, an einer im Kipphebel 1 befestigten Abschlussplatte 9 ab. An einen Hohlraum im Arbeitskolben 8, der als Vorratsraum 10 für Öl ausgebildet ist, schließt sich ein Ventilsitz 11 an, dem ein Ventilschließkörper 12 zugeordnet ist. Der Ventilschließkörper 12 weist eine partielle Kugeloberfläche 13 auf, die in eine zylindrische Mantelfläche 14 übergeht. Im Anschluss an die zylindrische Mantelfläche 14 ist am Ventilschließkörper 12 ein Zapfen 15 angeformt, der von einer Ventilschließfeder 16 umschlossen ist. Die Ventilschließfeder 16 stützt sich weiterhin an einer Ventilkappe 17 ab, die fest im Arbeitskolben eingesetzt, beispielsweise eingepresst, ist. Zwischen der Ventilkappe 17 und dem Zylindergehäuse 7 ist eine Rückstellfeder 18 eingebaut, die den Arbeitskolben vom Zylindergehäuse 7 weg beaufschlagt. Der Raum um die Rückstellfeder 18 ist als Hochdruckraum 19 ausgebildet, der von dem Ventilschließkörper 12 beherrscht ist, der ein Zusammendrücken des Hochdruckraumes verhindert. In der den Ventilschließkörper 12 umgebenden Wandung der Ventilkappe 17 sind Sicken 20 und Öffnungen 21 vorgesehen, die eine schnelle Füllung des Hochdruckraumes 19 aus dem Vorratsraum 10 sicherstellen.The hydraulic valve clearance compensation element 5 has a cylinder housing 7, which is displaceably guided in the rocker arm 1. In the cylinder housing 7, a working piston 8 is installed, the outward movement is limited in the cylinder housing 7 by a spring ring. The working piston 8 is supported, as in FIG. 1 shown, attached to a fixed in the rocker arm 1 end plate 9. To a cavity in the working piston 8, which is designed as a reservoir 10 for oil, a valve seat 11 connects to which a valve closing body 12 is associated. The valve closing body 12 has a partial spherical surface 13, which merges into a cylindrical lateral surface 14. Following the cylindrical surface 14, a pin 15 is formed on the valve closing body 12, which is enclosed by a valve closing spring 16. The valve closing spring 16 is further supported on a valve cap 17, which is firmly inserted in the working piston, for example, pressed, is. Between the valve cap 17 and the cylinder housing 7, a return spring 18 is installed, which acts on the working piston from the cylinder housing 7 away. The space around the return spring 18 is formed as a high pressure chamber 19, which is dominated by the valve closing body 12, which prevents compression of the high-pressure chamber. In the wall surrounding the valve closing body 12 of the valve cap 17, beads 20 and openings 21 are provided, which ensure rapid filling of the high-pressure chamber 19 from the storage space 10.

An dem dem Zapfen 15 abgewandten Ende des Ventilschließkörpers 12 ist ein Sackloch 22 eingearbeitet, wodurch die Masse des Ventilschließkörpers verringert wird, gleichzeitig der Vorratsraum 10 vergrößert wird und eine Auffangtasche ausgebildet ist, in der Kontaminationen des Öls sich ablagern können.At the end facing away from the pin 15 of the valve closing body 12, a blind hole 22 is incorporated, whereby the mass of the valve closing body is reduced, at the same time the storage space 10 is increased and a collecting bag is formed in the contaminants of the oil can be deposited.

Abschließend sei noch einmal darauf hingewiesen, dass üblicherweise das Verhältnis des Durchmessers des Arbeitskolbens zum Durchmesser des Ventilschließkörpers, der üblicherweise als Kugel ausgebildet ist, über 3 liegt. Im vorliegenden Fall ist das Verhältnis bei gleichbleibendem Durchmesser des Arbeitskolbens und einem Radius der partiellen Kugeloberfläche von r = 4 mm ≤ 2.Finally, it should be pointed out again that usually the ratio of the diameter of the working piston to the diameter of the valve closing body, which is usually formed as a ball, is above 3. In the present case, the ratio is at a constant diameter of the working piston and a radius of the partial spherical surface of r = 4 mm ≤ 2.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Kipphebelrocker arm
22
Kipphebelachserocker shaft
33
Rollerole
44
Nockencam
55
hydraulisches Ventilspiel-Ausgleichselementhydraulic valve clearance compensation element
66
Kanalchannel
77
Zylindergehäusecylinder housing
88th
Arbeitskolbenworking piston
99
AbschlussplatteEnd plate
1010
Vorratsraumpantry
1111
Ventilsitzvalve seat
1212
VentilschließkörperValve closing body
1313
partielle Kugeloberflächepartial sphere surface
1414
zylindrische Mantelflächecylindrical surface
1515
Zapfenspigot
1616
VentilschließfederValve closing spring
1717
Ventilkappevalve cap
1818
RückstellfederReturn spring
1919
HochdruckraumHigh-pressure chamber
2020
Sickenbeading
2121
Öffnungopening
2222
Sacklochblind

Claims (11)

  1. Reciprocating-piston internal combustion engine operating by the four-stroke method, with a crankcase and with at least one cylinder which is arranged therein and in which a piston is guided by a crankshaft, with at least one cylinder head which closes the cylinder and the inlet and outlet ducts of which are controlled in each case by at least one inlet and outlet valve which are loaded by a valve spring and which can be actuated by transmission elements driven by a camshaft, and with a hydraulic valve-play compensating element (5) which is installed between the camshaft and at least one inlet and/or outlet valve in at least one of the transmission elements or in a component installed in the transmission element and which has a working piston (8), a cylinder housing (7) cooperating with the working piston (8), a restoring spring (18) installed between them and a non-return valve which delimits a high-pressure space (19) and the valve-closing body (12) of which matches with a valve seat (11) on the working piston (8), characterized in that the valve-closing body (12) has a partial spherical surface (13) in the region of the valve seat (11), and in that the ratio of the diameter of the working piston (8) to double the radius of the partial spherical surface (13) is ≤ 2.
  2. Reciprocating-piston internal combustion engine according to Claim 1, characterized in that a cylindrical surface area (14) adjoins the partial spherical surface (13) in the region of the valve seat (11).
  3. Reciprocating-piston internal combustion engine according to either one of Claims 1 and 2, characterized in that the valve-seat diameter is ≥ 5.0 mm.
  4. Reciprocating-piston internal combustion engine according to one of Claims 1 to 3, characterized in that the diameter of the valve-closing body (12) is ≥ 7.5 mm.
  5. Reciprocating-piston internal combustion engine according to one of Claims 1 to 4, characterized in that a blind hole (22) facing away from the high-pressure space (19) is provided in the region of the partial spherical surface (13), preferably at its centre.
  6. Reciprocating-piston internal combustion engine according to one of Claims 1 to 5, characterized in that the radius of the partial spherical surface (13) is ≥ 2.5 mm.
  7. Reciprocating-piston internal combustion engine according to one of the preceding claims, characterized in that the valve-closing body (12) has, adjoining the cylindrical surface area (14), a tenon (15).
  8. Reciprocating-piston internal combustion engine according to one of the preceding claims, characterized in that the tenon (15) is surrounded by a valve-closing spring (16) which, furthermore, is supported in an orifice of a valve cap (17).
  9. Reciprocating-piston internal combustion engine according to one of the preceding claims, characterized in that a bore, preferably a stepped bore, is provided, adjoining the orifice in the valve cap (17).
  10. Reciprocating-piston internal combustion engine according to one of the preceding claims, characterized in that the valve cap (17) is formed with a stepped inside diameter, the large inside diameter surrounding the cylindrical surface area (14) of the valve-closing body (12) and the smaller diameter surrounding the valve-closing spring (16).
  11. Reciprocating-piston internal combustion engine according to one of the preceding claims, characterized in that beads (20) or orifices (21), which reach from the high-pressure space (19) as far as the valve seat (11), are provided on the valve cap (17) in the region of the large diameter.
EP11715902.0A 2010-04-26 2011-04-13 Hydraulic valve play compensating element for reciprocating-piston internal combustion engines Active EP2564038B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010018208A DE102010018208A1 (en) 2010-04-26 2010-04-26 Hydraulic valve clearance compensation element for reciprocating internal combustion engines
PCT/EP2011/055753 WO2011134790A2 (en) 2010-04-26 2011-04-13 Hydraulic valve play compensating element for reciprocating-piston internal combustion engines

Publications (2)

Publication Number Publication Date
EP2564038A2 EP2564038A2 (en) 2013-03-06
EP2564038B1 true EP2564038B1 (en) 2014-09-17

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EP11715902.0A Active EP2564038B1 (en) 2010-04-26 2011-04-13 Hydraulic valve play compensating element for reciprocating-piston internal combustion engines

Country Status (4)

Country Link
US (1) US20130000573A1 (en)
EP (1) EP2564038B1 (en)
DE (1) DE102010018208A1 (en)
WO (1) WO2011134790A2 (en)

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DE102015216291B3 (en) * 2015-08-26 2016-11-03 Schaeffler Technologies AG & Co. KG Hydraulic compensating element of a valve train
DE102015220628B3 (en) * 2015-10-22 2016-10-27 Schaeffler Technologies AG & Co. KG Flat or roller plunger for a reciprocating internal combustion engine
CN105736086B (en) * 2016-02-02 2018-06-29 吉林大学 The engine braking methods and decompressor that burning braking is combined with pressure m
US11242774B2 (en) * 2019-09-20 2022-02-08 Caterpillar Inc. Rocker assembly with a hydraulic lash adjuster
CN111720184B (en) * 2020-06-29 2024-07-02 杭州新坐标科技股份有限公司 Plane hydraulic support piece for large-sized engine

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Also Published As

Publication number Publication date
DE102010018208A1 (en) 2011-10-27
WO2011134790A3 (en) 2012-03-15
US20130000573A1 (en) 2013-01-03
EP2564038A2 (en) 2013-03-06
WO2011134790A2 (en) 2011-11-03

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