EP1143121A2 - Engine braking system with displaceable rocker arm pivot centre - Google Patents

Engine braking system with displaceable rocker arm pivot centre Download PDF

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Publication number
EP1143121A2
EP1143121A2 EP01105766A EP01105766A EP1143121A2 EP 1143121 A2 EP1143121 A2 EP 1143121A2 EP 01105766 A EP01105766 A EP 01105766A EP 01105766 A EP01105766 A EP 01105766A EP 1143121 A2 EP1143121 A2 EP 1143121A2
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EP
European Patent Office
Prior art keywords
rocker arm
piston
shaft
rocker
engages
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
EP01105766A
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German (de)
French (fr)
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EP1143121B1 (en
EP1143121A3 (en
Inventor
David James Haugen
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Deere and Co
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Deere and Co
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Publication of EP1143121A3 publication Critical patent/EP1143121A3/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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • 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
    • 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

Definitions

  • the invention relates to an engine brake device with a rocker arm arranged pivotably on a shaft, one in a piston chamber arranged piston, the position of one controlled by a pressure control device and on pressure is dependent on it, with a movement of the Piston shifting the pivot axis of the rocker arm causes.
  • engine brake devices are known.
  • One type of engine brake device is a freewheel element provided in one end of a rocker arm or in connections, that connect the rocker arm to a cam or valve, to allow a control mechanism to target an area react to the cam profile or ignore it.
  • a another type of engine brake device is disclosed in US-A-5,647,319 and shown in US-A-3,367,312. Both engine braking devices have a braking mechanism in which a Swivel center of an outlet rocker arm through an eccentric is shifted or postponed, which with a Hydraulic piston / actuator is connected via a lever arm.
  • an engine brake device is available which is simple in construction, since it is only a small one Has number of components. Most of these components need not have increased requirements regarding the Manufacturing tolerances meet and are not increased Loads particularly in the type of bending stress exposed. Such a system has a reduced Complexity and is therefore inexpensive and insensitive to errors. Due to the lower number of components and the waiver of additional levers or connections Height of a drive with an inventive Engine brake device not or only slightly increased.
  • the projection has a convex Surface, which with an appropriately trained Surface of the piston, which is preferably concave is cooperating.
  • the displacement of the rocker arm or its pivot axis can be achieved in that a hole in the rocker arm has a larger diameter than the shaft on which it is arranged.
  • the relocation option is thereby limited that the rocker arm or its bore on at least in substantially opposite sides of the shaft in Depending on the position of the piston come to rest can.
  • an engine brake device (compression braking system) 10 shown which a Exhaust valve rocker arm 12 pivotable via a rocker arm shaft or shaft 14, which is supported by a rocker arm shaft bore or a bore 15 is received.
  • the shaft 14 has one Diameter, which by a small amount, like for example, 7.62 mm (0.030 inches), is smaller than that Hole 15.
  • One end of rocker arm 12 carries a roller 16, which on a camshaft 18 with a molded Freewheel cam 20 attacks.
  • the other end of the rocker arm 12 engages an exhaust valve stem assembly 22. Because of the bias of the springs of the valve stem assembly 22 the rocker arm 12 normally abuts a bottom the shaft 14 held, as can be seen from the figure can.
  • the rocker arm 12 has a projection 24 which extends away from him.
  • the projection 24 has one partially cylindrical convex outer surface 26.
  • On Piston 28 engages the projection 24 and has one cylindrical concave surface 29, which with the convex Surface 26 of projection 24 is
  • the piston 28 is displaceable in a piston bore 30 added, which is provided in a housing 32, which preferably part of a cylinder block of a diesel drive (not shown).
  • the piston 28 and a wall of the Piston bore 30 enclose a pressure chamber 34.
  • the pressure in the pressure chamber 34 is preferably by a Pressure control unit 36 controlled, which preferably also is arranged in the housing 32, as it is from "FAQs: Engine Brake Theory, "by Jacobs Vehicle Systems, in 1996.
  • the pressure control unit 36 preferably has a solenoid valve not shown), and the application of the solenoid valve is controlled by a switch 46 operated by an operator can be operated, controlled, which preferably with a Vehicle battery 48 via a fuel pump switch 50, a clutch switch 52 and a fuse 54 is connected. Pressurization of the pressure chamber 34 causes the Piston 28 moves in the direction of the shaft 14 and thereby one central area of the rocker arm 12 moves until the wall of the Bore 15 engages an upper part of the shaft 14 so that the pivot axis of the rocker arm 12 is shifted.
  • this engine brake device 10 uses electronically controlled hydraulic elements to the Pivot position of the rocker arm 12 for decelerating the drive or To control braking.
  • a control of the swivel position of the Rocker arm 12 allows some or all of it Exhaust cam profile / movement of the camshaft 18 to the valve stem assembly 22 to be transmitted.
  • the selected one Transmission of part or all of the exhaust cam movement to the valves determined in connection with the fuel supply level of the drive the ability of the drive positive Generate power or absorb (braking) power.
  • Expansion of the piston 28 moves the rocker arm pivot point transversely to its axis so that the rocker arm 12 is selective react to the movement of the freewheel cam 20 or this can ignore.
  • the pressure on the piston 28 can be controlled be so that the piston 28 selectively a light force or a very large force on the rocker arm 12, so that the The pivot point of the rocker arm 12 is controlled.
  • a minor one Piston force allows the rocker arm 12 in its normal position to work when the drive (not shown) -under load located. This normal position prevents the rocker arm 12 to respond to the freewheel cam 20 and forces on the Valve stem assembly 22 to transfer because of the freewheel cam 20 is small enough to "lose" in the valve clearance.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Braking Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

An engine compression braking system includes an exhaust rocker arm pivotally supported on rocker shaft. One end of the rocker arm carries a roller which engages a camshaft which has a lost motion bump formed thereon. The other end of the rocker arm engages an exhaust valve stem assembly. A part of the rocker shaft engages a pressure operated piston. Extension of the piston moves the rocker shaft transversely to its axis, so that the rocker arm can selectively react to or ignore the lost motion portion bump. A pressure control system includes a solenoid operated valve controlled by an operator controlled switch, so that the piston selectively applies a light force or a very high force to the rocker arm rocker shaft, thus controlling the pivot point of the rocker arm.

Description

Die Erfindung betrifft eine Motorbremseinrichtung mit einem schwenkbar auf einer Welle angeordneten Kipphebel, einem in einer Kolbenkammer angeordneten Kolben, dessen Stellung von einem durch eine Drucksteuerungseinrichtung gesteuerten und auf ihn ausgeübten Druck abhängig ist, wobei eine Bewegung des Kolbens eine Verlagerung der Schwenkachse des Kipphebels bewirkt.The invention relates to an engine brake device with a rocker arm arranged pivotably on a shaft, one in a piston chamber arranged piston, the position of one controlled by a pressure control device and on pressure is dependent on it, with a movement of the Piston shifting the pivot axis of the rocker arm causes.

Es sind verschiedene Arten von Motorbremseinrichtungen bekannt. Bei einer Art von Motorbremseinrichtung ist ein Freilaufelement in einem Ende eines Kipphebels oder in Verbindungen vorgesehen, die den Kipphebel mit einem Nocken oder einem Ventil verbinden, um es einem Steuermechanismus zu erlauben, auf einen Bereich des Nockenprofils zu reagieren oder diesen zu ignorieren. Eine andere Art von Motorbremseinrichtung wird in der US-A-5,647,319 und in der US-A-3,367,312 gezeigt. Beide Motorbremseinrichtungen weisen einen Bremsmechanismus auf, bei dem ein Schwenkzentrum eines Auslaß-Kipphebels durch einen Exzenter verlagert oder verschoben wird, welcher mit einem Hydraulikkolben/-betätiger über einen Hebelarm verbunden ist.Various types of engine brake devices are known. One type of engine brake device is a freewheel element provided in one end of a rocker arm or in connections, that connect the rocker arm to a cam or valve, to allow a control mechanism to target an area react to the cam profile or ignore it. A another type of engine brake device is disclosed in US-A-5,647,319 and shown in US-A-3,367,312. Both engine braking devices have a braking mechanism in which a Swivel center of an outlet rocker arm through an eccentric is shifted or postponed, which with a Hydraulic piston / actuator is connected via a lever arm.

Das der Erfindung zugrunde liegende Problem wird darin gesehen, daß bekannte Motorbremseinrichtungen aufwendig und störungsanfällig sind.The problem underlying the invention is seen in that known engine braking devices are complex and are prone to failure.

Dieses Problem wird erfindungsgemäß durch die Lehre des Patentanspruchs 1 gelöst, wobei in den weiteren Patentansprüchen die Lösung in vorteilhafter Weise weiterentwickelnde Merkmale aufgeführt sind.This problem is solved according to the invention by the teaching of the patent claim 1 solved, the in the further claims Features that further develop features in an advantageous manner are listed.

Auf diese Weise wird eine Motorbremseinrichtung zur Verfügung gestellt, die einfach im Aufbau ist, da sie nur eine geringe Anzahl von Bauteilen aufweist. Die meisten dieser Bauteile müssen keine erhöhten Erfordernisse bezüglich der Fertigungstoleranzen erfüllen und sind auch keinen erhöhten Belastungen insbesondere in der Art von Biegebeanspruchungen ausgesetzt. Ein solches System weist eine reduzierte Komplexität auf und ist daher kostengünstig und fehlerunempfindlich. Aufgrund der geringeren Bauteilanzahl und einem Verzicht auf zusätzliche Hebel bzw. Verbindungen wird die Bauhöhe eines Antriebs mit einer erfindungsgemäßen Motorbremseinrichtung nicht bzw. nur geringfügig erhöht.In this way, an engine brake device is available which is simple in construction, since it is only a small one Has number of components. Most of these components need not have increased requirements regarding the Manufacturing tolerances meet and are not increased Loads particularly in the type of bending stress exposed. Such a system has a reduced Complexity and is therefore inexpensive and insensitive to errors. Due to the lower number of components and the waiver of additional levers or connections Height of a drive with an inventive Engine brake device not or only slightly increased.

Es ist denkbar, daß der Kolben direkt auf den Kipphebel bzw. auf eine zumindest im wesentlichen ebene Fläche/Oberfläche des Kipphebels einwirkt oder auch in eine dort vorgesehene, geeignet ausgebildete Vertiefung an dem Kipphebel eingreift. Besonders einfach in Montage ist es aber, wenn an dem Kipphebel ein Vorsprung vorgesehen ist, an dem ein Endbereich des Kolbens angreifen kann. Auf diese Weise wird darüber hinaus gewährleistet, daß ein dauerhaftes Zusammenwirken des Kolbens und des Kipphebels sichergestellt wird.It is conceivable that the piston directly on the rocker arm or on an at least substantially flat surface / surface of the Acts rocker arm or also in a provided there suitably designed recess engages on the rocker arm. But it is particularly easy to assemble when on the rocker arm a projection is provided on which an end region of the piston can attack. This way it will go beyond that ensures that the piston works together permanently and the rocker arm is ensured.

Um eine Schwenkbewegung des Kipphebels zu begünstigen, ohne daß es zu einem Verkanten oder Verklemmen zwischen dem Kipphebel und Kolben kommen kann, weist der Vorsprung eine konvexe Oberfläche auf, welche mit einer entsprechend ausgebildeten Oberfläche des Kolbens, die vorzugsweise konkav ausgestaltet ist, zusammenwirkt.In order to favor a pivoting movement of the rocker arm without jamming or jamming between the rocker arm and piston can come, the projection has a convex Surface, which with an appropriately trained Surface of the piston, which is preferably concave is cooperating.

Die Verlagerung des Kipphebels bzw. seiner Schwenkachse kann dadurch erzielt werden, daß eine Bohrung in dem Kipphebel einen größeren Durchmesser aufweist, als die Welle auf der er angeordnet ist. Die Verlagerungsmöglichkeit wird dadurch begrenzt, daß der Kipphebel bzw. seine Bohrung an zumindest im wesentlichen gegenüberliegenden Seiten der Welle in Abhängigkeit von der Stellung des Kolbens zur Anlage kommen kann.The displacement of the rocker arm or its pivot axis can can be achieved in that a hole in the rocker arm has a larger diameter than the shaft on which it is arranged. The relocation option is thereby limited that the rocker arm or its bore on at least in substantially opposite sides of the shaft in Depending on the position of the piston come to rest can.

Vorzugsweise handelt es sich bei der Seite der Welle, an der der Kipphebel anliegt, wenn der Kolben durch Druck belastet wird, um die Oberseite der Welle und entsprechend um die Unterseite, wenn der Kolben nicht belastet ist, da dies der Richtung der Vorspannung der durch den Kipphebel betätigten Ventile bzw. Ventilschaftzusammenbauten entspricht.It is preferably the side of the shaft on which the rocker arm rests when the piston is loaded by pressure to the top of the shaft and accordingly around the Underside when the piston is not loaded, as this is the Direction of preload of those operated by the rocker arm Corresponds to valves or valve stem assemblies.

In der Zeichnung ist ein nachfolgend näher beschriebenes Ausführungsbeispiel der Erfindung dargestellt.In the drawing is one described in more detail below Embodiment of the invention shown.

Mit Bezug auf die einzige Figur wird eine Motorbremseinrichtung (compression braking system) 10 gezeigt, welche einen Auslaßventil-Kipphebel 12 schwenkbar über eine Kipphebelwelle bzw. Welle 14 stützt, welche durch eine Kipphebelwellenbohrung bzw. eine Bohrung 15 aufgenommen wird. Die Welle 14 weist einen Durchmesser auf, welcher um einen kleinen Betrag, wie beispielsweise 7,62 mm (0,030 Inch), kleiner ist als die Bohrung 15. Ein Ende des Kipphebels 12 trägt eine Rolle 16, welche an einer Nockenwelle 18 mit einem angeformten Freilaufnocken 20 angreift. Das andere Ende des Kipphebels 12 greift an einem Auslaß-Ventilschaftzusammenbau 22 an. Aufgrund der Vorspannung der Federn des Ventilschaftzusammenbaus 22 wird der Kipphebel 12 normalerweise in Anlage mit einer Unterseite der Welle 14 gehalten, wie dies aus der Figur ersehen werden kann. Der Kipphebel 12 weist einen Vorsprung 24 auf, welcher sich von ihm weg erstreckt. Der Vorsprung 24 weist eine teilweise zylindrisch konvexe äußere Oberfläche 26 auf. Ein Kolben 28 greift an dem Vorsprung 24 an und weist eine zylindrisch konkave Oberfläche 29 auf, welche mit der konvexen Oberfläche 26 des Vorsprungs 24 in Eingriff steht.With reference to the single figure, an engine brake device (compression braking system) 10 shown which a Exhaust valve rocker arm 12 pivotable via a rocker arm shaft or shaft 14, which is supported by a rocker arm shaft bore or a bore 15 is received. The shaft 14 has one Diameter, which by a small amount, like for example, 7.62 mm (0.030 inches), is smaller than that Hole 15. One end of rocker arm 12 carries a roller 16, which on a camshaft 18 with a molded Freewheel cam 20 attacks. The other end of the rocker arm 12 engages an exhaust valve stem assembly 22. Because of the bias of the springs of the valve stem assembly 22 the rocker arm 12 normally abuts a bottom the shaft 14 held, as can be seen from the figure can. The rocker arm 12 has a projection 24 which extends away from him. The projection 24 has one partially cylindrical convex outer surface 26. On Piston 28 engages the projection 24 and has one cylindrical concave surface 29, which with the convex Surface 26 of projection 24 is engaged.

Der Kolben 28 wird verschiebbar in einer Kolbenbohrung 30 aufgenommen, die in einem Gehäuse 32 vorgesehen ist, welches vorzugsweise Teil eines Zylinderblocks eines Dieselantriebs (nicht gezeigt) ist. Der Kolben 28 und eine Wand der Kolbenbohrung 30 umschließen eine Druckkammer 34. Der Druck in der Druckkammer 34 wird vorzugsweise durch eine Drucksteuereinheit 36 gesteuert, welche vorzugsweise ebenfalls in dem Gehäuse 32 angeordnet ist, wie es aus "FAQs: Engine Brake Theory", by Jacobs Vehicle Systems, 1996 bekannt ist. The piston 28 is displaceable in a piston bore 30 added, which is provided in a housing 32, which preferably part of a cylinder block of a diesel drive (not shown). The piston 28 and a wall of the Piston bore 30 enclose a pressure chamber 34. The pressure in the pressure chamber 34 is preferably by a Pressure control unit 36 controlled, which preferably also is arranged in the housing 32, as it is from "FAQs: Engine Brake Theory, "by Jacobs Vehicle Systems, in 1996.

Die Drucksteuereinheit 36 weist vorzugsweise ein Magnetventil nicht gezeigt) auf, und die Beaufschlagung des Magnetventils wird durch einen Schalter 46, der durch eine Bedienungsperson betätigt werden kann, gesteuert, welcher vorzugsweise mit einer Fahrzeugbatterie 48 über einen Kraftstoffpumpenschalter 50, einen Kupplungsschalter 52 und eine Sicherung 54 verbunden ist. Eine Druckbeaufschlagung der Druckkammer 34 bewirkt, daß der Kolben 28 sich in Richtung der Welle 14 bewegt und dabei einen zentralen Bereich des Kipphebels 12 bewegt, bis die Wand der Bohrung 15 an einem oberen Teil der Welle 14 angreift, so daß die Schwenkachse des Kipphebels 12 verschoben wird.The pressure control unit 36 preferably has a solenoid valve not shown), and the application of the solenoid valve is controlled by a switch 46 operated by an operator can be operated, controlled, which preferably with a Vehicle battery 48 via a fuel pump switch 50, a clutch switch 52 and a fuse 54 is connected. Pressurization of the pressure chamber 34 causes the Piston 28 moves in the direction of the shaft 14 and thereby one central area of the rocker arm 12 moves until the wall of the Bore 15 engages an upper part of the shaft 14 so that the pivot axis of the rocker arm 12 is shifted.

Auf diese Weise benutzt diese Motorbremseinrichtung 10 elektronisch gesteuerte Hydraulikelemente, um die Schwenkstellung des Kipphebels 12 zur Antriebsverzögerung oder Bremsung zu steuern. Eine Steuerung der Schwenkstellung des Kipphebels 12 erlaubt es einem Teil oder dem/der gesamten Auslaßnockenprofil/-bewegung der Nockenwelle 18 zu dem Ventilschaftzusammenbau 22 übertragen zu werden. Die ausgewählte Übertragung eines Teils oder der gesamten Auslaßnockenbewegung zu den Ventilen bestimmt in Verbindung mit dem Kraftstoffzufuhrniveau des Antriebs die Fähigkeit des Antriebs positive Leistung zu erzeugen oder (Brems-)Leistung zu absorbieren.In this way, this engine brake device 10 uses electronically controlled hydraulic elements to the Pivot position of the rocker arm 12 for decelerating the drive or To control braking. A control of the swivel position of the Rocker arm 12 allows some or all of it Exhaust cam profile / movement of the camshaft 18 to the valve stem assembly 22 to be transmitted. The selected one Transmission of part or all of the exhaust cam movement to the valves determined in connection with the fuel supply level of the drive the ability of the drive positive Generate power or absorb (braking) power.

Eine Ausdehnung des Kolbens 28 bewegt den Kipphebelschwenkpunkt transversal zu seiner Achse, so daß der Kipphebel 12 selektiv auf die Bewegung des Freilaufnockens 20 reagieren oder diese ignorieren kann. Der Druck auf den Kolben 28 kann gesteuert werden, so daß der Kolben 28 selektiv eine leichte Kraft oder eine sehr große Kraft an den Kipphebel 12, anlegt, so daß der Schwenkpunkt des Kipphebels 12 gesteuert wird. Eine geringe Kolbenkraft erlaubt es dem Kipphebel 12 in seiner normalen Lage zu arbeiten, wenn sich der Antrieb (nicht gezeigt) -unter Last befindet. Diese normale Stellung hindert den Kipphebel 12 daran, auf den Freilaufnocken 20 zu reagieren und Kräfte an den Ventilschaftzusammenbau 22 zu übertragen, da der Freilaufnocken 20 klein genug ist, um sich in dem Ventilspiel zu "verlieren". Expansion of the piston 28 moves the rocker arm pivot point transversely to its axis so that the rocker arm 12 is selective react to the movement of the freewheel cam 20 or this can ignore. The pressure on the piston 28 can be controlled be so that the piston 28 selectively a light force or a very large force on the rocker arm 12, so that the The pivot point of the rocker arm 12 is controlled. A minor one Piston force allows the rocker arm 12 in its normal position to work when the drive (not shown) -under load located. This normal position prevents the rocker arm 12 to respond to the freewheel cam 20 and forces on the Valve stem assembly 22 to transfer because of the freewheel cam 20 is small enough to "lose" in the valve clearance.

Eine große Kolbenkraft verschiebt und hält den Kipphebel 12 an der Oberseite der Welle 14, wodurch der Kipphebel 12 auf den Freilaufnocken 20 reagiert und Kraft an den Ventilschaftzusammenbau 22 überträgt, da der Kipphebel 12 kein effektives Ventilspiel aufweist.A large piston force shifts and stops the rocker arm 12 the top of the shaft 14, whereby the rocker arm 12 on the Freewheel cam 20 responds and force to the Valve stem assembly 22 transmits because the rocker arm 12 does not has effective valve clearance.

Das oben beschriebene System weist keine zusätzlichen mechanischen Komponenten zwischen dem Hydraulikzylinder/betätiger und dem Kipphebel 12 auf, wodurch eine verbesserte Funktion, Zuverlässigkeit und verringerte Kosten erzielt werden. Da der Kolben 28 nur eine Druckkraft auf den Kipphebel 12 ausübt, werden Biegebelastungen vermieden und die Fehlerwahrscheinlichkeit reduziert. Eine geringere Teileanzahl resultiert in geringeren Anforderungen an die Fertigungstoleranzen der Komponenten neben dem/der Hydraulikzylinder/-bohrung und der Bohrung 15. Abschließend ermöglicht dieses Design einen kompakten Antrieb von geringer Höhe.The system described above has no additional mechanical components between the hydraulic cylinder / actuator and the rocker arm 12, whereby an improved Function, reliability and reduced costs achieved become. Because the piston 28 only exerts a compressive force on the rocker arm 12 exercises, bending stresses are avoided and the Error probability reduced. A lower number of parts results in lower demands on the Manufacturing tolerances of the components next to the hydraulic cylinder / bore and the bore 15. Finally, allows this design has a compact drive of low height.

Obwohl die vorliegende Erfindung in Zusammenhang mit einer spezifischen Ausführungsform beschrieben wurde, sollte es klar sein, daß viele verschiedene Alternativen, Modifikationen und Variationen für den Fachmann im Lichte der vorausgegangenen Beschreibung offenkundig sind. Entsprechend ist es beabsichtigt, daß diese Erfindung alle solchen Alternativen, Modifikationen und Variationen umfaßt, welche in den Geist und Umfang der folgenden Ansprüche fallen.Although the present invention is related to a specific embodiment, it should be clear be that many different alternatives, modifications and Variations for the expert in the light of the previous ones Description are obvious. It is accordingly intends that this invention include all such alternatives, Modifications and variations included, which in the mind and The scope of the following claims falls.

Claims (5)

Motorbremseinrichtung (10) mit einem schwenkbar auf einer Welle (14) angeordneten Kipphebel (12), sowie einem Kolben (28), dessen Stellung druckabhängig ist und durch eine Drucksteuerungseinrichtung (36) bestimmt wird, wobei der Kolben (28) derart wirksam mit dem Kipphebel (12) verbunden ist, daß eine Bewegung des Kolbens (28) eine Verlagerung der Schwenkachse des Kipphebels (12) bewirkt, dadurch gekennzeichnet, daß der Kolben (28) einen Endbereich (24) aufweist, welcher direkt an dem Kipphebel (12) angreift.Motor brake device (10) with a rocker arm (12) arranged pivotably on a shaft (14), and a piston (28), the position of which is pressure-dependent and is determined by a pressure control device (36), the piston (28) being so effective with the Rocker arm (12) is connected such that movement of the piston (28) causes a displacement of the pivot axis of the rocker arm (12), characterized in that the piston (28) has an end region (24) which is directly on the rocker arm (12) attacks. Motorbremseinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Kipphebel (12) einen Vorsprung (24) aufweist, der an dem Endbereich des Kolbens (28) angreift.Engine braking device according to claim 1, characterized in that the rocker arm (12) has a projection (24) which engages the end region of the piston (28). Motorbremseinrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Vorsprung (24) eine zumindest im wesentlichen konvex ausgebildete Oberfläche (26) aufweist, welche mit einer vorzugsweise wenigstens annähernd konkav ausgebildeten Oberfläche (29) des Kolbens (28) zusammenwirkt.Engine braking device according to claim 2, characterized in that the projection (24) has an at least substantially convex surface (26) which interacts with a preferably at least approximately concave surface (29) of the piston (28). Motorbremseinrichtung nach einem oder mehreren der vorherigen Ansprüche, dadurch gekennzeichnet, daß der Kipphebel (12) in einem ersten Betriebsmodus in an einem ersten Bereich der Welle (14) anliegt und durch eine Bewegung des Kolbens (28) in Anlage mit einem zweiten, vorzugsweise zumindest im wesentlichen gegenüberliegenden Bereich der Welle (14) gelangen kann. Engine brake device according to one or more of the preceding claims, characterized in that the rocker arm (12) rests in a first operating mode in a first region of the shaft (14) and by movement of the piston (28) in contact with a second, preferably at least can reach substantially opposite area of the shaft (14). Motorbremseinrichtung nach Anspruch 4, dadurch gekennzeichnet das der erste Bereich an einer Unterseite der Welle (14) und der zweite Bereich on einer Oberseite der Welle (14) angeordnet ist.Engine braking device according to claim 4, characterized in that the first region is arranged on an underside of the shaft (14) and the second region on an upper side of the shaft (14).
EP01105766A 2000-03-21 2001-03-08 Engine braking system with displaceable rocker arm pivot centre Expired - Lifetime EP1143121B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US528936 2000-03-21
US09/528,936 US6213091B1 (en) 2000-03-21 2000-03-21 Engine compression brake system

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EP1143121A2 true EP1143121A2 (en) 2001-10-10
EP1143121A3 EP1143121A3 (en) 2001-10-24
EP1143121B1 EP1143121B1 (en) 2005-06-08

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US (1) US6213091B1 (en)
EP (1) EP1143121B1 (en)
AT (1) ATE297499T1 (en)
CA (1) CA2322988A1 (en)
DE (1) DE50106426D1 (en)
ZA (1) ZA200102329B (en)

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CN105723055A (en) * 2013-11-13 2016-06-29 戴姆勒股份公司 Engine braking device for an internal combustion engine

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US8746190B2 (en) 2010-11-15 2014-06-10 Achates Power, Inc. Two stroke opposed-piston engines with compression release for engine braking
JP6144206B2 (en) 2011-02-23 2017-06-07 アカーテース パワー，インク． 2-stroke opposed piston engine with engine brake
CN103775154B (en) * 2014-01-26 2016-01-20 天津大学 A kind of hydraulic type changeable air valve rocker arm system
US10024247B2 (en) * 2015-03-25 2018-07-17 Cummins Inc. Engine brake lever
US9429049B2 (en) 2015-05-11 2016-08-30 Caterpillar Inc. Intake valve actuation system for dual fuel engine
CN107143394B (en) * 2017-05-27 2023-05-12 东风商用车有限公司 Split rocker arm braking mechanism of heavy diesel engine of commercial vehicle

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EP1143121B1 (en) 2005-06-08
ZA200102329B (en) 2002-09-20
EP1143121A3 (en) 2001-10-24
CA2322988A1 (en) 2001-09-21
DE50106426D1 (en) 2005-07-14
US6213091B1 (en) 2001-04-10
ATE297499T1 (en) 2005-06-15

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