EP0636206B1 - Valve actuating mechanism for an internal combustion engine - Google Patents

Valve actuating mechanism for an internal combustion engine Download PDF

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Publication number
EP0636206B1
EP0636206B1 EP93908895A EP93908895A EP0636206B1 EP 0636206 B1 EP0636206 B1 EP 0636206B1 EP 93908895 A EP93908895 A EP 93908895A EP 93908895 A EP93908895 A EP 93908895A EP 0636206 B1 EP0636206 B1 EP 0636206B1
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EP
European Patent Office
Prior art keywords
valve
pistons
levers
valve levers
speed range
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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
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EP93908895A
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German (de)
French (fr)
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EP0636206A1 (en
Inventor
Michael Paul
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Audi AG
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Audi AG
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Publication of EP0636206A1 publication Critical patent/EP0636206A1/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
    • F01L13/0015—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
    • 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
    • F01L1/267—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 with means for varying the timing or the lift of the valves

Definitions

  • the invention relates to a valve actuation mechanism for an internal combustion engine according to the preamble of claim 1.
  • the pistons are displaced such that they penetrate the parting planes, as a result of which the second rocker arms are connected to the first rocker arms and the valves are actuated by the second rocker arms in accordance with the cam contour of the cams assigned to the second rocker arms.
  • This enables different valve strokes and different opening times for the valves in the lower and in the upper speed range.
  • the disadvantage of this known construction is that in the lower speed range the pistons with their end faces constantly slide on each other and that a very high precision is required in the manufacture of the pistons and the bores.
  • the invention has for its object to provide a valve actuation mechanism of the generic type, in which the wear is reduced and the manufacture is simplified.
  • the pistons are retracted by their springs in the lower speed range, so that there is no contact with the second rocker arms.
  • the bores and the pistons in the first rocker arms preferably have a circular cross section.
  • the end sections of the pistons which interact with the underside of the crossmember in the upper speed range, can have a flat surface, as a result of which flat contact between the pistons and the crossmember is achieved and the surface pressure is correspondingly reduced.
  • valve train for three intake valves E is shown. Each valve E is acted upon by a spring 1 in the closing direction.
  • the valves are operated by their own cams 2, 3 and 4 of a camshaft 5 via first rocker arms 6, which are pivotably mounted on a common fixed axis 7.
  • the cams 2, 3 and 4 preferably have different cam profiles in order to achieve a different valve lift, a different opening duration and / or different control times for the individual intake valves and to create optimal conditions in the lower and middle speed range of the internal combustion engine.
  • second cams 8 are provided on the camshaft 5 with an identical cam profile, which is designed for the conditions in the upper speed range of the internal combustion engine, that is, for example, produces a larger valve lift and a longer opening time.
  • second cams 8 interact second rocker arms 9, which can be coupled in the upper speed range with the first rocker arms 6, so that in this speed range the valves E are operated according to the contour of the cams 8.
  • the free ends of the second rocker arms 9 are connected to one another by a traverse 10 which runs in front of and at a short distance from the free ends of the first rocker arms 6.
  • first rocker arms 6 are provided for the pivot axis 7 radial bores 11, in each of which a piston 12 is arranged, which is displaceable between a first, inner position and a second outer position, in which the piston protrudes from its rocker arm 6.
  • the pistons 12 In this second position, shown in FIG. 1, the pistons 12 cooperate with the flat underside 10a of the cross member 10, so that the second rocker arms 9 can actuate the valves E via the first rocker arms 6 in accordance with the contour of the cams 8.
  • the displacement of the pistons 12 to the outside takes place with the aid of a pressure medium which is supplied through a channel 14 in the axis 7, which is connected to the bores 11.
  • the pistons 12 are returned into their bores 11 by a spring 13, so that the second rocker arms 9 can swing freely and the actuation of the valves by the first rocker arms 6 in accordance with the contour of the cams 2, 3 and 4 he follows.
  • the spring 13 is supported on the one hand on an insert 15 fixed in the bore 11 and on the other hand on the end of a sleeve 16 which is fastened to the piston 12 and extends through the insert 15.
  • Each rocker arm 6 or 9 has a sliding surface 17 with which it rests on its cam 2, 3, 4 or 8.
  • the second rocker arms 9 are held in contact with their cams by a spring 18.
  • the spring 18 is arranged on a spark plug dome 19 and is supported on the one hand on a stationary spring plate 20 and on the other hand on a displaceable spring plate 21, which cooperates with extensions 22 of the second rocker arms 9, which partially encompass the spark plug dome.
  • the end sections of the pistons 12 are provided with flat surfaces 23 on which the cross member 10 with its flat underside 10a rests when the pistons 12 are in the pushed-out position shown.
  • the surface pressure between the cross member 10 and the piston 13 is thus reduced.
  • an anti-rotation device is provided in the form of a pin 24 which is inserted in the rocker arms 6 and with its lower end face on the flat surface 23 of the piston rests. In the pushed-out position, the shoulder 25 created by the flat surface 23 bears against the pin 24, as a result of which the outward movement of the piston 12 is limited.

Abstract

A valve actuating mechanism for the inlet valves (E) of a cylinder of an internal combustion engine has first drag levers (6), each operating an inlet valve (E) and actuated by a cam (2, 3 or 4), for a lower rotation speed range, and second drag levers (9) which are arranged between adjacent first drag levers (6) and actuated by their own identical cams (8) for the upper rotation speed range. The second drag levers (9) are interconnected by a cross-member (10). The first drag levers (6) contain radially movable pistons (12) which are pushed outwards in the upper rotation speed range by a pressurized medium and on which the cross-member (10) of the second drag levers (9) can be supported. The valves (E) are thus actuated by the second drag levers (9) according to the contour of the cams (8).

Description

Die Erfindung bezieht sich auf einen Ventilbetätigungsmechanismus für eine Brennkraftmaschine entsprechend dem Oberbegriff des Anspruchs 1.The invention relates to a valve actuation mechanism for an internal combustion engine according to the preamble of claim 1.

Bei einem bekannten Ventilbetätigungsmechanismus dieser Art (GB-A-2199894) erfolgt die Verbindung zwischen den ersten und zweiten Schlepphebeln im oberen Drehzahlbereich mit Hilfe von durch Öldruck verschiebbaren Kolben, die in radial zur Schwenkachse der Schlepphebel angeordneten, in den Schlepphebeln vorgesehenen Bohrungen angeordnet sind und mit ihren Stirnflächen aneinanderstoßen. Die Bohrungen fluchten miteinander, wenn die Schlepphebel auf den Grundkreisen ihrer Nocken liegen. Im unteren Drehzahlbereich, in welchem die Ventile von den den ersten Schlepphebeln zugeordneten Nocken betätigt werden sollen, liegen die aneinander anstoßenden Stirnflächen der Kolben in den Teilungsebenen zwischen den Schlepphebeln, so daß die Ventile nur von den ersten Schlepphebeln betätigt werden und die zweiten Schlepphebel frei schwingen können. Im oberen Drehzahlbereich werden die Kolben derart verschoben, daß sie die Teilungsebenen durchdringen, wodurch die zweiten Schlepphebeln mit den ersten Schlepphebeln verbunden werden und die Ventile von den zweiten Schlepphebeln entsprechend der Nockenkontur der den zweiten Schlepphebeln zugeordneten Nocken betätigt werden. Damit lassen sich unterschiedliche Ventilhübe und unterschiedliche Öffnungszeiten für die Ventile im unteren und im oberen Drehzahlbereich verwirklichen. Nachteilig ist bei dieser bekannten Konstruktion, daß im unteren Drehzahlbereich die Kolben mit ihren Stirnflächen ständig aufeinander gleiten und daß eine sehr hohe Präzission bei der Herstellung der Kolben und der Bohrungen erforderlich ist.In a known valve actuation mechanism of this type (GB-A-2199894), the connection between the first and second rocker arms in the upper speed range takes place with the aid of pistons which can be displaced by oil pressure and which are arranged in bores provided in the rocker arms and arranged radially to the pivot axis of the rocker arms and butt with their faces. The holes are aligned when the rocker arms are on the base circles of their cams. In the lower speed range in which the valves are to be actuated by the cams assigned to the first rocker arms, the abutting end faces of the pistons lie in the parting planes between the rocker arms, so that the valves are actuated only by the first rocker arms and the second rocker arms swing freely can. In the upper speed range, the pistons are displaced such that they penetrate the parting planes, as a result of which the second rocker arms are connected to the first rocker arms and the valves are actuated by the second rocker arms in accordance with the cam contour of the cams assigned to the second rocker arms. This enables different valve strokes and different opening times for the valves in the lower and in the upper speed range. The disadvantage of this known construction is that in the lower speed range the pistons with their end faces constantly slide on each other and that a very high precision is required in the manufacture of the pistons and the bores.

Der Erfindung liegt die Aufgabe zugrunde, einen Ventilbetätigungsmechanismus der gattungsgemäßen Art zu schaffen, bei dem der Verschleiß verringert und die Herstellung vereinfacht ist.The invention has for its object to provide a valve actuation mechanism of the generic type, in which the wear is reduced and the manufacture is simplified.

Diese Aufgabe wird erfindungsgemäß durch die im Kennzeichen des Anspruchs 1 angegebenen Merkmale gelöst.This object is achieved by the features specified in the characterizing part of claim 1.

Bei dem erfindungsgemäßen Vorschlag sind die Kolben im unteren Drehzahlbereich durch ihre Federn zurückgezogen, so daß keine Berührung mit den zweiten Schlepphebeln stattfindet. Dadurch, daß in den zweiten Schlepphebeln keine Bohrungen vorgesehen sind, die mit den Bohrungen in den ersten Schlepphebeln fluchten müssen, wenn die Ventile von den zweiten Schlepphebeln betätigt werden sollen, ist die Fertigung wesentlich vereinfacht. Es ist lediglich eine plane Bearbeitung der Unterseite der Traverse erforderlich.In the proposal according to the invention, the pistons are retracted by their springs in the lower speed range, so that there is no contact with the second rocker arms. The fact that no holes are provided in the second rocker arms which must be aligned with the holes in the first rocker arms when the valves are to be actuated by the second rocker arms, manufacturing is considerably simplified. Only a flat machining of the underside of the traverse is required.

Die Bohrungen und die Kolben in den ersten Schlepphebeln haben aus Fertigungsgründen vorzugsweise einen kreisförmigen Querschnitt. Dabei können die Endabschnitte der Kolben, die im oberen Drehzahlbereich mit der Unterseite der Traverse zusammenwirken, eine Planfläche aufweisen, wodurch eine flächige Berührung zwischen den Kolben und der Traverse erreicht und die Flächenpressung entsprechend reduziert wird. Um sicherzustellen, daß die Planflächen der Endabschnitte stets parallel zu der Unterseite der Traverse liegen, ist es zweckmäßig, eine Verdrehsicherung für den Kolben vorzusehen, die gleichzeitig die Auswärtsbewegung des Kolbens begrenzen kann.For manufacturing reasons, the bores and the pistons in the first rocker arms preferably have a circular cross section. The end sections of the pistons, which interact with the underside of the crossmember in the upper speed range, can have a flat surface, as a result of which flat contact between the pistons and the crossmember is achieved and the surface pressure is correspondingly reduced. To ensure that the flat surfaces of the end sections are always parallel to the underside of the crossmember, it is expedient to provide an anti-rotation device for the piston, which can simultaneously limit the outward movement of the piston.

Ein Ausführungsbeispiel der Erfindung wird im folgenden unter Bezugnahme auf die Zeichnungen beschrieben. Es zeigt:

Fig. 1
einen Ventiltrieb mit einem erfindungsgemäßen Ventilbetätigungsmechanismus für drei Einlaßventile im senkrechten Schnitt entlang Linie 1-1 in Fig. 2, und
Fig. 2
eine Ansicht in Richtung des Pfeils 2 in Fig. 1.
An embodiment of the invention is described below with reference to the drawings. It shows:
Fig. 1
a valve train with a valve actuation mechanism according to the invention for three intake valves in vertical section along line 1-1 in Fig. 2, and
Fig. 2
a view in the direction of arrow 2 in Fig. 1st

In den Zeichnungen ist ein Ventiltrieb für drei Einlaßventile E dargestellt. Jedes Ventil E ist im Schließsinn von einer Feder 1 beaufschlagt. Die Ventile werden von eigenen Nocken 2, 3 und 4 einer Nockenwelle 5 über erste Schlepphebel 6 betätigt, die auf einer gemeinsamen ortsfesten Achse 7 schwenkbar gelagert sind. Die Nocken 2, 3 und 4 haben vorzugsweise unterschiedliche Nockenprofile, um für die einzelnen Einlaßventile einen unterschiedlichen Ventilhub, eine unterschiedliche Öffnungsdauer und/oder unterschiedliche Steuerzeiten zu erreichen und im unteren und mittleren Drehzahlbereich der Brennkraftmaschine optimale Voraussetzungen zu schaffen. Zwischen benachbarten Nocken 2, 3 und 4 sind auf der Nockenwelle 5 zweite Nocken 8 mit identischem Nockenprofil vorgesehen, das für die Verhältnisse im oberen Drehzahlbereich der Brennkraftmaschine ausgelegt ist, also beispielsweise einem größeren Ventilhub und eine längere Öffnungsdauer erzeugt. Mit den zweiten Nocken 8 wirken zweite Schlepphebel 9 zusammen, die im oberen Drehzahlbereich mit den ersten Schlepphebeln 6 gekoppelt werden können, so daß in diesem Drehzahlbereich die Ventile E entsprechend der Kontur der Nocken 8 betätigt werden. Die freien Enden der zweiten Schlepphebel 9 sind durch eine Traverse 10 miteinander verbunden, die vor und in geringem Abstand von den freien Enden der ersten Schlepphebel 6 verläuft. In den ersten Schlepphebeln 6 sind zur Schwenkachse 7 radiale Bohrungen 11 vorgesehen, in denen jeweils ein Kolben 12 angeordnet ist, der zwischen einer ersten, inneren Stellung und einer zweiten äußeren Stellung verschiebbar ist, in welcher der Kolben von seinem Schlepphebel 6 vorsteht. In dieser zweiten, in Fig. 1 dargestellten Stellung wirken die Kolben 12 mit der planen Unterseite 10a der Traverse 10 zusammen, so daß die zweiten Schlepphebeln 9 die Ventile E über die ersten Schlepphebel 6 entsprechend der Kontur der Nocken 8 betätigen können. Die Verschiebung der Kolben 12 nach außen erfolgt mit Hilfe eines Druckmittels, das durch einen Kanal 14 in der Achse 7 zugeführt wird, der mit den Bohrungen 11 in Verbindung steht. Wird die Druckmittelzufuhr unterbrochen, so werden die Kolben 12 durch eine Feder 13 in ihre Bohrungen 11 zurückgeführt, so daß die zweiten Schlepphebel 9 frei schwingen können und die Betätigung der Ventile durch die ersten Schlepphebel 6 entsprechend der Kontur der Nocken 2, 3 bzw. 4 erfolgt. Die Feder 13 stützt sich einerseits an einem in der Bohrung 11 fixierten Einsatz 15 und andererseits am Ende einer Hülse 16 ab, die am Kolben 12 befestigt ist und sich durch den Einsatz 15 hindurch erstreckt.In the drawings, a valve train for three intake valves E is shown. Each valve E is acted upon by a spring 1 in the closing direction. The valves are operated by their own cams 2, 3 and 4 of a camshaft 5 via first rocker arms 6, which are pivotably mounted on a common fixed axis 7. The cams 2, 3 and 4 preferably have different cam profiles in order to achieve a different valve lift, a different opening duration and / or different control times for the individual intake valves and to create optimal conditions in the lower and middle speed range of the internal combustion engine. Between adjacent cams 2, 3 and 4, second cams 8 are provided on the camshaft 5 with an identical cam profile, which is designed for the conditions in the upper speed range of the internal combustion engine, that is, for example, produces a larger valve lift and a longer opening time. With the second cams 8 interact second rocker arms 9, which can be coupled in the upper speed range with the first rocker arms 6, so that in this speed range the valves E are operated according to the contour of the cams 8. The free ends of the second rocker arms 9 are connected to one another by a traverse 10 which runs in front of and at a short distance from the free ends of the first rocker arms 6. In the first rocker arms 6 are provided for the pivot axis 7 radial bores 11, in each of which a piston 12 is arranged, which is displaceable between a first, inner position and a second outer position, in which the piston protrudes from its rocker arm 6. In this second position, shown in FIG. 1, the pistons 12 cooperate with the flat underside 10a of the cross member 10, so that the second rocker arms 9 can actuate the valves E via the first rocker arms 6 in accordance with the contour of the cams 8. The displacement of the pistons 12 to the outside takes place with the aid of a pressure medium which is supplied through a channel 14 in the axis 7, which is connected to the bores 11. If the pressure medium supply is interrupted, the pistons 12 are returned into their bores 11 by a spring 13, so that the second rocker arms 9 can swing freely and the actuation of the valves by the first rocker arms 6 in accordance with the contour of the cams 2, 3 and 4 he follows. The spring 13 is supported on the one hand on an insert 15 fixed in the bore 11 and on the other hand on the end of a sleeve 16 which is fastened to the piston 12 and extends through the insert 15.

Jeder Schlepphebel 6 bzw. 9 weist eine Gleitfläche 17 auf, mit welcher er an seinem Nocken 2, 3, 4 bzw. 8 anliegt. Die zweiten Schlepphebel 9 werden durch eine Feder 18 in Anlage an ihren Nocken gehalten. Die Feder 18 ist im Ausführungsbeispiel auf einem Zündkerzendom 19 angeordnet und stützt sich einerseits an einem ortsfesten Federteller 20 und andererseits an einem verschiebbaren Federteller 21 ab, der mit Fortsätzen 22 der zweiten Schlepphebel 9 zusammenwirkt, die den Zündkerzendom teilweise umgreifen.Each rocker arm 6 or 9 has a sliding surface 17 with which it rests on its cam 2, 3, 4 or 8. The second rocker arms 9 are held in contact with their cams by a spring 18. In the exemplary embodiment, the spring 18 is arranged on a spark plug dome 19 and is supported on the one hand on a stationary spring plate 20 and on the other hand on a displaceable spring plate 21, which cooperates with extensions 22 of the second rocker arms 9, which partially encompass the spark plug dome.

Die Endabschnitte der Kolben 12 sind mit Planflächen 23 versehen, an denen die Traverse 10 mit ihrer planen Unterseite 10a anliegt, wenn sich die Kolben 12 in der dargestellten herausgeschobenen Stellung befinden. Damit wird die Flächenpressung zwischen der Traverse 10 und den Kolben 13 verringert. Um ein Verdrehen der Kolben 13 zu vermeiden und zu gewährleisten, daß die Planfläche 23 stets parallel zu der Unterseite 10a der Traverse 10 ist, ist eine Verdrehsicherung in Form eines Stiftes 24 vorgesehen, der in den Schlepphebeln 6 eingesetzt ist und mit seiner unteren Stirnseite an der Planfläche 23 des Kolbens anliegt. In der herausgeschobenen Stellung liegt die durch die Planfläche 23 entstehende Schulter 25 an dem Stift 24 an, wodurch die Auswärtsbewegung des Kolbens 12 begrenzt ist.The end sections of the pistons 12 are provided with flat surfaces 23 on which the cross member 10 with its flat underside 10a rests when the pistons 12 are in the pushed-out position shown. The surface pressure between the cross member 10 and the piston 13 is thus reduced. In order to prevent the pistons 13 from rotating and to ensure that the flat surface 23 is always parallel to the underside 10a of the cross member 10, an anti-rotation device is provided in the form of a pin 24 which is inserted in the rocker arms 6 and with its lower end face on the flat surface 23 of the piston rests. In the pushed-out position, the shoulder 25 created by the flat surface 23 bears against the pin 24, as a result of which the outward movement of the piston 12 is limited.

Claims (4)

  1. Valve actuating mechanism for an internal combustion engine, comprising
    - at least two intake valves (E) to each cylinder,
    - first valve levers (6) which are adapted to swivel about a common shaft (7) and in each case cooperate with an intake valve (E) and their own cam (2, 3 and 4, respectively) on a camshaft (5) for a first engine speed range,
    - second valve levers (9) which are adapted to swivel about the common shaft (7) and cooperate with their own cams (8) for a second engine speed range,
    - spring elements (18) which hold the second valve levers (9) in contact against their cams (8), and
    - pistons (12) for coupling the first valve levers (6) with the second valve levers (9) in the second engine speed range, being provided in bores (11) which extend radially to the swivelling shaft (7) and being adapted to be displaced outwards by oil pressure against the force of a spring (13),
    characterised in that
    - the pistons (12) are arranged in bores (11) in the first valve levers (6),
    - the second valve levers (9) are in each case arranged between two neighbouring first valve levers (6) and cooperate with identical cams (8),
    - the free ends of the second valve levers (9) are connected to one another by a cross member (10) situated in front of and a short distance from the free ends of the first valve levers (6), and
    - the cross member (10) features a plane lower face (10a) with which the pistons (12) cooperate when they are displaced outwards.
  2. Valve actuating mechanism according to claim 1, characterised in that the pistons (12) are circular in cross-section and their end portions are provided with a plane surface (23) which cooperates with the lower face (10a) of the cross member (10) when the pistons are displaced outwards.
  3. Valve actuating mechanism according to claim 2, characterised in that an anti-torsion device (24) is provided for the pistons (12) and preferably at the same time limits the outward movement of the pistons.
  4. Valve actuating mechanism according to any of claims 1 to 3, characterised in that in the shaft (7) for the valve levers (6, 9) there is provided an oil feeder duct (14) which communicates with the bores (11) in the first valve levers (6).
EP93908895A 1992-04-16 1993-04-02 Valve actuating mechanism for an internal combustion engine Expired - Lifetime EP0636206B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4212844A DE4212844A1 (en) 1992-04-16 1992-04-16 Valve actuation mechanism for an internal combustion engine
DE4212844 1992-04-16
PCT/EP1993/000822 WO1993021427A1 (en) 1992-04-16 1993-04-02 Valve actuating mechanism for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP0636206A1 EP0636206A1 (en) 1995-02-01
EP0636206B1 true EP0636206B1 (en) 1996-07-17

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EP93908895A Expired - Lifetime EP0636206B1 (en) 1992-04-16 1993-04-02 Valve actuating mechanism for an internal combustion engine

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US (1) US5463988A (en)
EP (1) EP0636206B1 (en)
JP (1) JPH07505462A (en)
DE (2) DE4212844A1 (en)
WO (1) WO1993021427A1 (en)

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DE59303266D1 (en) 1996-08-22
WO1993021427A1 (en) 1993-10-28
EP0636206A1 (en) 1995-02-01
DE4212844A1 (en) 1993-10-21
JPH07505462A (en) 1995-06-15
US5463988A (en) 1995-11-07

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