EP0497194A1 - Method for actuating an exhaust valve tappet during braking of an internal combustion engine - Google Patents

Method for actuating an exhaust valve tappet during braking of an internal combustion engine Download PDF

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Publication number
EP0497194A1
EP0497194A1 EP92100960A EP92100960A EP0497194A1 EP 0497194 A1 EP0497194 A1 EP 0497194A1 EP 92100960 A EP92100960 A EP 92100960A EP 92100960 A EP92100960 A EP 92100960A EP 0497194 A1 EP0497194 A1 EP 0497194A1
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EP
European Patent Office
Prior art keywords
pressure
inner part
tappet
exhaust valve
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP92100960A
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German (de)
French (fr)
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EP0497194B1 (en
Inventor
Heribert Dipl.-Ing. Kubis
Dieter Wittmann
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MAN Truck and Bus SE
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MAN Nutzfahrzeuge AG
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Publication of EP0497194A1 publication Critical patent/EP0497194A1/en
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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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/245—Hydraulic tappets

Definitions

  • the invention relates to an outlet valve lifter according to the generic term.
  • a hydraulically actuated valve tappet is activated between the exhaust cam and the exhaust valve and can be acted upon by an external pressure source.
  • a pressure chamber is provided between the tappet outer part and an inner part movable therein, which is connected via a bore to the pressure source, which can be designed as a hydraulic pump unit.
  • the hydraulic pump unit is actuated and the pressure chamber is pressurized with hydraulic pressure, so that the inner part lifts the exhaust valve against the force of the valve spring via the push rod, the valve tappet in this phase the base circle of the exhaust cam.
  • the cam lift is used exclusively, as is usually the case, to raise the exhaust valve during the exhaust cycle.
  • the exhaust valve opens in the course of the compression stroke.
  • the pressure on the exhaust valve increases due to the increasing pressure in the compression cycle. Via the push rod this force is transmitted retrospectively to the inner part of the exhaust valve tappet and there leads to an increase in pressure which considerably exceeds the pressure which is required for opening the exhaust valve against the force of the valve spring. This pressure propagates through all pressurized parts to the external pressure source and leads to damage due to cavitation, erosion and leaks.
  • the invention is based on the object of avoiding excessive oil pressures outside the tappet in order to ensure that all parts subject to oil pressure are only exposed to the relatively low oil pressure which is only necessary to generate the additional elevation of the exhaust valve, So that the risk of damage is largely excluded and high operational safety is guaranteed over long terms.
  • Figure 1 shows an exhaust valve lifter 1 which is arranged between a camshaft 2 and a push rod 3.
  • the push rod 3 actuates an outlet valve 4, which is opened against the restoring force of a valve spring 5.
  • the exhaust valve 4 opened by a cam 6, which lifts the exhaust valve tappet 1 and this transfers its movement after exhausting a game 9 via the push rod 3 to the exhaust valve 4.
  • the exhaust valve 4 is additionally to be raised slightly during the compression stroke in order to blow off the compressed air, so that additional braking work is carried out.
  • the outlet valve tappet 1 has an inner part 8 which is axially movable in a tappet outer part 7 and which is installed with a stroke 9.
  • pressure fluid is supplied from an external pressure source 11, which raises the inner part 8 together with the push rod 3 until the inner part 8 has performed an intended stroke 9 and between the inner part 8 and a stop 8a a game 9a remains ( Figure 2).
  • the outlet valve 4 thereby opens and the pre-compressed air is blown off. Since the exhaust valve is raised only slightly in this phase, a considerable pressure builds up in the cylinder until the end of the compression stroke, which loads the exhaust valve 4 in the direction of the closed position.
  • the exhaust valve 4 passes this force on the push rod 3 to the inner part 8 of the exhaust valve tappet 1. This force creates a high hydraulic pressure in all pressure-carrying components, which can lead to damage.
  • this excess pressure is limited to the outlet valve tappet and cannot propagate further into the pressure-carrying organs.
  • the inner part 8 is subjected to a special training in order to prevent the reaction to high hydraulic pressure on the pressure-carrying parts.
  • the inner part 8 has an axially movable piston 12, which is held in the starting position by a compression spring 13 and keeps the valve seat 25 open.
  • the piston 12 has a stroke limiter 14 on the one hand and a mandrel 15 on the other hand.
  • the inner part has a ball socket 16 at its upper end, while the lower end is closed by a valve 17.
  • the push rod 3 shown in FIG. 1 is mounted in the ball socket 16.
  • a first pressure chamber 19 under the piston 12 can be connected to the external pressure source 11 (FIG. 1) via through bores 18.
  • the first pressure chamber 19 in turn communicates in the illustrated rest position of the piston 12 via first and second bores 20, 21 in the valve 17 with a second pressure chamber 22 below the inner part 8.
  • valve 17 there is a spring 23 with a ball 24 which is held in the starting position by means of the compression spring 13 via the mandrel 15.
  • the inner part 8 is limited with stroke 9 plus a game 9a by stop ring 8a in a tappet outer part 7 of the outlet valve tappet 1.
  • the first pressure chamber 19 can be connected via the bores 18 to the pressure source 11 shown in FIG.
  • the compression spring 13 is first compressed by the piston 12 until the stroke limitation 14 on the inner part 8 comes to a stop.
  • the ball 24 is pressed into a seat 25 by means of the spring 23 and initially closes the first bore 20.
  • the force of the spring 23 is now designed so that the ball 24 can still open due to the pressure building up in the first pressure chamber 19 and opens the path of the pressure fluid via the first bore 20 and the second bore 21 to the second pressure chamber 22. Due to the force exerted by the second pressure chamber 22 on the inner part 8, the latter is lifted together with the push rod 3 (FIG. 1) mounted in the spherical cap 16 and moved until the stroke 9 (FIG. 2) is exhausted.
  • the stroke 9 results as a function of the amount of oil delivered by the pressure source 11. This represents a constant since the pressure source 11 (FIG. 1) is designed as a positive displacement pump.
  • the outlet valve 4 (FIG. 1) is opened in accordance with the distance of the stroke 9. Under normal operating conditions, a play 9a remains between the inner part 8 and the stop ring 8a.
  • first and second regulating bores 26, 27 are provided in the inner part 8, which are connected to one another via an overflow channel 28.
  • the hydraulic pressure supplied by the bore 18 can act on its side facing the first pressure chamber 19 and move it against the restoring force of the compression spring 13.
  • the lower edge 29 of the piston 12 reaches the first regulating bore 26, as shown in FIG. 5, hydraulic fluid can flow into the space filled by the compression spring 13 via the overflow channel 28 and the second regulating bore 27.
  • This room is over a relief bore 30 is connected to the environment for pressure equalization, whereby a further movement of the piston 12 is stopped.
  • the functions of the other parts are the same as those in FIGS. 2 and 3 and have been explained in detail there.
  • the advantage of this tappet design is that the pressure relief valve (see claim 3) can be dispensed with.

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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)

Abstract

The invention relates to an outlet valve tappet for an internal combustion engine. To increase the braking power of engines, it is necessary to open the outlet valve 4 also in the compression cycle. Use is advantageously made of a hydraulically operating outlet valve tappet 1 which operates with hydraulic pressure from an external pressure source 11. Due to the pressure of the compressed air shortly before ignition upper dead centre, great forces act on the outlet valve 4 and, from the latter, on the outlet valve tappet 1. These forces retroact via the inner part 8 as hydraulic pressure on the pressure source 11 and may damage the latter (Figure 1). According to Figure 2, the outlet valve tappet 1 has an inner part 8, which is raised by the lift 9 by impinging with pressure via the second pressure space 22, as a result of which the outlet valve 4 opens. If the pressure then rises in the second pressure space 22 as a function of the force of the outlet valve 4 via the pressure of the pressure source 11, according to the invention the ball 24 (Figure 3) closes, as a result of which the second pressure space 22 is hermetically sealed and the hydraulic pressure building up therein cannot propagate to the pressure source 11.

Description

Die Erfindung bezieht sich auf einen Auslaß-Ventilstößel gemäß dem Gattungsbegriff.The invention relates to an outlet valve lifter according to the generic term.

Zur Erhöhung der Bremsleistung von Brennkraftmaschinen in Nutzfahrzeugen ist es bekannt, das Auslaßventil auch während des Verdichtungstaktes kurz vor dem Erreichen von Zünd-OT zu öffnen, um die verdichtete Luft abzublasen und so deren Rückexpansion zu verhindern. Um das Auslaßventil vor Zünd-OT zu öffnen wird zwischen Auslaßnocken und Auslaßventil ein hydraulisch betätigbarer Ventilstößel eingeschaltet, welcher von einer externen Druckquelle beaufschlagbar ist. Zwischen Stößel-Außenteil und einem darin beweglichen Innenteil ist ein Druckraum vorgesehen, der über eine Bohrung mit der Druckquelle verbunden ist, die als Hydraulikpumpeneinheit ausgeführt sein kann. Soll nun das Auslaßventil vor Zünd-OT angehoben werden, wird die Hydraulikpumpeneinheit betätigt und der Druckraum mit Hydraulikdruck beaufschlagt, so daß das Innenteil über die Stößelstange gegen die Kraft der Ventilfeder das Auslaßventil anhebt, wobei der Ventilstößel in dieser Phase auf dem Grundkreis des Auslaßnockens aufsitzt. Die Nockenerhebung dient ausschließlich, wie sonst üblich, der Anhebung des Auslaßventils während des Auslaßtaktes. Im Bremsbetrieb öffnet das Auslaßventil im Verlauf des Verdichtungstaktes. Durch den im Verdichtungstakt ansteigenden Druck steigt die Kraft auf das Auslaßventil. Über die Stößelstange überträgt sich diese Kraft rückwirkend auf das Innenteil des Auslaß-Ventilstößels und führt dort zu einem Druckanstieg, der erheblich den Druck übersteigt, der für die Öffnung des Auslaßventils entgegen der Kraft der Ventilfeder erforderlich ist. Dieser Druck pflanzt sich über alle druckführenden Teile bis zur externen Druckquelle fort und führt zu Schäden durch Kavitation, Erosion und Undichtheiten.To increase the braking power of internal combustion engines in commercial vehicles, it is known to open the exhaust valve even during the compression stroke shortly before ignition TDC is reached in order to blow off the compressed air and thus prevent its back expansion. In order to open the exhaust valve before ignition TDC, a hydraulically actuated valve tappet is activated between the exhaust cam and the exhaust valve and can be acted upon by an external pressure source. A pressure chamber is provided between the tappet outer part and an inner part movable therein, which is connected via a bore to the pressure source, which can be designed as a hydraulic pump unit. If the exhaust valve is now to be raised before ignition TDC, the hydraulic pump unit is actuated and the pressure chamber is pressurized with hydraulic pressure, so that the inner part lifts the exhaust valve against the force of the valve spring via the push rod, the valve tappet in this phase the base circle of the exhaust cam. The cam lift is used exclusively, as is usually the case, to raise the exhaust valve during the exhaust cycle. In braking mode, the exhaust valve opens in the course of the compression stroke. The pressure on the exhaust valve increases due to the increasing pressure in the compression cycle. Via the push rod this force is transmitted retrospectively to the inner part of the exhaust valve tappet and there leads to an increase in pressure which considerably exceeds the pressure which is required for opening the exhaust valve against the force of the valve spring. This pressure propagates through all pressurized parts to the external pressure source and leads to damage due to cavitation, erosion and leaks.

Ausgehend von dem Auslaß-Ventilstößel entsprechend dem Gattungsbegriff liegt der Erfindung die Aufgabe zugrunde, überhöhte Öldrücke außerhalb des Stößels zu vermeiden, um so zu erreichen, daß alle öldruckbeaufschlagten Teile nur dem relativ niedrigen, lediglich zur Erzeugung der Zusatzerhebung des Auslaßventiles notwendigen Öldruck ausgesetzt werden, so daß die Gefahr von Schäden weitgehend ausgeschlossen und hohe Betriebssicherheit über lange Laufzeiten gewährleistet ist.Starting from the exhaust valve tappet according to the generic term, the invention is based on the object of avoiding excessive oil pressures outside the tappet in order to ensure that all parts subject to oil pressure are only exposed to the relatively low oil pressure which is only necessary to generate the additional elevation of the exhaust valve, So that the risk of damage is largely excluded and high operational safety is guaranteed over long terms.

Erfindungsgemäß wird diese Aufgabe durch die kennzeichnenden Merkmale des patentanspruches 1 gelöst.According to the invention, this object is achieved by the characterizing features of patent claim 1.

Dadurch, daß der Druckraum unterhalb des Innenteiles durch die Kugel gegenüber den druckführenden Organen absperrbar ist, kann sich in ihm ein Druckniveau ausbilden, welches ein Mehrfaches dessen beträgt, was zur Öffnung des Auslaßventiles notwendig ist, ohne daß die externen druckführenden Organe davon berührt werden. Somit wird von ihnen mit Sicherheit Schaden abgewandt.Because the pressure chamber below the inner part can be shut off by the ball from the pressure-carrying elements, a pressure level can be formed in it which is a multiple of what is necessary to open the exhaust valve without the external pressure-carrying elements Organs are affected. Thus, damage is certainly averted from them.

Vorteilhafte Weiterbildungen der Erfindung können den Ansprüchen 2 bis 5 entnommen werden.Advantageous developments of the invention can be found in claims 2 to 5.

Ausführungsbeispiele der Erfindung sind in Zeichnungen dargestellt. Es zeigt:

Figur 1
einen Auslaß-Ventilstößel zwischen Nockenwelle und Auslaßventil
Figur 2
einen Auslaß-Ventilstößel mit mechanisch wirkendem Anschlag in Ruhestellung
Figur 3
einen Auslaß-Ventilstößel mit mechanisch wirkendem Anschlag gemäß Figur 2, jedoch in Arbeitsstellung
Figur 4
einen Auslaß-Ventilstößel mit hydraulisch wirkender Hubbegrenzung in Ruhestellung
Figur 5
einen Auslaß-Ventilstößel mit hydraulisch wirkender Hubbegrenzung nach Figur 4, jedoch in Arbeitsstellung
Embodiments of the invention are shown in drawings. It shows:
Figure 1
an exhaust valve lifter between the camshaft and exhaust valve
Figure 2
an outlet valve lifter with a mechanically acting stop in the rest position
Figure 3
an outlet valve lifter with a mechanical stop according to Figure 2, but in the working position
Figure 4
an outlet valve lifter with hydraulically acting stroke limitation in the rest position
Figure 5
an outlet valve lifter with hydraulically acting stroke limitation according to Figure 4, but in the working position

Figur 1 zeigt einen Auslaß-Ventilstößel 1 welcher zwischen einer Nockenwelle 2 und einer Stößelstange 3 angeordnet ist. Die Stößelstange 3 betätigt ein Auslaßventil 4, welches gegen die Rückstellkraft einer Ventilfeder 5 geöffnet wird. Im normalen Motorbetrieb wird das Auslaßventil 4 durch einen Nocken 6 geöffnet, welcher den Auslaß-Ventilstößel 1 anhebt und dieser seine Bewegung nach Ausschöpfung eines Spieles 9 über die Stößelstange 3 auf das Auslaßventil 4 weiterleitet.Figure 1 shows an exhaust valve lifter 1 which is arranged between a camshaft 2 and a push rod 3. The push rod 3 actuates an outlet valve 4, which is opened against the restoring force of a valve spring 5. In normal engine operation, the exhaust valve 4 opened by a cam 6, which lifts the exhaust valve tappet 1 and this transfers its movement after exhausting a game 9 via the push rod 3 to the exhaust valve 4.

Im Motorbremsbetrieb soll das Auslaßventil 4 zusätzlich während des Verdichtungstaktes leicht angehoben werden, um die verdichtete Luft abzublasen, so daß zusätzliche Bremsarbeit verrichtet wird.In engine braking mode, the exhaust valve 4 is additionally to be raised slightly during the compression stroke in order to blow off the compressed air, so that additional braking work is carried out.

Zu diesem Zweck weist der Auslaß-Ventilstößel 1 ein in einem Stößel-Außenteil 7 axial bewegliches Innenteil 8 auf, welches mit Hub 9 eingebaut ist. Während des Verdichtungstaktes, also wenn der Auslaß-Ventilstößel 1 auf einem Grundkreis 10 der Nockenwelle 2 aufsitzt wird von einer externen Druckquelle 11 Druckflüssigkeit zugeführt, welche den Innenteil 8 samt Stößelstange 3 anhebt, bis der Innenteil 8 einen vorgesehenen Hub 9 ausgeführt hat und zwischen Innenteil 8 und einem Anschlag 8a ein Spiel 9a verbleibt (Figur 2). Das Auslaßventil 4 öffnet dadurch und die vorverdichtete Luft wird abgeblasen. Da das Auslaßventil in dieser Phase nur geringfügig angehoben wird baut sich bis zum Ende des Verdichtungshubes ein beachtlicher Druck im Zylinder auf, der das Auslaßventil 4 in Richtung Schließstellung belastet. Das Auslaßventil 4 leitet diese Kraft über die Stößelstange 3 auf das Innenteil 8 des Auslaß-Ventilstößels 1 weiter. Durch diese Kraft baut sich in allen druckführenden Bauteilen ein hoher hydraulischer Druck auf, welcher zu Schäden führen kann.For this purpose, the outlet valve tappet 1 has an inner part 8 which is axially movable in a tappet outer part 7 and which is installed with a stroke 9. During the compression stroke, that is, when the exhaust valve tappet 1 is seated on a base circle 10 of the camshaft 2, pressure fluid is supplied from an external pressure source 11, which raises the inner part 8 together with the push rod 3 until the inner part 8 has performed an intended stroke 9 and between the inner part 8 and a stop 8a a game 9a remains (Figure 2). The outlet valve 4 thereby opens and the pre-compressed air is blown off. Since the exhaust valve is raised only slightly in this phase, a considerable pressure builds up in the cylinder until the end of the compression stroke, which loads the exhaust valve 4 in the direction of the closed position. The exhaust valve 4 passes this force on the push rod 3 to the inner part 8 of the exhaust valve tappet 1. This force creates a high hydraulic pressure in all pressure-carrying components, which can lead to damage.

Erfindungsgemäß wird dieser Überdruck auf den Auslaßventilstößel begrenzt und kann sich nicht weiter in die druckführenden Organe fortpflanzen.According to the invention, this excess pressure is limited to the outlet valve tappet and cannot propagate further into the pressure-carrying organs.

Nach Figur 2 wird dabei das Innenteil 8 einer besonderen Ausbildung unterzogen, um die Rückwirkung zu hohen Hydraulikdruckes auf die druckführenden Teile zu unterbinden. Zu diesem Zweck weist der Innenteil 8 einen axial beweglichen Kolben 12 auf, welcher durch eine Druckfeder 13 in Ausgangslage gehalten wird und den Ventilsitz 25 geöffnet hält. Der Kolben 12 verfügt einerseits über eine Hubbegrenzung 14 und andererseits über einen Dorn 15. Das Innenteil weist an seinem oberen Ende eine Kugelpfanne 16 auf, während das untere Ende durch ein Ventil 17 abgeschlossen ist. In der Kugelpfanne 16 ist die aus Figur 1 zu ersehende Stößelstange 3 gelagert. Über durchgehende Bohrungen 18 kann ein erster Druckraum 19 unter dem Kolben 12 mit der externen Druckquelle 11 (Figur 1) verbunden werden.According to Figure 2, the inner part 8 is subjected to a special training in order to prevent the reaction to high hydraulic pressure on the pressure-carrying parts. For this purpose, the inner part 8 has an axially movable piston 12, which is held in the starting position by a compression spring 13 and keeps the valve seat 25 open. The piston 12 has a stroke limiter 14 on the one hand and a mandrel 15 on the other hand. The inner part has a ball socket 16 at its upper end, while the lower end is closed by a valve 17. The push rod 3 shown in FIG. 1 is mounted in the ball socket 16. A first pressure chamber 19 under the piston 12 can be connected to the external pressure source 11 (FIG. 1) via through bores 18.

Der erste Druckraum 19 wiederum kommuniziert in der dargestellten Ruhelage des Kolbens 12 über erste und zweite Bohrungen 20, 21 im Ventil 17 mit einem zweiten Druckraum 22 unterhalb des Innenteils 8.The first pressure chamber 19 in turn communicates in the illustrated rest position of the piston 12 via first and second bores 20, 21 in the valve 17 with a second pressure chamber 22 below the inner part 8.

Im Ventil 17 befindet sich eine Feder 23 mit Kugel 24, welche über den Dorn 15 mittels der Druckfeder 13 in Ausgangslage gehalten wird.In the valve 17 there is a spring 23 with a ball 24 which is held in the starting position by means of the compression spring 13 via the mandrel 15.

Das Innenteil 8 ist mit Hub 9 plus einem Spiel 9a begrenzbar durch Anschlagring 8a in einem Stößel-Außenteil 7 des Auslaß-Ventilstößels 1 geführt.The inner part 8 is limited with stroke 9 plus a game 9a by stop ring 8a in a tappet outer part 7 of the outlet valve tappet 1.

Was die Funktion betrifft, wird auf Figur 3 verwiesen. Bei Betätigung der Motorbremse kann der erste Druckraum 19 über die Bohrungen 18 mit der in Figur 1 dargestellten Druck-quelle 11 verbunden werden. Beim Druckbeaufschlagen des Druckraumes 19 wird zunächst die Druckfeder 13 durch den Kolben 12 gestaucht, bis die Hubbegrenzung 14 am Innenteil 8 zum Anschlag kommt. Gleichzeitig wird die Kugel 24 nach Freigabe durch den Dorn 15 mittels der Feder 23 in einen Sitz 25 gedrückt und verschließt zunächst die erste Bohrung 20.With regard to the function, reference is made to FIG. 3. When the engine brake is actuated, the first pressure chamber 19 can be connected via the bores 18 to the pressure source 11 shown in FIG. When pressurizing the Pressure chamber 19, the compression spring 13 is first compressed by the piston 12 until the stroke limitation 14 on the inner part 8 comes to a stop. At the same time, after being released by the mandrel 15, the ball 24 is pressed into a seat 25 by means of the spring 23 and initially closes the first bore 20.

Die Kraft der Feder 23 ist nun so ausgelegt, daß die Kugel 24 dennoch durch den sich im ersten Druckraum 19 aufbauenden Druck öffnen kann und den Weg der Druckflüssigkeit über die erste Bohrung 20 und die zweite Bohrung 21 zum zweiten Druckraum 22 freigibt. Durch die vom zweiten Druckraum 22 auf das Innenteil 8 ausgeübte Kraft wird dieses samt der in der Kugelkalotte 16 gelagerten Stößelstange 3 (Figur 1) angehoben und solange verschoben, bis der Hub 9 (Figur 2) ausgeschöpft ist. Der Hub 9 ergibt sich als eine Funktion der von der Durckquelle 11 geförderten Ölmenge. Diese stellt eine Konstante dar, da die Druckquelle 11 (Figur 1) als Verdrängerpumpe ausgeführt ist. Entsprechend der Wegstrecke des Hubes 9 wird das Auslaßventil 4 (Figur 1) geöffnet. Unter normalen Betriebsbedingungen verbleibt zwischen Innenteil 8 und Anschlagring 8a ein Spiel 9a.The force of the spring 23 is now designed so that the ball 24 can still open due to the pressure building up in the first pressure chamber 19 and opens the path of the pressure fluid via the first bore 20 and the second bore 21 to the second pressure chamber 22. Due to the force exerted by the second pressure chamber 22 on the inner part 8, the latter is lifted together with the push rod 3 (FIG. 1) mounted in the spherical cap 16 and moved until the stroke 9 (FIG. 2) is exhausted. The stroke 9 results as a function of the amount of oil delivered by the pressure source 11. This represents a constant since the pressure source 11 (FIG. 1) is designed as a positive displacement pump. The outlet valve 4 (FIG. 1) is opened in accordance with the distance of the stroke 9. Under normal operating conditions, a play 9a remains between the inner part 8 and the stop ring 8a.

Da die Öffnung des Auslaßventiles 4 während des Verdichtungstaktes erfolgt steigt mit zunehmendem Verdichtungsdruck die in Schließrichtung wirkende Kraft auf das Auslaßventil. Diese Kraft wird über die Stößelstange 3 (Figur 1) auf das Innenteil 8 übertragen.Since the opening of the exhaust valve 4 takes place during the compression stroke, the force acting in the closing direction on the exhaust valve increases with increasing compression pressure. This force is transmitted to the inner part 8 via the push rod 3 (FIG. 1).

Um das Auslaßventil 4 gegen diese steigende Kraft im geöffneten Zustand zu halten müßte der von der Druckquelle 11 bereitzustellende Druck - resultierend aus der Kraft auf das Innenteil 8 und dessen Querschnittsfläche - ständig steigen. Dies führt aber zu Schäden durch Kavitation und Undichtheiten in den druckführenden Organen.In order to keep the outlet valve 4 against this increasing force in the open state, the pressure to be provided by the pressure source 11 would have to be constant - as a result of the force on the inner part 8 and its cross-sectional area climb. However, this leads to damage due to cavitation and leaks in the pressure-carrying organs.

Dies wird erfindungsgemäß dadurch vermieden, daß der im zweiten Druckraum 22 sich aufbauende Druck die Kugel 24 zusätzlich zur Kraft der Feder 23 in den Sitz 25 preßt und dadurch der zweite Druckraum 22 hermetisch abgeriegelt wird und sich der ansteigende Druck nicht mehr über die erste Bohrung 20 und die Bohrungen 18 in die druckführenden Organe zurück fortpflanzen kann. Somit wird die Druckquelle 11 und die Verbindungsleitungen vor erhöhten Drücken und deren nachteiligen Wirkungen verschont. Wenn der von der Druckquelle 11 aufgebrachte Druck absinkt, entriegelt der, von der Druckfeder 13 in Ausgangsstellung zurückbewegte Kolben 12 die Kugel 24 des Ventils 17. Das Öl aus dem zweiten Druckraum 22 kann abströmen und der Hub 9 des Innenteils 8 und damit des Auslaßventils 4 werden beendet.This is avoided according to the invention in that the pressure building up in the second pressure chamber 22 presses the ball 24 into the seat 25 in addition to the force of the spring 23 and the second pressure chamber 22 is thereby hermetically sealed and the increasing pressure no longer passes through the first bore 20 and can propagate the holes 18 back into the pressure-carrying organs. Thus, the pressure source 11 and the connecting lines are spared from increased pressures and their adverse effects. When the pressure applied by the pressure source 11 drops, the piston 12, which is moved back by the compression spring 13 in the starting position, unlocks the ball 24 of the valve 17. The oil from the second pressure chamber 22 can flow out and the stroke 9 of the inner part 8 and thus of the outlet valve 4 are ended.

Nach den Figuren 4 und 5 kann anstelle der mechanischen Hubbegrenzung 14 eine hydraulisch wirkende Hubbegrenzung verwendet werden. Aus diesem Grund werden nach Figur 4 im Innenteil 8 erste und zweite Abregelbohrungen 26, 27 vorgesehen, welche über einen Überströmkanal 28 untereinander verbunden sind. In Ruhestellung des Kolbens 12 kann der von der Bohrung 18 zugeführte Hydraulikdruck auf dessen, dem ersten Druckraum 19 zugewandte Seite einwirken und ihn gegen die Rückstellkraft der Druckfeder 13 verschieben. Wenn die Unterkante 29 des Kolbens 12 die erste Abregelbohrung 26 erreicht, wie es in Figur 5 dargestellt ist, kann über diese, den Überströmkanal 28 und die zweite Abregelbohrung 27 Hydraulikflüssigkeit in den von der Druckfeder 13 ausgefüllten Raum einströmen. Dieser Raum ist über eine Entlastungsbohrung 30 zum Druckausgleich mit der Umgebung verbunden, wodurch eine weitere Bewegung des Kolbens 12 gestoppt wird. Die Funktionen der übrigen Teile gleicht der Ausführung nach den Figuren 2 und 3 und wurde dort ausführlich erläutert. Vorteil dieser Stößelausführung ist, daß auf das Überdruckventil (siehe Anspruch 3) verzichtet werden kann.According to FIGS. 4 and 5, a hydraulically acting stroke limitation can be used instead of the mechanical stroke limitation 14. For this reason, according to FIG. 4, first and second regulating bores 26, 27 are provided in the inner part 8, which are connected to one another via an overflow channel 28. When the piston 12 is in the rest position, the hydraulic pressure supplied by the bore 18 can act on its side facing the first pressure chamber 19 and move it against the restoring force of the compression spring 13. When the lower edge 29 of the piston 12 reaches the first regulating bore 26, as shown in FIG. 5, hydraulic fluid can flow into the space filled by the compression spring 13 via the overflow channel 28 and the second regulating bore 27. This room is over a relief bore 30 is connected to the environment for pressure equalization, whereby a further movement of the piston 12 is stopped. The functions of the other parts are the same as those in FIGS. 2 and 3 and have been explained in detail there. The advantage of this tappet design is that the pressure relief valve (see claim 3) can be dispensed with.

Claims (5)

Auslaß-Ventilstößel für eine Brennkraftmaschine, bei welcher der Ventilstößel zwischen einem Auslaßnocken und einer Stößelstange eines Auslaßventiltriebes eingeschaltet ist, wobei der Ventilstößel im wesentlichen aus einem Stößel-Außenteil und einem darin axial beweglichen und von einer externen Druckquelle beaufschlagbaren Innenteil gebildet wird und das Innenteil mit Spiel axial beweglich im Stößel-Außenteil geführt ist, dadurch gekennzeichnet, daß das Innenteil (8) einen mittels Druckfeder (13) in Ausgangsstellung gehaltenen Kolben (12) aufweist, dessen axiale Bewegung in Richtung der Stößelstange (3) durch eine Hubbegrenzung und an dem der Druckfeder (13) abgewandten Ende durch einen Dorn (15) begrenzbar ist, wobei der Dorn (15) auf eine Kugel (24) drückt, welche in Richtung des Kolbens (12) durch eine Feder (23) belastbar ist, derart, daß zunächst ein zwischen Stößel-Außenteil (7) und Innenteil (8) befindlicher zweiter Druckraum (22) über Bohrungen (18), erste und zweite Bohrungen (20, 21) und einen Ventilsitz (25) mit der externen Druckquelle (11) verbindbar ist und anschließend durch steigenden Druck in einem ersten Druckraum (19), ausgelöst durch die externe Druckquelle (11), der Kolben (12) gegen die Druckfeder (13) bewegt, und damit die Kugel (24) freigegeben wird, wobei die Kugel (24) durch die Feder (23) den zweiten Druckraum (22) gegen den ersten Druckraum (19) absperrt, und wobei die Feder (23) so abgestimmt ist, daß der Druck der Druckquelle (11) zunächst ausreicht, die Kugel (24) vom Ventilsitz (25) abzuheben, wobei das in den zweiten Druckraum (22) einströmende Öl das Innenteil (8) anhebt und dadurch das Auslaßventil (4) geöffnet wird, und daß bei zunehmendem Druck aus der Kraft der Stößelstange (3) auf das Innenteil (8) durch den daraus im zweiten Druckraum (22) resultierenden, ansteigenden Druck die Kugel (24) über den Ventilsitz (25) den Druckraum (22) absperrt und die Rückströmung vom zweiten Druckraum (22) zur externen Druckquelle (11) durch Schließen des Ventilsitzes (25) unterbindet, und daß nach Absinken des Druckes von der externen Druckquelle (11) die Druckfeder (13) den Kolben (12) gegen die Kugel (24) in seine Ausgangslage zurückbringt, wodurch der Ventilsitz (25) geöffnet, das Öl aus dem zweiten Druckraum (22) ausströmen und der Hub des Innenteils (8) und damit des Auslaßventils (4) beendet wird.Exhaust valve tappet for an internal combustion engine, in which the valve tappet is switched between an exhaust cam and a tappet rod of an exhaust valve drive, the valve tappet essentially being formed from an outer tappet and an inner part which is axially movable and can be acted upon by an external pressure source, and the inner part with Play axially movable in the outer part of the tappet, characterized in that the inner part (8) has a piston (12) held in the starting position by means of a compression spring (13), the axial movement of which in the direction of the push rod (3) by means of a stroke limitation and on the the end facing away from the compression spring (13) can be limited by a mandrel (15), the mandrel (15) pressing on a ball (24) which can be loaded in the direction of the piston (12) by a spring (23) such that First a second pressure chamber (22) located between the tappet outer part (7) and inner part (8) via bores (18 ), first and second bores (20, 21) and a valve seat (25) can be connected to the external pressure source (11) and then by increasing pressure in a first pressure chamber (19), triggered by the external pressure source (11), moves the piston (12) against the compression spring (13), thereby releasing the ball (24), the ball (24) being released by the spring (23 ) shuts off the second pressure chamber (22) against the first pressure chamber (19), and wherein the spring (23) is adjusted so that the pressure of the pressure source (11) is initially sufficient to lift the ball (24) from the valve seat (25), wherein the oil flowing into the second pressure chamber (22) lifts the inner part (8) and thereby the outlet valve (4) is opened, and that with increasing pressure from the force of the push rod (3) on the inner part (8) by the resulting in resulting pressure increasing the second pressure chamber (22) the ball (24) shuts off the pressure chamber (22) via the valve seat (25) and prevents the backflow from the second pressure chamber (22) to the external pressure source (11) by closing the valve seat (25), and that after the pressure drops from the external pressure source (11) di e compression spring (13) returns the piston (12) against the ball (24) to its initial position, which opens the valve seat (25), allows the oil to flow out of the second pressure chamber (22) and the stroke of the inner part (8) and thus the Exhaust valve (4) is ended. Auslaß-Ventilstößel nach Anspruch 1, dadurch gekennzeichnet, daß die Hubbegrenzung aus einem Anschlag (14) gebildet wird, welcher starr mit dem Kolben (12) verbunden ist.Exhaust valve lifter according to claim 1, characterized in that the stroke limitation is formed from a stop (14) which is rigidly connected to the piston (12). Auslaß-Ventilstößel nach den Ansprüchen 1 und 2, dadurch gekennzeichnet, daß der maximale Hub (9) und eines verbleibenden Spiels (9a) des Stößel-Innenteiles (8) durch einen Anschlagring (8a) begrenzt wird, um ein Anschlagen des Auslaßventiles (4) auf einen Motor-Kolben bei extremer Überdrehzahl sicher zu vermeiden, wobei das in diesem Falle wegen des bereits durch den normalen Öldruck vollzogenen Zusatzhubes von einer Hydraulikpumpeneinheit der Druckquelle (11) unnötig geförderte Öl über ein Überdruckventil in der Hydraulikpumpeneinheit entweicht.Exhaust valve tappet according to claims 1 and 2, characterized in that the maximum stroke (9) and a remaining play (9a) of the tappet inner part (8) is limited by a stop ring (8a), in order to reliably prevent the exhaust valve (4) from striking a motor piston at extreme overspeed, in this case the oil which is unnecessarily pumped by a hydraulic pump unit of the pressure source (11) due to the additional stroke already carried out by the normal oil pressure via a pressure relief valve in the Hydraulic pump unit escapes. Auslaß-Ventilstößel nach Anspruch 1 und 3, dadurch gekennzeichnet, daß die Hubbegrenzung aus einer ersten und zweiten Abregelbohrung (26, 27) gebildet wird, wobei die erste Abregelbohrung (26) derart im Innenteil (8) lokalisiert ist, daß bei gewünschter Endlage des Kolbens (12) dieser Kolben die erste Abregelbohrung (26) freigibt, so daß diese über einen Überströmkanal (28), die zweite Abregelbohrung (27) und eine Entlastungsbohrung (30) mit der Umgebung korrespondiert.Exhaust valve lifter according to claim 1 and 3, characterized in that the stroke limiter is formed from a first and second regulating bore (26, 27), the first regulating bore (26) being located in the inner part (8) in such a way that when the desired end position of the Piston (12) of this piston releases the first regulating bore (26) so that it corresponds to the environment via an overflow channel (28), the second regulating bore (27) and a relief bore (30). Auslaß-Ventilstößel nach den Ansprüchen 1 bis 3, dadurch gekennzeichnet, daß der Hub (9) so festgelegt ist, daß im regulären Motor-Bremsbetrieb bei maximalem Zusatzhub, der durch die Hydraulikpumpeneinheit der Druckquelle (11) ausgelöst wird, ein Spiel (9a) zwischen Stößel-Innenteil (8) und Anschlagring (8a) vorhanden ist.Exhaust valve lifter according to claims 1 to 3, characterized in that the stroke (9) is fixed so that in regular engine braking operation with a maximum additional stroke, which is triggered by the hydraulic pump unit of the pressure source (11), a play (9a) between the tappet inner part (8) and stop ring (8a).
EP92100960A 1991-01-29 1992-01-22 Method for actuating an exhaust valve tappet during braking of an internal combustion engine Expired - Lifetime EP0497194B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4102537 1991-01-29
DE4102537A DE4102537A1 (en) 1991-01-29 1991-01-29 EXHAUST VALVE TUNEL FOR AN INTERNAL COMBUSTION ENGINE

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EP0497194A1 true EP0497194A1 (en) 1992-08-05
EP0497194B1 EP0497194B1 (en) 1995-04-05

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JP (1) JPH04311615A (en)
DE (2) DE4102537A1 (en)
ZA (1) ZA92569B (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996034183A1 (en) * 1995-04-27 1996-10-31 Ina Wälzlager Schaeffler Kg Hydraulic clearance compensator
WO2011134790A3 (en) * 2010-04-26 2012-03-15 Schaeffler Technologies Gmbh & Co. Kg Hydraulic valve play compensating element for reciprocating-piston internal combustion engines

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5253621A (en) * 1992-08-14 1993-10-19 Group Lotus Plc Valve control means
DE4209775A1 (en) * 1992-03-26 1993-09-30 Man Nutzfahrzeuge Ag Device for controlling an exhaust valve in engine braking mode
US5233951A (en) * 1992-09-25 1993-08-10 Hausknecht Louis A Flow restriction controlled variable engine valve system
US5327858A (en) * 1992-09-25 1994-07-12 Hausknecht Louis A Flow restriction controlled variable engine valve system
DE4238325C2 (en) * 1992-11-13 1999-09-09 Iav Motor Gmbh Switchable valve train with rocker arm and underlying camshaft for gas exchange valves of internal combustion engines
DE4334006C2 (en) * 1993-10-06 1996-10-10 Man Nutzfahrzeuge Ag Device for increasing the engine braking power of an internal combustion engine
US5372114A (en) * 1993-10-29 1994-12-13 Cummins Engine Company, Inc. Dampened pressure regulating and load cell tappet
DE9319435U1 (en) * 1993-12-17 1994-02-10 INA Wälzlager Schaeffler KG, 91074 Herzogenaurach Switchable support element
US5540201A (en) 1994-07-29 1996-07-30 Caterpillar Inc. Engine compression braking apparatus and method
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
DE4443137A1 (en) * 1994-12-03 1996-06-05 Bosch Gmbh Robert Method for determining the spring force of a closing spring when opening a valve, in particular a fuel injector, and device for carrying out the method
JP2002502004A (en) * 1998-02-02 2002-01-22 ディーゼル エンジン リターダーズ，インコーポレイテッド Self-braking slave piston arrangement with backlash adjustment for compression-release engine brakes
US6085721A (en) * 1998-04-03 2000-07-11 Diesel Engine Retarders, Inc. Bar engine brake
US6273057B1 (en) 1998-08-19 2001-08-14 Diesel Engine Retarders, Inc. Hydraulically-actuated fail-safe stroke-limiting piston
US5964193A (en) * 1998-08-20 1999-10-12 Ford Global Technologies, Inc. Synchronous hydraulic lash adjuster
KR100510751B1 (en) * 2003-07-29 2005-08-26 김용구 Air jack using oil jack and air booster
DE102004053203A1 (en) 2004-11-04 2006-06-01 Schaeffler Kg Variable valve train of an internal combustion engine
DE102004053202A1 (en) 2004-11-04 2006-06-01 Schaeffler Kg Valve gear of an internal combustion engine
DE102007014248A1 (en) * 2007-03-24 2008-09-25 Schaeffler Kg Reciprocating internal combustion engine with engine braking device
CN109296788B (en) * 2018-11-17 2021-12-21 徐州启峰智能科技有限公司 Exhaust device

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2006373A (en) * 1977-10-10 1979-05-02 Ricardo & Co Eng 1927 Ltd I. C. Engine Valve Clearance Regulating Means
US4164917A (en) * 1977-08-16 1979-08-21 Cummins Engine Company, Inc. Controllable valve tappet for use with dual ramp cam
FR2584773A1 (en) * 1985-07-15 1987-01-16 Peugeot Device for the variable control of an internal combustion engine valve

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3786792A (en) * 1971-05-28 1974-01-22 Mack Trucks Variable valve timing system
DE2832542A1 (en) * 1978-07-25 1980-02-07 Maschf Augsburg Nuernberg Ag INTERNAL COMBUSTION ENGINE WITH ENGINE BRAKE
US4408580A (en) * 1979-08-24 1983-10-11 Nippon Soken, Inc. Hydraulic valve lift device
US4337739A (en) * 1980-03-24 1982-07-06 Jordan Edgar R Valve control mechanism for internal combustion engines
DE3026529A1 (en) * 1980-07-12 1982-02-11 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Exhaust valve brake for IC engine - uses hydraulic plunger in tappet to cyclically increase valve drive-line effective length
US4399787A (en) * 1981-12-24 1983-08-23 The Jacobs Manufacturing Company Engine retarder hydraulic reset mechanism
JPS603436A (en) * 1983-06-22 1985-01-09 Mitsubishi Heavy Ind Ltd Exhaust brake system
GB8614310D0 (en) * 1986-06-12 1986-07-16 South Western Ind Res Variable actuator
DE3923371C1 (en) * 1989-07-14 1990-06-13 Daimler-Benz Aktiengesellschaft, 7000 Stuttgart, De IC engine valve control system - can adjust exhaust valve lift to give throttle effect during engine braking

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4164917A (en) * 1977-08-16 1979-08-21 Cummins Engine Company, Inc. Controllable valve tappet for use with dual ramp cam
GB2006373A (en) * 1977-10-10 1979-05-02 Ricardo & Co Eng 1927 Ltd I. C. Engine Valve Clearance Regulating Means
FR2584773A1 (en) * 1985-07-15 1987-01-16 Peugeot Device for the variable control of an internal combustion engine valve

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1996034183A1 (en) * 1995-04-27 1996-10-31 Ina Wälzlager Schaeffler Kg Hydraulic clearance compensator
WO2011134790A3 (en) * 2010-04-26 2012-03-15 Schaeffler Technologies Gmbh & Co. Kg Hydraulic valve play compensating element for reciprocating-piston internal combustion engines

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DE59201799D1 (en) 1995-05-11
DE4102537A1 (en) 1992-07-30
JPH04311615A (en) 1992-11-04
EP0497194B1 (en) 1995-04-05
US5161500A (en) 1992-11-10
ZA92569B (en) 1992-10-28

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