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EP0634564B1 - Deactivating device for internal combustion engine valve - Google Patents

Deactivating device for internal combustion engine valve Download PDF

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Publication number
EP0634564B1
EP0634564B1 EP94106892A EP94106892A EP0634564B1 EP 0634564 B1 EP0634564 B1 EP 0634564B1 EP 94106892 A EP94106892 A EP 94106892A EP 94106892 A EP94106892 A EP 94106892A EP 0634564 B1 EP0634564 B1 EP 0634564B1
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EP
European Patent Office
Prior art keywords
bearing pin
pin
locking
locking pin
internal combustion
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94106892A
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German (de)
French (fr)
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EP0634564A1 (en
Inventor
Albert Hörl-Liegl
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Bayerische Motoren Werke AG
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Bayerische Motoren Werke AG
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Publication of EP0634564A1 publication Critical patent/EP0634564A1/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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves

Definitions

  • the invention relates to a device for decommissioning a lift valve actuated by a cam via a rocker arm of an internal combustion engine, with a bearing pin forming an abutment for the rocker arm, which is arranged longitudinally displaceably against a spring element, and with a locking pin for blocking the bearing pin.
  • a device of this type is shown for a rocker arm in DE 32 39 941 A1.
  • a device with which an individual lift valve of an internal combustion engine can be shut down individually, is convincing, but further improvements are desirable, which the present invention has set out to demonstrate.
  • the bearing pin and the locking pin are mounted in a housing insert, which in turn is supported by a play compensation element in the cylinder head of the internal combustion engine.
  • a device according to the invention for decommissioning an internal combustion engine lift valve is characterized in particular by a lash adjuster, preferably by a commercially available hydraulic lash adjuster. Time-consuming adjustment work or readjustment work for the desired valve clearance is no longer necessary.
  • play compensation elements have long been state of the art, but the invention proposes a particularly favorable arrangement. Accordingly, both the bearing pin forming the abutment for the rocker arm and its locking pin are mounted in a housing insert, which in turn is supported on the internal combustion engine cylinder head via the hydraulic play compensation element. Because of this arrangement, no additional elaborate guide elements are required for the integration of a play compensation element in a valve train according to the preamble of claim 1.
  • the reference number 1 denotes a globe valve which, as usual, is mounted with its valve guide 2 and a valve spring 3 and a spring plate 4 in the cylinder head 5 of the internal combustion engine.
  • a rocker arm 6 acts on the stem of the lift valve, which is designed here as a roller rocker arm and which in turn is actuated by a cam 7.
  • the rocker arm 6 With its end opposite the stem of the lift valve 1, the rocker arm 6 is supported on a bearing pin 8 from.
  • This bearing pin 8 is guided in a longitudinally displaceable manner in the direction of the arrow 9 in a housing insert 10, which is likewise mounted in the cylinder head 5 in a slightly longitudinally displaceable manner in the direction of the arrow 9.
  • the housing insert 10 is supported on a play-compensating element, designated in its entirety with 11, which is also mounted in the cylinder head, specifically in a blind hole 12.
  • the hydraulic play-compensating element 11 is a common component known to the person skilled in the art and is therefore of a construction and design its function not explained in detail.
  • a locking pin 13 is likewise mounted in the housing insert 10. This locking pin 13 is guided in a longitudinally displaceable manner in a transverse bore 14 in the housing insert 10 in the direction of the arrow 15 and can therefore also be in addition to the position shown, in which the locking pin is located in a side space 16 away from the bearing pin 8 assume a position below the bearing pin 8, as is shown only in dashed lines for the contour of the locking pin 13.
  • the lift valve 1 is actuated as usual, that is to say opened in the direction of the arrow 17, since through the locking pin 13 a displacement movement of the bearing pin 8 according to the direction of arrow 9 is excluded. If, on the other hand, the locking pin 13 is located completely within the side space 16, the bearing pin 8 is moved downward according to the direction of the arrow 9 instead of the lift valve 1 when the cam 7 rotates about its cam axis 7 ', so that the lift valve 1 is closed remains.
  • valve clearance compensation required in a modern valve train is taken over by a play compensation element 11, on which the housing insert 10 is supported in the cylinder head 5.
  • the required valve clearance is automatically maintained, as is known.
  • slight relative movements can also occur between the bearing pin 8 and the housing insert 10. If the locking pin 13 is located in the side space 16, the bearing pin 8 can be pushed slightly into the transverse bore 14 as part of these slight relative movements.
  • the end face 19 of the bearing pin 8 inclined relative to the direction of movement 15 of the locking pin 13 such that the clear width w between the end face 19 and the opposite housing insert wall 20 from the left edge of the bearing pin 8 or the transverse bore 14 facing away from the side space 16 to the right longitudinal edge facing the side space of the bearing pin 8 or to the side space 16 increases.
  • the end edges 21 of the bearing pin 13 are also beveled, even if the bearing pin 8 with its end face 19 protrudes slightly into the transverse bore 14 due to slight displacements of the housing insert 10 in the cylinder head 5, the locking pin 13 is always safe and can be reliably pushed out of the position shown to the left under the bearing pin 8 to block it.
  • this design also completely compensates for component tolerances and manufacturing tolerances.
  • the locking pin 13 is displaceable transversely to the bearing pin 8 over its entire end face 19, that is to say when the bearing pin 8 is blocked, the latter is supported with its substantially entire end face 19 on the locking pin 13, the mechanical stress on the components concerned is minimized or minimized as far as possible at least optimized.
  • the locking bolt 13 is actuated or moved hydraulically, into its rest position - in this rest position the cup-shaped locking bolt lies completely within the side space 16 against a rest stop, which is formed by a pin 22 - this locking bolt 13 is moved back by a tension spring 23 This tension spring 23 is arranged essentially within the cup-shaped locking bolt 13 and is hung on the bottom of the pin on the one hand and on the pin 22 on the other hand. If the locking pin 13 is thus to be shifted from the position shown to the left in the direction of arrow 15, the interior of the cup is subjected to a suitable hydraulic pressure. Because of the described beveling of the end face 19 and the end edges 21, the locking pin 13 can then slide completely under the bearing pin 8 and thus prevent a displacement of the same according to arrow direction 9.
  • the lift valve 1 is then actuated in accordance with the cam lift when the cam 7 is rotated. If, on the other hand, the hydraulic pressure acting on the locking pin 13 is withdrawn, this locking pin 13 slides back into its rest position due to the force of the tension spring 23 and completely reaches the side space 16 which, as already described, is delimited by the pin 22. As also already described, when the cam 7 rotates, the cam lift is carried out completely or at least essentially by the bearing pin 8 according to the direction of arrow 9, the lift valve 1 remains completely or at least essentially closed. A slight stroke of the lift valve 1 can, however, also be desirable and result from the fact that the possible displacement path of the bearing pin 8 is not sufficient for a complete implementation of the stroke of the cam 7.
  • a transverse pin 24 is mounted in the housing insert 10, which at least partially penetrates the bearing pin 8 in a longitudinal groove 25.
  • the longitudinal groove 25 is required to enable the bearing pin 8 to move in the direction of the arrow 9.
  • the transverse pin 24 also represents an end stop for the bearing pin 8 within the housing insert 10, so that the housing insert 10 including the bearing pin 8 and locking pin 13 can be installed as a pre-assembly unit in the cylinder head 5 and thereby automatically adjusts a valve drive without play .
  • This preassembly unit which of course also contains the compression spring 18 and the tension spring 23 on the other elements described in connection with the housing insert 10, is centered by the eccentric shoulder 26 in the blind hole 12 and thus also in the cylinder head 5.
  • the area of the housing insert 10 lying above the shoulder 26 and essentially receiving the locking pin 13 in the transverse bore 14 is of circular cylindrical design.
  • the housing insert 10 has a stop 27, which becomes effective when the play compensation element 11 is not active, on which the compression spring 18 is supported at the same time.
  • the distance between the stop 27 and the paragraph below it in the cylinder head 5 represents the working area of the play compensation element 11.
  • a hydraulic channel which conveys the hydraulic medium required for a movement of the locking pin 13 into the interior of this cup-shaped locking pin 13, is not shown.
  • This hydraulic pressure can be applied in a targeted manner by means of a suitable control valve, but quasi-automatic regulation is possible depending on the speed of the internal combustion engine and the lubricating oil pressure that increases almost proportionally, if the lubricating oil of the internal combustion engine is used as the hydraulic fluid actuating the locking pin 13. Since the device described should preferably be used on internal combustion engines which have a plurality of intake lift valves per cylinder, with at least one of these intake lift valves being able to be put out of operation, the automatic control mechanism described above via the oil pressure of the internal combustion engine corresponds exactly to the one then present Control requirements.

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

Description

Die Erfindung betrifft eine Vorrichtung zum Außerbetriebsetzen eines von einem Nocken über einen Schwinghebel betätigten Hubventiles einer Brennkraftmaschine, mit einem ein Widerlager für den Schwinghebel bildenden Lagerbolzen, der gegen ein Federelement längsverschiebbar angeordnet ist, sowie mit einem Sperrbolzen zum Blockieren des Lagerbolzens.The invention relates to a device for decommissioning a lift valve actuated by a cam via a rocker arm of an internal combustion engine, with a bearing pin forming an abutment for the rocker arm, which is arranged longitudinally displaceably against a spring element, and with a locking pin for blocking the bearing pin.

Eine Vorrichtung dieser Art ist für einen Kipphebel in der DE 32 39 941 Al gezeigt. Vom Grundsatzgedanken her ist eine derartige Vorrichtung, mit der individuell ein einzelnes Hubventil einer Brennkraftmaschine stillgesetzt werden kann, überzeugend, jedoch sind weitere Verbesserungen wünschenswert, die aufzuzeigen sich die vorliegende Erfindung zur Aufgabe gestellt hat.
Zur Lösung dieser Aufgabe ist vorgesehen, daß der Lagerbolzen sowie der Sperrbolzen in einem Gehäuseeinsatz gelagert sind, der seinerseits unter Abstützung auf einem Spielausgleichselement im Zylinderkopf der Brennkraftmaschine gelagert ist. Vorteilhafte Aus- und Weiterbildungen der Erfindung sind im abhängigen Patentanspruch aufgelistet.A device of this type is shown for a rocker arm in DE 32 39 941 A1. In principle, such a device, with which an individual lift valve of an internal combustion engine can be shut down individually, is convincing, but further improvements are desirable, which the present invention has set out to demonstrate.
To solve this problem, it is provided that the bearing pin and the locking pin are mounted in a housing insert, which in turn is supported by a play compensation element in the cylinder head of the internal combustion engine. Advantageous developments and further developments of the invention are listed in the dependent claim.

Eine erfindungsgemäße Vorrichtung zum Außerbetriebsetzen eines Brennkraftmaschinen-Hubventiles ist insbesondere durch ein Spielausgleichselement, bevorzugt durch ein handelsübliches hydraulisches Spielausgleichselement gekennzeichnet. Aufwendige Einstellarbeiten bzw. Nachstellarbeiten für das gewünschte Ventilspiel sind soweit nicht mehr erforderlich. Selbstverständlich sind derartige Spielausgleichselemente seit langem Stand der Technik, jedoch schlägt die Erfindung eine besonders günstige Anordnung vor. Demnach ist sowohl der das Widerlager für den Schwinghebel bildende Lagerbolzen als auch dessen Sperrbolzen in einem Gehäuseeinsatz gelagert, welcher sich seinerseits über das hydraulische Spielausgleichselement am Brennkraftmaschinen-Zylinderkopf abstützt. Aufgrund dieser Anordnung sind für die Einbindung eines Spielausgleichselementes in einen Ventiltrieb nach dem Oberbegriff des Anspruchs 1 keine zusätzlichen aufwendigen Führungselemente erforderlich. Dies sowie weitere Vorteile der Erfindung und ggf. erfindungswesentliche Merkmale geht auch aus der folgenden Beschreibung eines bevorzugten Ausführungsbeispieles der Erfindung hervor.A device according to the invention for decommissioning an internal combustion engine lift valve is characterized in particular by a lash adjuster, preferably by a commercially available hydraulic lash adjuster. Time-consuming adjustment work or readjustment work for the desired valve clearance is no longer necessary. Of course, such play compensation elements have long been state of the art, but the invention proposes a particularly favorable arrangement. Accordingly, both the bearing pin forming the abutment for the rocker arm and its locking pin are mounted in a housing insert, which in turn is supported on the internal combustion engine cylinder head via the hydraulic play compensation element. Because of this arrangement, no additional elaborate guide elements are required for the integration of a play compensation element in a valve train according to the preamble of claim 1. This as well as further advantages of the invention and, if applicable, features essential to the invention can also be seen from the following description of a preferred embodiment of the invention.

In der einzigen Figur ist ein Teil-Querschnitt durch einen Brennkraftmaschinen-Zylinderkopf im Ventiltriebsbereich gezeigt. Mit der Bezugsziffer 1 ist ein Hubventil bezeichnet, das wie üblich mit seiner Ventilführung 2 sowie einer Ventilfeder 3 und einem Federteller 4 im Zylinderkopf 5 der Brennkraftmaschine gelagert ist. Ebenfalls wie üblich wirkt auf den Schaft des Hubventiles ein Schwinghebel 6 ein, der hier als Rollen-Schwinghebel ausgebildet ist und der seinerseits von einem Nocken 7 betätigt wird.In the single figure, a partial cross section through an internal combustion engine cylinder head in the valve train area is shown. The reference number 1 denotes a globe valve which, as usual, is mounted with its valve guide 2 and a valve spring 3 and a spring plate 4 in the cylinder head 5 of the internal combustion engine. As usual, a rocker arm 6 acts on the stem of the lift valve, which is designed here as a roller rocker arm and which in turn is actuated by a cam 7.

Mit seinem dem Schaft des Hubventiles 1 gegenüberliegenden Ende stützt sich der Schwinghebel 6 auf einem Lagerbolzen 8 ab. Dieser Lagerbolzen 8 ist gemäß Pfeilrichtung 9 längsverschiebbar in einem Gehäuseeinsatz 10 geführt, der ebenfalls gemäß Pfeilrichtung 9 geringfügig längsverschiebbar im Zylinderkopf 5 gelagert ist. Dabei stützt sich der Gehäuseeinsatz 10 auf einem in seiner Gesamtheit mit 11 bezeichneten Spielausgleichselement ab, das ebenfalls im Zylinderkopf gelagert ist, und zwar in einem Sackloch 12. Das hydraulische Spielausgleichselement 11 ist ein gängiges, dem Fachmann bekanntes Bauelement und wird daher in seinem Aufbau und seiner Funktion nicht näher erläutert.With its end opposite the stem of the lift valve 1, the rocker arm 6 is supported on a bearing pin 8 from. This bearing pin 8 is guided in a longitudinally displaceable manner in the direction of the arrow 9 in a housing insert 10, which is likewise mounted in the cylinder head 5 in a slightly longitudinally displaceable manner in the direction of the arrow 9. In this case, the housing insert 10 is supported on a play-compensating element, designated in its entirety with 11, which is also mounted in the cylinder head, specifically in a blind hole 12. The hydraulic play-compensating element 11 is a common component known to the person skilled in the art and is therefore of a construction and design its function not explained in detail.

Ebenfalls im Gehäuseeinsatz 10 gelagert ist ein Sperrbolzen 13. Dieser Sperrbolzen 13 ist in einer Querbohrung 14 im Gehäuseeinsatz 10 gemäß Pfeilrichtung 15 längsverschiebbar geführt und kann somit neben der gezeigten Position, in der sich der Sperrbolzen abseits des Lagerbolzens 8 in einem Seitenraum 16 befindet, auch eine Position unterhalb des Lagerbolzens 8 einnehmen, wie dies für die Kontur des Sperrbolzens 13 lediglich strichliert dargestellt ist. Befindet sich dabei der Sperrbolzen 13 in der letztgenannten Position, d. h. linksseitig in der Querbohrung 14 unterhalb des Lagerbolzens 8, so wird bei einer Drehbewegung des Nockens 7 um seine Nockenachse 7' das Hubventil 1 wie üblich betätigt, d. h. gemäß Pfeilrichtung 17 geöffnet, da durch den Sperrbolzen 13 eine Verschiebebewegung des Lagerbolzens 8 gemäß Pfeilrichtung 9 ausgeschlossen ist. Befindet sich hingegen der Sperrbolzen 13 - wie dargestellt - vollständig innerhalb des Seitenraumes 16, so wird bei einer Rotation des Nockens 7 um seine Nockenachse 7' anstelle des Hubventiles 1 der Lagerbolzen 8 gemäß Pfeilrichtung 9 nach unten bewegt, so daß hierbei das Hubventil 1 geschlossen bleibt. Wälzt schließlich der Nocken wieder mit seiner Grundkreisphase auf dem Schwinghebel 6 ab, so wird der Lagerbolzen 8 durch die Druckfeder 18, die zwischen dem Lagerbolzen 8 sowie dem Gehäuseeinsatz 10 eingespannt ist, in die gezeigte Position zurückgefahren, so daß stets der Schwinghebel 6 mit seiner Rolle 6' am Nocken 7 anliegt. Eine wesentliche Voraussetzung für den zuletzt geschilderten Bewegungsablauf ist es dabei selbstverständlich, daß die Druckfeder 18 zwischen dem Lagerbolzen 8 sowie dem Gehäuseeinsatz 10 eine geringere Federkraft oder eine andere progressive Federkennlinie aufweist, als die Ventilfeder 3.A locking pin 13 is likewise mounted in the housing insert 10. This locking pin 13 is guided in a longitudinally displaceable manner in a transverse bore 14 in the housing insert 10 in the direction of the arrow 15 and can therefore also be in addition to the position shown, in which the locking pin is located in a side space 16 away from the bearing pin 8 assume a position below the bearing pin 8, as is shown only in dashed lines for the contour of the locking pin 13. If the locking pin 13 is in the latter position, ie on the left-hand side in the transverse bore 14 below the bearing pin 8, when the cam 7 rotates about its cam axis 7 ', the lift valve 1 is actuated as usual, that is to say opened in the direction of the arrow 17, since through the locking pin 13 a displacement movement of the bearing pin 8 according to the direction of arrow 9 is excluded. If, on the other hand, the locking pin 13 is located completely within the side space 16, the bearing pin 8 is moved downward according to the direction of the arrow 9 instead of the lift valve 1 when the cam 7 rotates about its cam axis 7 ', so that the lift valve 1 is closed remains. Finally, if the cam rolls again with its base circle phase on the rocker arm 6, the bearing pin 8 is moved by the compression spring 18, which is located between the bearing pin 8 and the housing insert 10 is clamped, moved back into the position shown, so that the rocker arm 6 always rests with its roller 6 'on the cam 7. An essential requirement for the last-described movement sequence is, of course, that the compression spring 18 between the bearing pin 8 and the housing insert 10 has a lower spring force or another progressive spring characteristic than the valve spring 3.

Wie bereits erwähnt, wird die in einem modernen Ventiltrieb erforderliche Funktion des Ventilspielausgleichs von einem Spielausgleichselement 11 übernommen, auf dem sich der Gehäuseeinsatz 10 im Zylinderkopf 5 abstützt. Durch geringfügige Längsverschiebung des Gehäuseeinsatzes 10 gemäß Pfeilrichtung 9 wird dabei selbsttätig - wie bekannt - das jeweils erforderliche Ventilspiel eingehalten. Im Rahmen dieser geringfügigen Verschiebebewegungen des Gehäuseeinsatzes 10 können jedoch auch geringfügige Relativbewegungen zwischen dem Lagerbolzen 8 sowie dem Gehäuseeinsatz 10 auftreten. Befindet sich dabei der Sperrbolzen 13 im Seitenraum 16, so kann im Rahmen dieser geringfügigen Relativbewegungen der Lagerbolzen 8 geringfügig in die Querbohrung 14 hineingeschoben werden. Um trotz dieses geringfügigen Überstandes des Lagerbolzens 8 gegenüber der Querbohrung 14 weiterhin ein Blockieren des Lagerbolzens 8 zu ermöglichen, d. h. um trotz dieses Überstandes weiterhin den Sperrbolzen 13 gemäß Pfeilrichtung 15 nach links unterhalb des Lagerbolzens 8 verschieben zu können, ist die Stirnfläche 19 des Lagerbolzens 8 derart gegenüber der Bewegungsrichtung 15 des Sperrbolzens 13 geneigt, daß die lichte Weite w zwischen der Stirnfläche 19 sowie der gegenüberliegenden Gehäuseeinsatz-Wand 20 von der linken, dem Seitenraum 16 abgewandten Kante des Lagerbolzens 8 bzw. der Querbohrung 14 zur rechten, dem Seitenraum zugewandten Längskante des Lagerbolzens 8 bzw. zum Seitenraum 16 hin zunimmt. Da ferner, wie gezeigt, die Stirnkanten 21 des Lagerbolzens 13 ebenfalls abgeschrägt sind, kann auch dann, wenn der Lagerbolzen 8 mit seiner Stirnfläche 19 aufgrund geringfügiger Verschiebungen des Gehäuseeinsatzes 10 im Zylinderkopf 5 geringfügig in die Querbohrung 14 hineinragt, der Sperrbolzen 13 stets sicher und zuverlässig aus der gezeigten Position heraus nach links unter den Lagerbolzen 8 geschoben werden, um diesen zu blockieren. Selbstverständlich werden durch diese Gestaltung auch Bauteiltoleranzen sowie Fertigungstoleranzen vollständig ausgeglichen.As already mentioned, the function of valve clearance compensation required in a modern valve train is taken over by a play compensation element 11, on which the housing insert 10 is supported in the cylinder head 5. By slight longitudinal displacement of the housing insert 10 according to the direction of arrow 9, the required valve clearance is automatically maintained, as is known. Within the scope of these slight displacement movements of the housing insert 10, however, slight relative movements can also occur between the bearing pin 8 and the housing insert 10. If the locking pin 13 is located in the side space 16, the bearing pin 8 can be pushed slightly into the transverse bore 14 as part of these slight relative movements. In order to enable blocking of the bearing pin 8 in spite of this slight protrusion of the bearing pin 8 relative to the transverse bore 14, ie in order to be able to continue to move the locking pin 13 according to the direction of arrow 15 to the left below the bearing pin 8 despite this protrusion, the end face 19 of the bearing pin 8 inclined relative to the direction of movement 15 of the locking pin 13 such that the clear width w between the end face 19 and the opposite housing insert wall 20 from the left edge of the bearing pin 8 or the transverse bore 14 facing away from the side space 16 to the right longitudinal edge facing the side space of the bearing pin 8 or to the side space 16 increases. Since, furthermore, as shown, the end edges 21 of the bearing pin 13 are also beveled, even if the bearing pin 8 with its end face 19 protrudes slightly into the transverse bore 14 due to slight displacements of the housing insert 10 in the cylinder head 5, the locking pin 13 is always safe and can be reliably pushed out of the position shown to the left under the bearing pin 8 to block it. Of course, this design also completely compensates for component tolerances and manufacturing tolerances.

Indem der Sperrbolzen 13 quer zum Lagerbolzen 8 über dessen gesamte Stirnfläche 19 verschiebbar ist, indem also somit bei blockiertem Lagerbolzen 8 sich dieser mit seiner im wesentlichen gesamten Stirnfläche 19 auf dem Sperrbolzen 13 abstützt, ist die mechanische Beanspruchung der betreffenden Bauteile soweit als möglich minimiert bzw. zumindest optimiert.Since the locking pin 13 is displaceable transversely to the bearing pin 8 over its entire end face 19, that is to say when the bearing pin 8 is blocked, the latter is supported with its substantially entire end face 19 on the locking pin 13, the mechanical stress on the components concerned is minimized or minimized as far as possible at least optimized.

Betätigt bzw. bewegt wird der Sperrbolzen 13 auf hydraulischem Wege, in seine Ruhelage - in dieser Ruhelage liegt der becherförmige Sperrbolzen vollständig innerhalb des Seitenraumes 16 an einem Ruheanschlag an, der durch einen Stift 22 gebildet wird - zurückbewegt wird dieser Sperrbolzen 13 durch eine Zugfeder 23. Diese Zugfeder 23 ist im wesentlichen innerhalb des becherförmigen Sperrbolzens 13 angeordnet und einerseits an dessen Boden sowie andererseits am Stift 22 eingehängt. Soll somit der Sperrbolzen 13 aus der gezeigten Position heraus gemäß Pfeilrichtung 15 nach links verschoben werden, so wird der Becher-Innenraum mit geeignetem hydraulischen Druck beaufschlagt. Aufgrund der beschriebenen Abschrägung der Stirnfläche 19 sowie der Stirnkanten 21 kann dann der Sperrbolzen 13 vollständig unter den Lagerbolzen 8 gleiten und somit eine Verschiebung desselben gemäß Pfeilrichtung 9 verhindern. Wie bereits eingangs geschildert, wird dann bei einer Verdrehung des Nockens 7 das Hubventil 1 entsprechend dem Nockenhub betätigt. Wird hingegen der auf den Sperrbolzen 13 einwirkende Hydraulikdruck zurückgenommen, so gleitet dieser Sperrbolzen 13 aufgrund der Kraftwirkung der Zugfeder 23 wieder in seine Ruhelage und gelangt vollständig in den Seitenraum 16, der, wie bereits geschildert, durch den Stift 22 begrenzt wird. Wie ebenfalls bereits geschildert, wird dann bei einer Rotation des Nockens 7 der Nockenhub vollständig oder zumindest im wesentlichen vom Lagerbolzen 8 gemäß Pfeilrichtung 9 ausgeführt, das Hubventil 1 bleibt dabei vollständig oder zumindest im wesentlichen geschlossen. Ein geringfügiger Hub des Hubventiles 1 kann jedoch auch dann erwünscht sein und sich dadurch ergeben, daß der mögliche Verschiebeweg des Lagerbolzens 8 für eine vollständige Umsetzung des Hubes des Nockens 7 nicht ausreicht. Befindet sich dann wiederum der Sperrbolzen 13 in der gezeigten Position, so wird ein Großteil des Nockenhubes - wie geschildert - vom Lagerbolzen 8 ausgeübt, jedoch wird dieser über die Progression der Feder 18 so weit abgebremst und kann dabei sogar angehalten werden, so daß ein danach noch verbleibender Resthub des Nockens 7 dann auf das Hubventil 1 übertragen wird. Selbstverständlich kann der Lagerbolzen 8 bei Verschiebung durch den Nocken auch mit seiner Stirnfläche 19 nach einem gewissen anteiligen Nockenhub auf der gegenüberliegenden Gehäuseeinsatz-Wand 20 zum Anliegen kommen, jedoch ist dem Abbremsen durch die Federprogression der Vorzug zu geben, da ein Anliegen einen Ruck und Geräusch erzeugen würde. Durch geeignete Auswahl der Dimensionen läßt sich somit für das Hubventil 1 ein vollständiger oder auch nur ein teilweiser - bevorzugt äußerst geringer - Ventilhub erzielen. Durch entsprechende Abstimmung zwischen der Federkraft der Druckfeder 18 sowie der Federkraft der Ventilfeder 3 kann dieser Bewegungsablauf auch umgedreht werden, d. h. zuerst wird das Hubventil 1 geringfügig geöffnet und erst anschließend daran wird der Lagerbolzen 8 gemäß Pfeilrichtung 9 verschoben - jedoch stets nur dann, wenn sich der Sperrbolzen 13 außerhalb der Bewegungsrichtung des Lagerbolzens 8 im Seitenraum 16 befindet .The locking bolt 13 is actuated or moved hydraulically, into its rest position - in this rest position the cup-shaped locking bolt lies completely within the side space 16 against a rest stop, which is formed by a pin 22 - this locking bolt 13 is moved back by a tension spring 23 This tension spring 23 is arranged essentially within the cup-shaped locking bolt 13 and is hung on the bottom of the pin on the one hand and on the pin 22 on the other hand. If the locking pin 13 is thus to be shifted from the position shown to the left in the direction of arrow 15, the interior of the cup is subjected to a suitable hydraulic pressure. Because of the described beveling of the end face 19 and the end edges 21, the locking pin 13 can then slide completely under the bearing pin 8 and thus prevent a displacement of the same according to arrow direction 9. As already described at the beginning, the lift valve 1 is then actuated in accordance with the cam lift when the cam 7 is rotated. If, on the other hand, the hydraulic pressure acting on the locking pin 13 is withdrawn, this locking pin 13 slides back into its rest position due to the force of the tension spring 23 and completely reaches the side space 16 which, as already described, is delimited by the pin 22. As also already described, when the cam 7 rotates, the cam lift is carried out completely or at least essentially by the bearing pin 8 according to the direction of arrow 9, the lift valve 1 remains completely or at least essentially closed. A slight stroke of the lift valve 1 can, however, also be desirable and result from the fact that the possible displacement path of the bearing pin 8 is not sufficient for a complete implementation of the stroke of the cam 7. Is then again the locking pin 13 in the position shown, so a large part of the cam stroke - as described - exerted by the bearing pin 8, but this is braked so far over the progression of the spring 18 and can even be stopped so that one afterwards remaining stroke of the cam 7 is then transferred to the lift valve 1. Of course, the bearing pin 8 can also come to rest with its end face 19 after a certain proportion of cam stroke on the opposite housing insert wall 20 when displaced by the cam, but braking due to the spring progression is to be given preference, since a concern is a jerk and noise would generate. Through a suitable selection of the dimensions, a complete or only a partial — preferably extremely small — valve lift can thus be achieved for the lift valve 1. By appropriate coordination between the spring force of the compression spring 18 and the spring force of the valve spring 3 can this sequence of movements can also be reversed, ie first the lift valve 1 is opened slightly and only then is the bearing pin 8 shifted in the direction of the arrow 9 - but always only when the locking pin 13 is located outside the direction of movement of the bearing pin 8 in the side space 16.

Um eine Drehbewegung des Lagerbolzens 8 um seine Längsachse zu verhindern und um somit sicherzustellen, daß die Stirnfläche 19 unter allen Umständen in der beschriebenen Neigungsposition verbleibt, ist im Gehäuseeinsatz 10 ein Querstift 24 gelagert, der den Lagerbolzen 8 in einer Längsnut 25 zumindest teilweise durchdringt. Die Längsnut 25 ist dabei erforderlich, um eine Verschiebebewegung des Lagerbolzens 8 gemäß Pfeilrichtung 9 zu ermöglichen. In einer vorteilhaften Funktionsvereinigung stellt der Querstift 24 gleichzeitig einen Endanschlag für den Lagerbolzen 8 innerhalb des Gehäuseeinsatzes 10 dar, so daß der Gehäuseeinsatz 10 inklusive Lagerbolzen 8 und Sperrbolzen 13 als Vormontageeinheit komplettiert in den Zylinderkopf 5 eingebaut werden kann und sich dabei selbsttätig ein spielfreier Ventiltrieb einstellt. Dabei wird diese Vormontageeinheit, die selbstverständlich auch die Druckfeder 18 sowie die Zugfeder 23 an die weiteren im Zusammenhang mit dem Gehäuseeinsatz 10 beschriebenen Elemente enthält, durch den exzentrischen Absatz 26 im Sackloch 12 und somit auch im Zylinderkopf 5 zentriert. Zur Bearbeitungsvereinfachung ist der oberhalb des Absatzes 26 liegende, im wesentlichen dem Sperrbolzen 13 in der Querbohrung 14 aufnehmende Bereich des Gehäuseeinsatzes 10 kreiszylindrisch ausgebildet. Ferner weist der Gehäuseeinsatz 10 einen bei nicht aktivem Spielausgleichselement 11 wirksam werdenden Anschlag 27 auf, auf dem sich gleichzeitig die Druckfeder 18 abstützt. Der Abstand zwischen dem Anschlag 27 sowie dem darunterliegenden Absatz im Zyinderkopf 5 stellt den Arbeitsbereich des Spielausgleichselementes 11 dar.In order to prevent rotation of the bearing pin 8 about its longitudinal axis and thus to ensure that the end face 19 remains in the described inclination position under all circumstances, a transverse pin 24 is mounted in the housing insert 10, which at least partially penetrates the bearing pin 8 in a longitudinal groove 25. The longitudinal groove 25 is required to enable the bearing pin 8 to move in the direction of the arrow 9. In an advantageous combination of functions, the transverse pin 24 also represents an end stop for the bearing pin 8 within the housing insert 10, so that the housing insert 10 including the bearing pin 8 and locking pin 13 can be installed as a pre-assembly unit in the cylinder head 5 and thereby automatically adjusts a valve drive without play . This preassembly unit, which of course also contains the compression spring 18 and the tension spring 23 on the other elements described in connection with the housing insert 10, is centered by the eccentric shoulder 26 in the blind hole 12 and thus also in the cylinder head 5. To simplify processing, the area of the housing insert 10 lying above the shoulder 26 and essentially receiving the locking pin 13 in the transverse bore 14 is of circular cylindrical design. Furthermore, the housing insert 10 has a stop 27, which becomes effective when the play compensation element 11 is not active, on which the compression spring 18 is supported at the same time. The distance between the stop 27 and the paragraph below it in the cylinder head 5 represents the working area of the play compensation element 11.

Nicht näher dargestellt ist ein Hydraulikkanal, der das für eine Bewegung des Sperrbolzens 13 erforderliche Hydraulikmedium in den Innenraum dieses becherförmigen Sperrbolzens 13 fördert. Dabei kann dieser Hydraulikdruck gezielt mittels eines geeigneten Steuerventiles angelegt werden, es ist aber eine quasi selbsttätige Regelung in Abhängigkeit von der Drehzahl der Brennkraftmaschine und dem damit nahezu proportional ansteigenden Schmieröldruck möglich, wenn als den Sperrbolzen 13 betätigendes Hydraulikmedium das Schmieröl der Brennkraftmaschine verwendet wird. Da die beschriebene Vorrichtung bevorzugt an Brennkraftmaschinen zum Einsatz kommen soll, die mehrere Einlaß-Hubventile je Zylinder aufweisen, wobei zumindest eines dieser Einlaß-Hubventile außer Betrieb gesetzt werden können soll, entspricht der oben beschriebene selbsttätige Ansteuerungsmechanismus über den Öldruck der Brennkraftmaschine exakt den dann vorliegenden Steuerungsanforderungen. Bei niedrigen Brennkraftmaschinen-Drehzahlen soll nämlich lediglich eines der bevorzugt beiden Einlaßventile geöffnet werden, somit wird bei niedrigem Öldruck das zweite Einlaß-Hubventil, das mit einer erfindungsgemäßen Vorrichtung versehen ist, nicht geöffnet. Bei höheren Brennkraftmaschinen-Drehzahl hingegen sollen beide Einlaßventile geöffnet werden, dann liegt aber auch ein höherer Öldruck an, der - wie beschrieben - den Sperrbolzen 13 gegen die Kraft der Zugfeder 23 aus dem Seitenraum 16 herausbewegt und somit den Lagerbolzen 8 blockiert. Dann aber wird auch dieses Einlaß-Hubventil, das mit einer erfindungsgemäßen Vorrichtung versehen ist, bei Rotation des Nockens 7 durch den Nockenhub geöffnet. Selbstverständlich kann der Schaltvorgang, d. h. das Verschieben des Sperrbolzens 13 unter den Lagerbolzen 8 nur lastfrei, d. h. in der entsprechenden Grundkreisphase des Nockens 7 erfolgen. Darauf hingewiesen werden soll ferner, daß eine Vielzahl von Details insbesondere konstruktiver Art durchaus abweichend vom gezeigten Ausführungsbeispiel gestaltet sein kann, ohne den Inhalt der Patentansprüche zu verlassen.A hydraulic channel, which conveys the hydraulic medium required for a movement of the locking pin 13 into the interior of this cup-shaped locking pin 13, is not shown. This hydraulic pressure can be applied in a targeted manner by means of a suitable control valve, but quasi-automatic regulation is possible depending on the speed of the internal combustion engine and the lubricating oil pressure that increases almost proportionally, if the lubricating oil of the internal combustion engine is used as the hydraulic fluid actuating the locking pin 13. Since the device described should preferably be used on internal combustion engines which have a plurality of intake lift valves per cylinder, with at least one of these intake lift valves being able to be put out of operation, the automatic control mechanism described above via the oil pressure of the internal combustion engine corresponds exactly to the one then present Control requirements. At low internal combustion engine speeds, namely, only one of the preferably two inlet valves is to be opened, so the second inlet lift valve, which is provided with a device according to the invention, is not opened at low oil pressure. At higher engine speed, however, both intake valves should be opened, but then there is also a higher oil pressure, which - as described - moves the locking pin 13 against the force of the tension spring 23 out of the side space 16 and thus blocks the bearing pin 8. But then this inlet lift valve, which is provided with a device according to the invention, is opened by the cam lift when the cam 7 rotates. Of course, the switching process, ie moving the locking pin 13 under the bearing pin 8 can only be load-free, ie in the corresponding base circle phase of the Cam 7 take place. It should also be pointed out that a large number of details, in particular of a constructive nature, can be designed quite differently from the exemplary embodiment shown, without departing from the content of the claims.

Claims (2)

  1. A device for deactivating a gate valve (1) of an internal combustion engine operated by a cam (7) via a rocking lever (6), the device comprising a bearing pin (8) constituting an abutment for the rocking lever (6) and disposed so as to be longitudinally movable relative to a spring element (18), and also comprising a locking pin (13) for locking the bearing pin (8),
    characterised in that the bearing pin (8) and the locking pin (13) are disposed in a casing insert (10) which abuts a clearance-compensating element (11) in the cylinder head (5) of the internal combustion engine.
  2. A device according to claim 1, characterised by at least one of the following features:
    - the locking pin (13) is movable substantially transversely relative to the bearing pin (8) and over its entire end face (19),
    - the end face (19) of the bearing pin (8) is so inclined relative to the direction (15) of motion of the locking pin (13), which is situated in a side chamber (16) when the bearing pin is not locked, that the internal width (w) between the end face (19) and the opposite wall (20) of the casing insert increases from the longitudinal edge of the bearing pin remote from the side chamber (16) to the longitudinal edge facing the side chamber (16),
    - a transverse pin (24) disposed in the casing insert (10) and extending in a longitudinal groove (25) through the bearing pin (8) prevents the bearing pin (8) from rotating around its longitudinal axis and
    - the locking pin (13), which is cup-shaped, is held in the side chamber (16) by a tension spring (23) suspended in a pin (22) constituting a stop for the locking pin when at rest, and is movable relative to the tension spring (23) by hydraulic means during a locking operation.
EP94106892A 1993-07-14 1994-05-03 Deactivating device for internal combustion engine valve Expired - Lifetime EP0634564B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4323555 1993-07-14
DE4323555A DE4323555A1 (en) 1993-07-14 1993-07-14 Device for decommissioning an internal combustion engine lift valve

Publications (2)

Publication Number Publication Date
EP0634564A1 EP0634564A1 (en) 1995-01-18
EP0634564B1 true EP0634564B1 (en) 1996-10-30

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DE (2) DE4323555A1 (en)

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DE19838926A1 (en) * 1998-08-27 2000-03-02 Schaeffler Waelzlager Ohg Switchable valve train of an internal combustion engine
DE19838909A1 (en) * 1998-08-27 2000-03-02 Schaeffler Waelzlager Ohg Switchable valve train of an internal combustion engine
DE19952909B4 (en) * 1999-11-03 2010-06-24 Schaeffler Kg Switchable support element
EP1143120A3 (en) * 2000-03-08 2001-10-24 Eaton Corporation Valve deactivator assembly for internal combustion engine
DE10048619A1 (en) * 2000-09-30 2002-04-11 Ina Schaeffler Kg Supporting element that can be decoupled for internal combustion engine valve drive drag lever, has annular fitting on inner end of housing built into bore in outer housing in cylinder head
DE10111512A1 (en) * 2001-03-09 2002-09-12 Ina Schaeffler Kg Switchable tappet for direct transmission of a cam stroke to a tappet rod
US6615783B2 (en) 2001-03-08 2003-09-09 Ina Schaeffler Kg Switchable tappet for the direct transmission of a cam lift to a tappet push rod
DE10122373B4 (en) * 2001-05-09 2014-09-18 Schaeffler Technologies Gmbh & Co. Kg Switchable support element
DE102005020586A1 (en) * 2005-05-03 2006-11-09 Bayerische Motoren Werke Ag Valve drive for internal combustion engine has stopper which is provided for supporting element with that unfixed supporting element is fixed in second position
DE102007033757A1 (en) 2007-07-18 2009-01-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Control element for hydraulic valve-play compensation element in valve timing drive of internal combustion engine, has multiple radial penetrating holes are arranged in housing of valve-play compensation element
FR2925574A3 (en) * 2007-12-21 2009-06-26 Renault Sas Valve e.g. intake valve, control device for oil engine of vehicle, has movable stop including support element that is provided in contact with end, where position of movable element defines displacement amplitude of valve
US8375909B2 (en) * 2009-01-30 2013-02-19 Eaton Corporation Rocker arm retention
WO2011015603A2 (en) * 2009-08-04 2011-02-10 Eaton Srl Lost motion valve control apparatus
FR2969708B1 (en) * 2010-12-22 2012-12-28 Valeo Sys Controle Moteur Sas IMPROVEMENT OF VALVE ACTUATION DEVICES WITH POSSIBILITY OF DEACTIVATION AND MEANS FOR LOCKING SUCH A DEVICE.
DE102011005575A1 (en) * 2011-03-15 2012-09-20 Schaeffler Technologies Gmbh & Co. Kg Valve gear with additional lift in the cam base circle
DE102017126702A1 (en) 2017-11-14 2019-05-16 Schaeffler Technologies AG & Co. KG Switchable valve train element of a valve train of an internal combustion engine
CN112282886B (en) * 2020-10-27 2022-04-08 一汽解放汽车有限公司 Engine cylinder deactivation hydraulic system and vehicle

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DE4211631A1 (en) * 1992-04-07 1993-04-08 Bayerische Motoren Werke Ag Valve drive with play compensation - has movement path limitation of slide, resulting in valve lift

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Publication number Publication date
DE59400932D1 (en) 1996-12-05
EP0634564A1 (en) 1995-01-18
DE4323555A1 (en) 1995-01-19

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