EP1568859B1 - Kipphebeleinrichtung für Ventilsteuerung - Google Patents

Kipphebeleinrichtung für Ventilsteuerung Download PDF

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Publication number
EP1568859B1
EP1568859B1 EP04100732A EP04100732A EP1568859B1 EP 1568859 B1 EP1568859 B1 EP 1568859B1 EP 04100732 A EP04100732 A EP 04100732A EP 04100732 A EP04100732 A EP 04100732A EP 1568859 B1 EP1568859 B1 EP 1568859B1
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EP
European Patent Office
Prior art keywords
rocker arm
area
arm assembly
piston
pressure
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
EP04100732A
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English (en)
French (fr)
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EP1568859A1 (de
Inventor
Axel Berndorfer
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Delphi Technologies Inc
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Delphi Technologies Inc
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Filing date
Publication date
Application filed by Delphi Technologies Inc filed Critical Delphi Technologies Inc
Priority to DE602004013714T priority Critical patent/DE602004013714D1/de
Priority to AT04100732T priority patent/ATE395504T1/de
Priority to EP04100732A priority patent/EP1568859B1/de
Publication of EP1568859A1 publication Critical patent/EP1568859A1/de
Application granted granted Critical
Publication of EP1568859B1 publication Critical patent/EP1568859B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • 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
    • 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
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction

Definitions

  • the present invention generally relates to a rocker arm assembly for a valve train, in particular to a two-step finger follower type rocker arm assembly of a valve train.
  • Variable valve activation mechanisms for internal combustion engines are well known. It is known to be desirable to lower the lift, or even provide no lift at all, of one or more valves of a multiple-cylinder engine, especially intake valves, during periods of high engine load.
  • a conventional two-step finger follower type rocker arm assembly includes an elongate, rigid main rocker arm body.
  • This main rocker arm body has a first end for engaging a conventional hydraulic lash adjuster (HLA) as a pivot means, and has an interface means at an opposite, second end for engaging a valve stem of a valve to be actuated.
  • HLA hydraulic lash adjuster
  • the assembly further includes two lateral rocker arms that can be selectively coupled to the main rocker arm to provide switching between two assembly configurations so as obtain two different valve lift capabilities.
  • This coupling is typically achieved by means of a latch member mounted on the main rocker arm.
  • the latch member is moveable between a first, rest position, in which the lateral rocker arms are uncoupled, and a second position, in which the main rocker arm is coupled to the lateral rocker arms. In the first latch position, the valve lift is only due to the action of a main cam on the main rocker arm, whereas in the second position, the valve lift is due to the action of associated lateral cams on the lateral rocker arms.
  • a piston coupled to the latter is arranged in the main body on the socket side.
  • This piston is reciprocally arranged in a piston bore and defines therewith a hydraulic chamber, which is in communication with the socket via an oil feed channel. Actuation of the piston is achieved by increasing the oil pressure delivered by the HLA so as to move the piston against a return spring that biases the latch member in the uncoupled position.
  • rocker arm assemblies have a random trigger mechanism for actuation. That is, at a random point of the cam revolution, the command to change the valve lift is received from an ECM.
  • the latch member is then urged into its second position regardless of the position of the lateral rocker arms with respect to the main rocker arm. Often, the latch member is prevented from reaching the second position because the latch member hits another part of the assembly.
  • the switch to another valve lift is delayed, causing slight drivability and emission problems. More critically, partial switches are also possible, wherein the latch member only partially locks the lateral rocker arms to the main rocker arm such that, during the lift, the lateral rocker arms can free themselves from engagement with the main rocker arm, leading to high stress at the switching mechanism.
  • valve is let loose and either slams into its seat driven by the valve spring or slams back to the low lift profile.
  • the valve, valve seat, cam surfaces and cam contacting surfaces of the assembly can thereby be damaged.
  • the object of the present invention is to provide a rocker arm assembly having an improved switching capability. This object is achieved by a rocker arm assembly as claimed in claim 1.
  • a rocker arm assembly for variably activating a gas valve in an internal combustion engine has at least two configurations to vary its valve lift capability.
  • the rocker arm assembly comprises a main rocker arm body having a socket for engaging a pivot at a first end and having an interface means for engaging a valve stem at a second end.
  • the assembly further comprises a latch member associated with the main rocker arm body, the latch member being moveable between a first position to provide a first rocker arm assembly configuration and a second position to provide a second rocker arm assembly configuration.
  • the assembly also has latch actuating means comprising a piston reciprocally arranged in a piston bore and coupled to the latch member for moving the latch member from the first position to the second position, wherein the piston has a pressure surface defining with the piston bore a hydraulic chamber, the hydraulic chamber comprising at least one inlet for a pressurized hydraulic medium so as to move the piston under the action of hydraulic pressure, as shown for example in document US-5544626 A .
  • the assembly comprises a first feed channel arranged so as to fluidly connect a supply port to a first area of the pressure surface when the piston is in its first position and a second feed channel is arranged so as to fluidly connect a supply port to a second area of the pressure surface, the second area being larger than the first area.
  • the second feed channel is in fluid communication with a supply port only in a switching position of the main rocker arm body.
  • the pressurized hydraulic medium is at a first pressure or at a second pressure, wherein the first pressure is insufficient to displace the piston when acting on the first area and/or the second area; and the second pressure is insufficient to displace the piston when acting only on the first area, but sufficient to displace the piston when acting on the second area.
  • the rocker arm assembly can only be switched into its second rocker arm assembly configuration when the pressurized hydraulic medium is at the second pressure and the second feed channel is in fluid communication with a supply port.
  • the latch member can only be moved into its second position when the main rocker arm body is in the switching position, i.e. when the main rocker arm is in a particular position with respect to a lateral rocker arm. Safe switching of the latch member is thereby guaranteed and all disadvantages of mistimed switching, such as drivability and emission problems, high stress at the switching mechanism, wear and tear at the switching mechanism, damages to valve, valve seat, cam surfaces and cam contacting surfaces, are avoided.
  • the first area represents a minor portion of the piston pressure surface and the second area represents a comparatively predominant portion of the piston pressure surface.
  • the second area corresponds to the total area of the pressure surface, including the first area.
  • the first and second feed channels comprise a first and second feed port arranged in the socket of the main rocker arm body; and the pivot comprises a supply port communicating with the first and second feed ports for supplying pressurized hydraulic medium to the first and second feed channels. Pressurized hydraulic medium is thereby fed to the first or second feed channel through the pivot.
  • the supply port communicates with a first feed port of the first feed channel when the main rocker arm body is not in the switching position; and the supply port communicates with a second feed port of the second feed channel only when the main rocker arm body is in the switching position. Pressurized hydraulic medium is thereby fed to the first or second feed channel depending on the rotational position of the socket on the pivot. This is an easy, yet effective, way of ensuring that the hydraulic medium is applied to the second area of the pressure surface only when the main rocker arm body is in the switching position.
  • the supply port communicates with a first feed port of the first feed channel; and the supply port communicates with a second feed port of the second feed channel.
  • a control valve is arranged in the second feed channel for opening the second feed channel only when the main rocker arm body is in the switching position. This is an alternative way of ensuring that the hydraulic medium is applied to the second area of the pressure surface only when the main rocker arm body is in the switching position.
  • the first and second feed ports can be fused together to form a common feed port.
  • the control valve preferably comprises a plunger transversely arranged in the second feed channel, and biasing means for maintaining the valve in a closed position when the main rocker arm body is not in the switching position.
  • the rocker arm assembly preferably further comprises a configuration switch element moveably connected to the main rocker arm body.
  • the configuration switch element In the first rocker arm assembly configuration, the configuration switch element is freely moveable with respect to the main rocker arm body and the valve lift is defined by a first cam surface contacting a first cam contacting surface of the rocker arm assembly.
  • the configuration switch element In the second rocker arm assembly configuration, the configuration switch element is locked in position with respect to the main rocker arm body and the valve lift is defined by a second cam surface contacting a second cam contacting surface of the rocker arm assembly.
  • the configuration switch element is preferably a pair of lateral auxiliary rocker arm bodies, the main rocker arm body being sandwiched therebetween.
  • a main cam contacts the main rocker arm body and moves the valve according to a first valve lift configuration.
  • two lateral cams can enter into contact with the lateral auxiliary rocker arm bodies to move the valve according to a second valve lift configuration.
  • the pivot is preferably a hydraulic lash adjuster.
  • Fig.1 shows a rocker arm assembly 10 of a valve train of an internal combustion engine.
  • This rocker arm assembly 10 is of the so-called two-step finger follower type, so that the configuration of the rocker arm assembly 10 can be varied to provide two different valve lift capabilities.
  • a main rocker arm body 12 has a first end 14 having a spherical socket 16 for receiving a head 18 of a hydraulic lash adjuster HLA 20.
  • An opposite, second end 22 of the main rocker arm body 12 is provided with an actuate pad 24 for interfacing with and actuating a valve stem 26.
  • a first lateral rocker arm body 32 is provided and pivotably mounted on the main rocker arm body 12.
  • a second lateral rocker arm body (not shown) is, for symmetry reasons, provided on the other lateral side of the main rocker arm body 12.
  • Such a rocker arm assembly 10 cooperates with the camshaft (not shown), which has one main cam (not shown) for engaging a cam contacting surface 34 of the main rocker arm 12, as well as two lateral cams for engaging respective cam contacting surfaces 36 on the lateral rocker arm bodies 32.
  • the assembly 10 further includes a latch actuating means, generally indicated 40, in order to couple or uncouple the lateral rocker arm bodies 32 to the main rocker arm 12 so as to vary the configuration of the assembly 10 and thus the valve lift capability.
  • a latch actuating means generally indicated 40, in order to couple or uncouple the lateral rocker arm bodies 32 to the main rocker arm 12 so as to vary the configuration of the assembly 10 and thus the valve lift capability.
  • the latter comprises a piston 44 reciprocally mounted in a piston bore having a cylindrical lateral wall 46 and an end wall 48.
  • the piston 44 has a head with a pressure surface defining with the lateral and end walls 46, 48 of the piston bore a hydraulic chamber 50.
  • the pressure surface of the head of the piston 44 has a first area 52 and a second area 54, wherein the second area 54 is larger than the first area 52.
  • the first area 52 is in communication with a first feed channel 56 for feeding pressurized hydraulic medium, normally engine oil, to the first area 52.
  • the second area 54 is in communication with a second feed channel 58 for feeding pressurized hydraulic medium to the second area 54.
  • the first feed channel 56 leads to a first feed port 60 in the socket 16 and the second feed channel 58 leads to a second feed port 62 in the socket 16.
  • oil is fed from a supply port 64 arranged in the head 18 to one or both of the first and second feed ports 60,62 and hence to one or both of the first and second areas 52,54.
  • the piston 44 is coupled to a latch member 66 for coupling the lateral rocker arm bodies 32 to the main rocker arm body 12.
  • the latch actuating means 40 preferably comprises a spring 68 for pushing the piston 44 into a rest position as shown in Fig.1 . Only the part of the latch member 66, which is connected to the latch actuating means 40, is shown in the figures.
  • the latch member 66 can be any sort of mechanism capable of coupling the lateral rocker arm bodies 32 to the main rocker arm body 12, resp. of uncoupling the lateral rocker arm bodies 32 from the main rocker arm body 12.
  • the pressure of the oil being fed to the lash actuating means 40 is insufficient to move the piston 44 against the force of the spring 68, whether the oil is being fed to the first area 52 via the first feed channel or to the second area 54 via the second feed channel 58.
  • the piston 44 hence remains in its rest position as shown in Fig.1 .
  • the piston 44 In order to switch to the other assembly configuration, the piston 44 must be moved towards the left for engaging the lateral rocker arm bodies, and e.g. ultimately to the end position shown in Fig.3 .
  • the engine control module ECM
  • ECM engine control module
  • the pressure of the oil is increased to a level wherein it is still insufficient to move the piston 44 against the force of the spring 68 when the pressure is only applied to the first area 52 of the pressure surface of the piston 44.
  • the pressure is however sufficiently high to move the piston 44 against the force of the spring 68 when the pressure is applied to the second area 54 of the pressure surface of the piston 44.
  • the oil pressure is increased to a switching pressure.
  • the piston 44 however can only be moved if the switching pressure is applied to the second area 54, i.e. when the oil is fed through the second feed channel 58.
  • the second feed port 62 of the second feed channel 58 is arranged so that it is only in communication with the supply port 64 of the head 18 of the HLA 20, as shown in Fig.2 . This ensures that movement of the latch member 66 can only occur when the main rocker arm body 12 is in a switching position, i.e. in a position wherein the engagement of the lateral rocker arm bodies 32 with the main rocker arm body 12 is guaranteed. All problems associated with failed or partial engagements can thereby be avoided.
  • Fig.2 the main rocker arm body 12 is shown in the switching position and the supply port 64 is in communication with the second feed port 62 of the second feed channel 58.
  • the supply port 64 is also still in communication with the first feed port 60 of the first feed channel 56. This is however not necessary for the functioning of the invention, but provides an advantage in that the oil pressure can remain slightly lower as the pressure surface is bigger due to the fact that the first area is also pressurised by the oil.
  • the latch member 66 can engage the lateral rocker arm bodies 32 with the main rocker arm body 12 as shown in Fig.3 .
  • the cam continues to rotate and move the main rocker arm body 12 out of the switching position.
  • the lateral rocker arm bodies 32 now move in harmony with the main rocker arm body 12 and the second assembly configuration is achieved.
  • the valve activation is due to the action of the main cam on the cam contacting surface 34 of the main rocker arm body 12 and of the lateral cams on the cam contacting surfaces 36 of the lateral rocker arm bodies 32 and the valve lift is determined by the design of these elements.
  • the main rocker arm body 12 is again shown in the position as in Fig.1 and the supply port 64 is in communication with the first feed port 60 of the first feed channel 60 only. No more oil is fed through the second feed channel 58. However, as the oil is still maintained at switching pressure and is fed to the pressure surface via the first feed channel 56, oil at switching pressure still acts on the first and second areas 52,54 of the pressure surface of the head of the piston 44. The piston 44 is therefore maintained in its end position and the latch member 66 still maintains the main and lateral rocker arm bodies in coupled relationship. As long as the oil is maintained at the switching pressure, the force on the piston 44 is stronger than the force of the spring 68 and the main and lateral rocker arm bodies 12,32 remain in the coupled state.
  • FIG.4 An alternative embodiment for a rocker arm assembly according to the invention is shown in Fig.4 , wherein the first and second feed ports 60,62 of the previous embodiment, have been fused to a single common feed port 70.
  • the supply port 64 is in communication with the feed port 70 and oil is fed to the first and second feed channels 56,58.
  • a control valve 72 is arranged in the second feed channel 58. The control valve 72 is normally in a closed position, preventing oil from flowing through the second feed channel 58. Only when the main rocker arm body 12 is in a particular switching position, the control valve is allowed to open the second feed channel 58.
  • the control valve 72 and its functioning can be more clearly described by referring to Fig.5 and Fig.6 .
  • the control valve 72 comprises a plunger 74 reciprocally arranged in a bore 76.
  • the bore 76 is arranged perpendicularly to and through the second feed channel 58.
  • the plunger 74 is dimensioned so as to prevent any flow of oil from the common feed port 70 to the piston 44 when the plunger 74 is in a first position as shown in Fig.5 .
  • a spring 78 is associated with the plunger 78 and acts on one end of the plunger 74, so as to push the other end of the plunger 74 against a profiled surface 80 of the lateral rocker arm body 32.

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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)

Claims (11)

  1. Kipphebelbaugruppe (10) zum variablen Betätigen eines Gasventils in einem Motor mit innerer Verbrennung, wobei die Kipphebelbaugruppe mindestens zwei Konfigurationen aufweit, um ihre Ventilhubleistung zu variieren, wobei die Kipphebelbaugruppe umfasst:
    einen Hauptkipphebelkörper (12), der eine Pfanne (16) zum Eingreifen mit einem Drehzapfen (18) an einem ersten Ende und ein Kopplungsmittel (24) zum Eingreifen mit einem Ventilschaft (26) an einem zweiten Ende aufweist;
    ein Verriegelungsglied (66), das dem Hauptkipphebelkörper (12) zugeordnet ist, wobei das Verriegelungsglied (66) zwischen einer ersten Position, um eine erste Kipphebelbaugruppenkonfiguration vorzusehen, und einer zweiten Position, um eine zweite Kipphebelbaugruppenkonfiguration vorzusehen, bewegbar ist;
    ein Verriegelungsbetätigungsmittel (40), das einen Kolben (44) umfasst, der in einer Kolbenbohrung (46) hin und her bewegbar angeordnet ist und mit dem Verriegelungsglied (66) gekoppelt ist, zum Bewegen des Verriegelungsglieds (66) aus der ersten Position in die zweite Position, wobei der Kolben (44) eine Druckoberfläche aufweist, die mit der Kolbenbohrung eine Hydraulikkammer definiert, wobei die Hydraulikkammer mindestens einen Einlass für ein mit Druck beaufschlagtes Hydraulikmedium umfasst, um den Kolben (44) unter der Einwirkung von hydraulischem Druck zu bewegen;
    dadurch gekennzeichnet, dass
    ein erster Zulaufkanal (56) angeordnet ist, um eine Zufuhröffnung (60) mit einer ersten Fläche der Druckoberfläche in Fluidverbindung zu bringen, wenn sich der Kolben (44) in seiner ersten Position befindet;
    ein zweiter Zulaufkanal (58) angeordnet ist, um eine Zufuhröffnung (62) mit einer zweiten Fläche der Druckoberfläche in Fluidverbindung zu bringen wobei die zweite Fläche (54) größer als die erste Flache (52) ist; und
    der zweite Zulaufkanal (58) nur in einer Schaltposition des Hauptkipphebelkörpers (12) mit einer Zufuhröffnung (62) in Fluidkommunikation steht;
    das mit Druck beaufschlagte Hydraulikmedium auf einem ersten Druck oder auf einem zweiten Druck ist;
    der erste Druck nicht ausreichend ist, um den Kolben (44) zu verschieben, wenn er auf die erste Fläche (52) und/oder die zweite Fläche (54) einwirkt;
    der zweite Druck nicht ausreichend ist, um den Kolben (44) zu verschieben, wenn er nur auf die erste Fläche (52) einwirkt, jedoch ausreichend ist, um den Kolben (44) zu verschieben, wenn er auf die zweite Fläche (54) einwirkt.
  2. Kipphebelbaugruppe (10) nach Anspruch 1, wobei die erste Fläche (52) einen unwesentlichen Abschnitt der Druckoberfläche darstellt und die zweite Fläche (54) einen überwiegenden Abschnitt der Druckoberfläche darstellt.
  3. Kipphebelbaugruppe (10) nach Anspruch 1, wobei die zweite Fläche (54) der Gesamtfläche der Druckoberfläche entspricht, einschließlich der ersten Fläche (52).
  4. Kipphebelbaugruppe (10) nach einem beliebigen der vorhergehenden Ansprüche,
    wobei der erste (56) und der zweite Zulaufkanal (58) eine erste (60) und eine zweite Zulauföffnung (62) umfassen, die in der Pfanne (16) des Hauptkipphebelkörpers (12) angeordnet sind; und
    wobei der Drehzapfen (18) eine Zufuhröffnung (64) umfasst, die mit der ersten (60) und der zweiten Zulauföffnung (62) zum Zuführen von mit Druck beaufschlagtem Hydraulikmedium zu dem ersten (56) und dem zweiten Zulaufkanal (58) kommuniziert.
  5. Kipphebelbaugruppe (10) nach einem beliebigen der Ansprüche 1 bis 4,
    wobei die Zufuhröffnung (64) mit einer ersten Zulauföffnung (60) des ersten Zulaufkanals (56) kommuniziert, wenn sich der Hauptkipphebelkörper (12) nicht in der Schaltposition befindet; und
    wobei die Zufuhröffnung (64) nur dann mit einer zweiten Zulauföffnung (62) des zweiten Zulaufkanals (58) kommuniziert, wenn sich der Hauptkipphebelkörper in der Schaltposition befindet.
  6. Kipphebelbaugruppe (10) nach einem beliebigen der Ansprüche 1 bis 4,
    wobei die Zufuhröffnung (64) mit einer ersten Zulauföffnung (60) des ersten Zulaufkanals (56) kommuniziert; und
    wobei die Zufuhröffnung mit einer zweiten Zulauföffnung (62) des zweiten Zulaufkanals (58) kommuniziert;
    wobei der zweite Zulaufkanal (58) ein Regelventil (72) zum Öffnen des zweiten Zulaufkanals (58) nur dann, wenn sich der Hauptkipphebelkörper (12) in der Schaltposition befindet, umfasst.
  7. Kipphebelbaugruppe (10) nach Anspruch 6, wobei die erste und die zweite Zulauföffnung miteinander vereinigt sind, um eine gemeinsame Zulauföffnung (70) zu bilden.
  8. Kipphebelbaugruppe nach Anspruch 6 oder 7, wobei das Regelventil (72) einen Ventilkolben (74) umfasst, der in dem zweiten Zulaufkanal (58) quer angeordnet ist, und Vorspannmittel (78) zum Halten des Regelventils (72) in einer geschlossenen Position, wenn sich der Hauptkipphebelkörper (12) nicht in der Schaltposition befindet.
  9. Kipphebelbaugruppe (10) nach einem beliebigen der vorhergehenden Ansprüche, ferner umfassend:
    ein Konfigurationsumschaltelement, das mit dem Hauptkipphebelkörper (12) bewegbar verbunden ist, wobei:
    - in der ersten Kipphebelbaugruppenkonfiguration das Konfigurationsumschaltelement in Bezug auf den Hauptkipphebelkörper frei bewegbar ist und der Ventilhub durch eine erste Nockenoberfläche definiert wird, die eine erste nockenberührende Oberfläche der Kipphebelbaugruppe berührt;
    - in der zweiten Kipphebelbaugruppenkonfiguration das Konfigurationsumschaltelement in Bezug auf den Hauptkipphebelkörper in seiner Position verriegelt ist und der Ventilhub durch eine zweite Nockenoberfläche definiert wird, die eine zweite nockenberührende Oberfläche der Kipphebeibaugruppe berührt
  10. Kipphebelbaugruppe (10) nach Anspruch 9, wobei das Konfigurationsumschaltelement ein Paar von seitlichen Kipphebelkörpern (32) ist, zwischen denen der Hauptkipphebelkörper (12) angeordnet ist.
  11. Kipphebelbaugruppe (10) nach einem beliebigen der vorhergehenden Ansprüche, wobei der Drehzapfen ein Hydrostößel (20) ist.
EP04100732A 2004-02-25 2004-02-25 Kipphebeleinrichtung für Ventilsteuerung Expired - Lifetime EP1568859B1 (de)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE602004013714T DE602004013714D1 (de) 2004-02-25 2004-02-25 Kipphebeleinrichtung für Ventilsteuerung
AT04100732T ATE395504T1 (de) 2004-02-25 2004-02-25 Kipphebeleinrichtung für ventilsteuerung
EP04100732A EP1568859B1 (de) 2004-02-25 2004-02-25 Kipphebeleinrichtung für Ventilsteuerung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04100732A EP1568859B1 (de) 2004-02-25 2004-02-25 Kipphebeleinrichtung für Ventilsteuerung

Publications (2)

Publication Number Publication Date
EP1568859A1 EP1568859A1 (de) 2005-08-31
EP1568859B1 true EP1568859B1 (de) 2008-05-14

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EP04100732A Expired - Lifetime EP1568859B1 (de) 2004-02-25 2004-02-25 Kipphebeleinrichtung für Ventilsteuerung

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EP (1) EP1568859B1 (de)
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DE (1) DE602004013714D1 (de)

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US7278384B2 (en) 2005-09-30 2007-10-09 Delphi Technologies, Inc. Timing mechanism for a switchable two-step roller finger follower
US20080035085A1 (en) * 2006-08-14 2008-02-14 Hendriksma Nick J Method and apparatus for controlling a switchable cam follower

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US5544626A (en) * 1995-03-09 1996-08-13 Ford Motor Company Finger follower rocker arm with engine valve deactivator
DE19510106A1 (de) * 1995-03-20 1996-09-26 Bayerische Motoren Werke Ag Schwinghebel-Anordnung

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