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EP0644318A1 - Variable valve drive - Google Patents

Variable valve drive Download PDF

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Publication number
EP0644318A1
EP0644318A1 EP94112492A EP94112492A EP0644318A1 EP 0644318 A1 EP0644318 A1 EP 0644318A1 EP 94112492 A EP94112492 A EP 94112492A EP 94112492 A EP94112492 A EP 94112492A EP 0644318 A1 EP0644318 A1 EP 0644318A1
Authority
EP
European Patent Office
Prior art keywords
camshaft
variable valve
valve control
control according
cams
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.)
Withdrawn
Application number
EP94112492A
Other languages
German (de)
French (fr)
Inventor
Peter Schmid
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
Original Assignee
Dr Ing HCF Porsche AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Dr Ing HCF Porsche AG filed Critical Dr Ing HCF Porsche AG
Publication of EP0644318A1 publication Critical patent/EP0644318A1/en
Withdrawn legal-status Critical Current

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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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a variable valve control according to the preamble of claim 1.
  • variable valve controls not only can raw HC emissions be influenced favorably, but NO x emissions can also be reduced. They can also improve fuel consumption, stable idling, torque and performance of an internal combustion engine.
  • valve overlaps - intake and exhaust valves - are changed such that there is a relatively small overlap at low speeds and a relatively large overlap at higher speeds.
  • variable valve control with inlet and outlet cams which can be rotated relative to one another and which can be implemented without problems and is distinguished by good function.
  • the actuator with its drivers which engage in the groove of the inlet cam is not only structurally easy to implement but also reliable and highly effective with respect to the rotation function of the inlet cam.
  • Both the actuator and the camshaft are simple in construction, the latter being a so-called built camshaft can be fixed on the outlet cams, bearing bushes or the like and the inlet cams are rotatably mounted.
  • the actuating device comprises a hydraulic device and an electromagnet, is arranged on one end of the camshaft in a spatially advantageous manner and can optionally be constructed as a module that can be supplied, which can be used, for example, as a variant compared to a camshaft with fixed inlet and outlet cams for engines of the same construction but with different performance profiles .
  • this type of camshaft adjustment is suitable for so-called single-camshaft internal combustion engines, in which the intake and exhaust cams are arranged on a common shaft.
  • the camshaft 1 is arranged in a camshaft housing 2, which limits the combustion chambers of cylinders or a cylinder head of a multi-cylinder internal combustion engine.
  • the bearing journal 3 is made in one piece with the camshaft 1; the bearing pins 4, 5 and 6 are made separately from it. It is therefore a camshaft composed of several components, for which the term built camshaft is also used. In addition, are arranged on the camshaft 1: inlet cams 11, 12, 13 and outlet cams 14, 15, 16, and the bearing pins 4 and 5 are part of the bearing bushes 17, 18 surrounding the camshaft 1.
  • the camshaft 1 is on its outer peripheral surface 19 provided with a toothing 20 extending in the axial direction BB, on which the outlet cams 14, 15, 16, the bearing bushes 17, 18 and the bearing 6, which delimits an end face 21 of the camshaft 1, are rotatably fixed with a corresponding design.
  • a closing element 23 is inserted into a through bore 24 of the camshaft 1.
  • an actuator 26 belonging to a control device 25, which is axially movable - direction BB - and has a tubular configuration.
  • the actuator 26 has pins 27, 28, 29 designed as drivers which penetrate slot-like guide openings (FIG. 3) 30, 31, 32 in the camshaft 1 and with grooves 33, 34, 35 of control guides 36, 37, 38 of the inlet cams 11, 12, 13 work together.
  • the control guides 36, 37, 38 are positioned obliquely to a central longitudinal plane CC of the camshaft 1 (FIG. 4), as a result of which longitudinal movements - direction BB - of the actuator 26 in the region of the length FO L of the guide openings 30, 31, 32 to rotary movements - angle ⁇ (Fig. 2) - the inlet cam 11, 12, 13 lead.
  • the grooves 33, 34, 35 and opposite grooves 33 ', 34', 35 ' are from a bearing bore 39 of the respective inlet cam, e.g. 13, introduced, in the grooves 33, 34, 35 or in the grooves 33 ', 34', 35 'opposite these pin portions 40, 41 of the pins 27, 28, 29 engage.
  • the actuator 26 comprises a plurality of piston-like guide sections 42, 43, 44 and 45 distributed over its length, which are shown as local thickened bearings 46, 47, 48, 49 and interact with cylinder sections 50, 51, 52, 53 of the bore 24 of the camshaft 1.
  • the pins 27, 28, 29, which can be pressed into openings 54, 55, 56 of the actuator 26, are provided in the region of the bearing thickenings 47, 48, 49.
  • the bearing thickening 46 which runs adjacent to the other end face 57 of the camshaft, is designed as an oil supply device 58 for a hydraulic device 59.
  • the bearing thickening 46 has a sliding bore 60 for a fixed cylinder, in which an axial slide 62 is inserted.
  • the axial slide 62 is connected to an electromagnet 63.
  • a hydraulic piston 64 is attached to the bearing thickening 46, which is surrounded by a housing 65 and can be acted upon by hydraulic oil via a first pressure chamber D1 and a second pressure chamber D2.
  • the housing 65 is circular and has on its outside transmission means 66 - sprocket, belt ring - for belts, chains or the like, with which the camshaft 1 is driven by a crankshaft. With 67 a closing part for the housing 65 is designated; that limits the pressure space D1. Screws 68, which are aligned in the axial direction B-B of the camshaft, are used to fasten the hydraulic device 59 to the camshaft 1.
  • the camshaft 1 with the hydraulic device 59 and the adjusting device 25, possibly also just the housing 65, can be a prefabricated module which can be inserted into the camshaft housing 2 - possibly interchangeable with a camshaft with a fixed intake cam.
  • the switching points for the switching device 25, which bring about an adjustment of the inlet cams 11, 12, 13, can be determined as a function of the parameters speed, load - accelerator pedal position - and oil temperature by means of a computer.

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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

This variable valve timing gear is suitable for internal combustion engines of the reciprocating piston type, which have inlet and exhaust valves for controlling the exhaust and refill. The inlet and exhaust valves are actuated by a camshaft, which for this purpose has inlet and exhaust cams. For influencing the valve overlap of the inlet and exhaust valves, the inlet and exhaust cams are designed so that they can rotate in opposition to one another, for which purpose an adjusting device is provided. The said adjusting device is provided with an adjusting element, which is arranged axially movably in a bore of the camshaft and, by way of drivers designed as pins and control guides, rotates the inlet cams in relation to the exhaust cams. <IMAGE>

Description

Die Erfindung betrifft eine variable Ventilsteuerung nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a variable valve control according to the preamble of claim 1.

Dank variabler Ventilsteuerungen sind nicht nur HC-Rohemissionen günstig beeinflussbar, sondern auch NOx-Emissionen reduzierbar. Außerdem können sie den Kraftstoffverbrauch, den stabilen Leerlauf, das Drehmoment und die Leistung einer Brennkraftmaschine verbessern. Hierzu werden Ventilüberschneidungen - Ein- und Auslaßventile - verändert, dergestalt, daß bei niedrigen Drehzahlen eine relativ geringe und bei höheren Drehzahlen eine relativ große Überschneidung erfolgt.Thanks to variable valve controls, not only can raw HC emissions be influenced favorably, but NO x emissions can also be reduced. They can also improve fuel consumption, stable idling, torque and performance of an internal combustion engine. For this purpose, valve overlaps - intake and exhaust valves - are changed such that there is a relatively small overlap at low speeds and a relatively large overlap at higher speeds.

Bekannt ist, US-SAE Paper 740 102, Seite 2 Fig. 1, eine variable Ventilsteuerung, bei der in einer Bohrung einer Nockenwelle ein axial bewegliches Stellorgan vorgesehen ist, das mit einem Mitnehmer in eine Verdrehung der Einlaßnocken bewirkende bogenförmige Steuerführung eingreift. Zwar wird mit dieser Ausführung eine vage Konstruktionsrichtung vorgegeben, jedoch ist sie von einer in die Praxis umsetzbaren Lösung noch entfernt.It is known, US-SAE Paper 740 102, page 2 Fig. 1, a variable valve control, in which an axially movable actuator is provided in a bore of a camshaft, which engages with a driver in a rotation of the inlet cams causing arcuate control guide. Although this version specifies a vague direction of construction, it is still a long way from a practical solution.

Aufgabe der Erfindung ist es daher, ausgehend von diesem Stand der Technik eine variable Ventilsteuerung mit gegeneinander verdrehbaren Ein- und Auslaßnocken zu schaffen, die sich problemlos verwirklichen lässt und sich durch gute Funktion auszeichnet.It is therefore the object of the invention to create, based on this prior art, a variable valve control with inlet and outlet cams which can be rotated relative to one another and which can be implemented without problems and is distinguished by good function.

Erfindungsgemäß wird diese Aufgabe durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst. Weitere Merkmale sind in den Unteransprüchen enthalten.According to the invention, this object is achieved by the characterizing features of patent claim 1. Further features are contained in the subclaims.

Die mit der Erfindung hauptsächlich erzielten Vorteile sind darin zu sehen, daß das Stellorgan mit seinen Mitnehmern, die in Nute der Einlaßnocken eingreifen, nicht nur baulich leicht realisierbar sondern bezüglich Verdrehfunktion der Einlaßnocken betriebssicher und hochwirksam ist. Dabei ist sowohl das Stellorgan wie auch die Nockenwelle im Aufbau einfach, wobei letztere eine sogenannte gebaute Nockenwelle sein kann, auf der Auslaßnocken, Lagerbüchsen oder dergleichen festgesetzt und die Einlaßnocken drehbar gelagert sind. Die Stellvorrichtung umfasst eine Hydraulikeinrichtung und ein Elektromagnet, ist an einer Stirnseite der Nockenwelle räumlich günstig angeordnet und kann gegebenenfalls als zulieferfähiges Modul aufgebaut sein, das z.B. als Variante gegenüber einer Nockenwelle mit festem Ein- und Auslaßnocken bei Motoren gleichen Aufbaus jedoch unterschiedlichen Leistungsprofils verwendet werden kann. Schließlich eignet sich diese Art der Nockenwellenverstellung für sogenannte Einnockenwellen-Brennkraftmaschinen, bei denen die Ein- und Auslaßnocken auf einer gemeinsamen Welle angeordnet sind.The main advantages achieved with the invention can be seen in the fact that the actuator with its drivers which engage in the groove of the inlet cam is not only structurally easy to implement but also reliable and highly effective with respect to the rotation function of the inlet cam. Both the actuator and the camshaft are simple in construction, the latter being a so-called built camshaft can be fixed on the outlet cams, bearing bushes or the like and the inlet cams are rotatably mounted. The actuating device comprises a hydraulic device and an electromagnet, is arranged on one end of the camshaft in a spatially advantageous manner and can optionally be constructed as a module that can be supplied, which can be used, for example, as a variant compared to a camshaft with fixed inlet and outlet cams for engines of the same construction but with different performance profiles . Finally, this type of camshaft adjustment is suitable for so-called single-camshaft internal combustion engines, in which the intake and exhaust cams are arranged on a common shaft.

In der Zeichnung wird ein Ausführungsbeispiel der Erfindung gezeigt, das nachstehend näher beschrieben ist.In the drawing, an embodiment of the invention is shown, which is described in more detail below.

Es zeigt

Fig. 1
einen Schnitt durch eine Brennkraftmaschinen-Nockenwelle im Bereich eines Nockenwellengehäuses mit der erfindungsgemäßen variablen Ventilsteuerung,
Fig. 2
einen Schnitt nach der Linie II-II der Fig. 1, teilweise im Schnitt,
Fig. 3
eine Ansicht in Pfeilrichtung A der Fig. 1,
Fig. 4
einen Schnitt nach der Linie IV-IV der Fig. 1.
It shows
Fig. 1
3 shows a section through an internal combustion engine camshaft in the area of a camshaft housing with the variable valve control according to the invention,
Fig. 2
2 shows a section along the line II-II of FIG. 1, partly in section,
Fig. 3
2 shows a view in the direction of arrow A in FIG. 1,
Fig. 4
a section along the line IV-IV of Fig. 1st

Eine Nockenwelle 1 für eine nicht näher dargestellte Brennkraftmaschine - Hubkolbenbauart mit Ein- und Auslaß-Hubventilen; fremdgezündet - ist mit einer variablen Ventilsteuerung versehen. Die Nockenwelle 1 ist in einem Nockenwellengehäuse 2 angeordnet, das Brennräumen von Zylindern bzw. eines Zylinderkopfes einer Mehrzylinderbrennkraftmaschine begrenzt.A camshaft 1 for an internal combustion engine, not shown - reciprocating piston type with intake and exhaust lift valves; spark-ignited - is equipped with a variable valve control. The camshaft 1 is arranged in a camshaft housing 2, which limits the combustion chambers of cylinders or a cylinder head of a multi-cylinder internal combustion engine.

Zur Lagerung der Nockenwelle 1 dienen Lagerzapfen 3, 4, 5, 6, die mit korrespondierenden Lagerstühlen 7, 8, 9, 10 des Nockenwellengehäuses 2 zusammenarbeiten.Bearing journals 3, 4, 5, 6, which cooperate with corresponding bearing seats 7, 8, 9, 10 of the camshaft housing 2, serve to mount the camshaft 1.

Der Lagerzapfen 3 ist aus einem Stück mit der Nockenwelle 1 hergestellt; die Lagerzapfen 4, 5, und 6 sind getrennt von ihr hergestellt. Es handelt sich folglich um eine aus mehreren Bauteilen zusammengesetzte Nockenwelle, für die auch der Begriff gebaute Nockenwelle verwendet wird. Darüber hinaus sind auf der Nockenwelle 1 angeordnet: Einlaßnocken 11, 12, 13 und Auslaßnocken 14, 15, 16, und die Lagerzapfen 4 und 5 sind Bestandteil von die Nockenwelle 1 umgebenden Lagerbüchsen 17, 18. Auf ihrer äußeren Umfangsfläche 19 ist die Nockenwelle 1 mit einer sich in axialer Richtung B-B erstreckenden Verzahnung 20 versehen, auf der die Auslaßnocken 14, 15, 16, die Lagerbüchsen 17, 18 und das die eine Stirnseite 21 der Nockenwelle 1 begrenzende Lager 6 mit korrespondierender Ausbildung verdrehfest festgelegt. Bei 22 ist ein Schließelement 23 in eine durchgehende Bohrung 24 der Nockenwelle 1 eingesetzt.The bearing journal 3 is made in one piece with the camshaft 1; the bearing pins 4, 5 and 6 are made separately from it. It is therefore a camshaft composed of several components, for which the term built camshaft is also used. In addition, are arranged on the camshaft 1: inlet cams 11, 12, 13 and outlet cams 14, 15, 16, and the bearing pins 4 and 5 are part of the bearing bushes 17, 18 surrounding the camshaft 1. The camshaft 1 is on its outer peripheral surface 19 provided with a toothing 20 extending in the axial direction BB, on which the outlet cams 14, 15, 16, the bearing bushes 17, 18 and the bearing 6, which delimits an end face 21 of the camshaft 1, are rotatably fixed with a corresponding design. At 22, a closing element 23 is inserted into a through bore 24 of the camshaft 1.

Innerhalb der Bohrung 24 ist ein einer Steuervorrichtung 25 zugehöriges Stellorgan 26 angeordnet, das axial beweglich - Richtung B-B - ausgebildet ist und eine rohrförmige Konfiguration besitzt. Das Stellorgan 26 weist als Mitnehmer ausgebildete Zapfen 27, 28, 29 auf, die schlitzartige Führungsöffnungen (Fig. 3) 30, 31, 32 in der Nockenwelle 1 durchdringen und mit Nute 33, 34, 35 von Steuerführungen 36, 37, 38 der Einlaßnocken 11, 12, 13 zusammenarbeiten. Die Steuerführungen 36, 37, 38 sind schräg zu einer Mittellängsebene C-C der Nockenwelle 1 angestellt (Fig. 4), wodurch Längsbewegungen - Richtung B-B - des Stellorgans 26 im Bereich der Länge FOL der Führungsöffnungen 30, 31, 32 zu Drehbewegungen - Winkel α (Fig. 2) - der Einlaßnocken 11, 12, 13 führen.Arranged within the bore 24 is an actuator 26 belonging to a control device 25, which is axially movable - direction BB - and has a tubular configuration. The actuator 26 has pins 27, 28, 29 designed as drivers which penetrate slot-like guide openings (FIG. 3) 30, 31, 32 in the camshaft 1 and with grooves 33, 34, 35 of control guides 36, 37, 38 of the inlet cams 11, 12, 13 work together. The control guides 36, 37, 38 are positioned obliquely to a central longitudinal plane CC of the camshaft 1 (FIG. 4), as a result of which longitudinal movements - direction BB - of the actuator 26 in the region of the length FO L of the guide openings 30, 31, 32 to rotary movements - angle α (Fig. 2) - the inlet cam 11, 12, 13 lead.

Die Nute 33, 34, 35 und gegenüberliegende Nute 33', 34', 35' sind von einer Lagerbohrung 39 des jeweiligen Einlaßnockens, z.B. 13, eingebracht, wobei in die Nute 33, 34, 35 bzw. in die diesen gegenüberliegende Nute 33', 34', 35' Zapfenabschnitte 40, 41 der Zapfen 27, 28, 29 eingreifen.The grooves 33, 34, 35 and opposite grooves 33 ', 34', 35 'are from a bearing bore 39 of the respective inlet cam, e.g. 13, introduced, in the grooves 33, 34, 35 or in the grooves 33 ', 34', 35 'opposite these pin portions 40, 41 of the pins 27, 28, 29 engage.

Das Stellorgan 26 umfasst über seine Länge verteilt mehrere kolbenartige Führungsabschnitte 42, 43, 44 und 45, die als örtliche Lagerverdickungen 46, 47, 48, 49 dargestellt sind und mit Zylinderabschnitten 50, 51, 52, 53 der Bohrung 24 der Nockenwelle 1 zusammenwirken.The actuator 26 comprises a plurality of piston-like guide sections 42, 43, 44 and 45 distributed over its length, which are shown as local thickened bearings 46, 47, 48, 49 and interact with cylinder sections 50, 51, 52, 53 of the bore 24 of the camshaft 1.

Im Ausführungsbeispiel sind die Zapfen 27, 28, 29, die in Öffnungen 54, 55, 56 des Stellorgans 26 eingepresst sein können, im Bereich der Lagerverdickungen 47, 48, 49 vorgesehen. Die Lagerverdickung 46, die benachbart der anderen Stirnseite 57 der Nockenwelle verläuft, ist als Ölzuführeinrichtung 58 für eine Hydraulikeinrichtung 59 ausgebildet. Dabei weist die Lagerverdickung 46 eine Schiebebohrung 60 für einen feststehenden Zylinder auf, in den ein Axialschieber 62 eingesetzt ist. Der Axialschieber 62 ist mit einem Elektromagnet 63 verbunden. Außerdem ist an der Lagerverdickung 46 ein Hydraulikkolben 64 befestigt, der von einem Gehäuse 65 umgeben ist und über einen ersten Druckraum D1 und einen zweiten Druckraum D2 mit Hydrauliköl beaufschlagbar ist. Das Gehäuse 65 ist kreisrund und besitzt an seiner Außenseite Übertragungsmittel 66 - Zahnkranz, Riemenkranz - für Riemen, Ketten oder dergleichen, mit der die Nockenwelle 1 von einer Kurbelwelle angetrieben wird. Mit 67 ist ein Schließteil für das Gehäuse 65 bezeichnet; das den Druckraum D1 begrenzt. Zur Befestigung der Hydraulikeinrichtung 59 an der Nockenwelle 1 dienen Schrauben 68, die in axialer Richtung B-B der Nockenwelle ausgerichtet sind.In the exemplary embodiment, the pins 27, 28, 29, which can be pressed into openings 54, 55, 56 of the actuator 26, are provided in the region of the bearing thickenings 47, 48, 49. The bearing thickening 46, which runs adjacent to the other end face 57 of the camshaft, is designed as an oil supply device 58 for a hydraulic device 59. The bearing thickening 46 has a sliding bore 60 for a fixed cylinder, in which an axial slide 62 is inserted. The axial slide 62 is connected to an electromagnet 63. In addition, a hydraulic piston 64 is attached to the bearing thickening 46, which is surrounded by a housing 65 and can be acted upon by hydraulic oil via a first pressure chamber D1 and a second pressure chamber D2. The housing 65 is circular and has on its outside transmission means 66 - sprocket, belt ring - for belts, chains or the like, with which the camshaft 1 is driven by a crankshaft. With 67 a closing part for the housing 65 is designated; that limits the pressure space D1. Screws 68, which are aligned in the axial direction B-B of the camshaft, are used to fasten the hydraulic device 59 to the camshaft 1.

Die Nockenwelle 1 mit Hydraulikeinrichtung 59 und Stellvorrichtung 25, eventuell auch nur Gehäuse 65, kann ein vorgefertigtes Modul sein, das in das Nockenwellengehäuse 2 einsetzbar - gegebenenfalls gegen eine Nockenwelle mit feststehenden Einlaßnocken austauschbar - ist.The camshaft 1 with the hydraulic device 59 and the adjusting device 25, possibly also just the housing 65, can be a prefabricated module which can be inserted into the camshaft housing 2 - possibly interchangeable with a camshaft with a fixed intake cam.

Die Schaltpunkte für die Schaltvorrichtung 25, die eine Verstellung der Einlaßnocken 11, 12, 13 bewirken, können als Funktion der Parameter Drehzahl, Last - Gaspedalstellung - und Öltemperatur mittels eines Rechners festgelegt werden.The switching points for the switching device 25, which bring about an adjustment of the inlet cams 11, 12, 13, can be determined as a function of the parameters speed, load - accelerator pedal position - and oil temperature by means of a computer.

Claims (10)

Variable Ventilsteuerung für Brennkraftmaschinen der Hubkolbenbauart mit Ein- und Auslaßventilen zur Gaswechselsteurerung, die mit Ein- und Auslaßnocken einer Nockenwelle betätigt werden, wobei ein Teil ihrer Nocken zur Beeinflussung der Ventilüberschneidung der Ein- und Auslaßventile gegeneinander verdrehbar sind, was durch eine Stellvorrichtung bewerkstelligt wird, die ein in einer Axialbohrung der Nockenwelle axialbewegliches Stellorgan umfasst, welches Stellorgan über Mitnehmer und Verdrehung bewirkende Steuerführungen die Einlaßnocken gegenüber den Auslaßnocken verstellt, dadurch gekennzeichnet, daß die Mitnehmer Zapfen (27, 28, 29) des Stellorgans (26) sind, die Führungsöffnungen (30, 31, 32) in der Nockenwelle (1) durchdringen und in als Steuerführungen (36, 37, 38) ausgebildete Nute (33, 34, 35) in Lagerbohrungen (39) der drehbar auf der Nockenwelle (1) gelagerten Einlaßnocken (11, 12, 13) eingreifen.Variable valve control for internal combustion engines of the reciprocating piston type with intake and exhaust valves for gas exchange control, which are actuated with intake and exhaust cams of a camshaft, some of their cams being rotatable relative to one another to influence the valve overlap of the intake and exhaust valves, which is accomplished by an actuating device, which comprises an actuator which is axially movable in an axial bore of the camshaft, which actuator adjusts the inlet cams with respect to the outlet cams by means of drivers and rotation, characterized in that the drivers are pins (27, 28, 29) of the actuator (26), the guide openings ( 30, 31, 32) penetrate in the camshaft (1) and in grooves (33, 34, 35) designed as control guides (36, 37, 38) in bearing bores (39) of the inlet cam (11) rotatably mounted on the camshaft (1) , 12, 13) intervene. Variable Ventilsteuerung nach Anspruch 1, dadurch gekennzeichnet, daß jeweils eine Nut (33, 34, 35 und 33', 34', 35') an gegenüberliegenden Seiten der Lagerbohrung (39) angeordnet sind, in die Zapfenabschnitte (40, 41) der Zapfen (27, 28, 29) eingreifen.Variable valve control according to claim 1, characterized in that in each case a groove (33, 34, 35 and 33 ', 34', 35 ') is arranged on opposite sides of the bearing bore (39) into the pin sections (40, 41) of the pins (27, 28, 29) intervene. Variable Ventilsteuerung nach Anspruch 1, dadurch gekennzeichnet, daß das Stellorgan (26) rohrartig ausgebildet ist und mehrere über seine Länge verteilte kolbenartige Führungsabschnitte (42, 43, 44, 45) aufweist, die Zylinderabschnitten (50, 51, 52, 53) der Bohrung (24) der Nockenwelle (1) zusammenarbeiten.Variable valve control according to claim 1, characterized in that the actuator (26) is tubular and has a plurality of piston-like guide sections (42, 43, 44, 45) distributed over its length, the cylinder sections (50, 51, 52, 53) of the bore (24) of the camshaft (1) work together. Variable Ventilsteuerung nach Anspruch 3, dadurch gekennzeichnet, daß die Führungsabschnitte (42, 43, 44, 45) durch örtliche Verdickungen (46, 47, 48, 49) gebildet werden.Variable valve control according to claim 3, characterized in that the guide sections (42, 43, 44, 45) are formed by local thickenings (46, 47, 48, 49). Variable Ventilsteuerung nach den Ansprüchen 3 und 4, dadurch gekennzeichnet, daß ein Teil der Führungsabschnitte (43, 44, 45) im Bereich der Zapfen (27, 28, 29) vorgesehen sind.Variable valve control according to claims 3 and 4, characterized in that part of the guide sections (43, 44, 45) are provided in the region of the pins (27, 28, 29). Variable Ventilsteuerung nach einem oder mehreren der vorangehenden Ansprüche, dadurch gekennzeichnet, daß auf einer Stirnseite (57) der Nockenwelle(1) das Verstellorgan (26) mit einer Lagerverdickung als Ölzuführeinrichtung (58) für eine Hydraulikeinrichtung (59) der Stellvorrichtung (25) ausgebildet ist.Variable valve control according to one or more of the preceding claims, characterized in that on one end face (57) of the camshaft (1) the adjusting member (26) is formed with a thickened bearing as an oil feed device (58) for a hydraulic device (59) of the adjusting device (25) is. Variable Ventilsteuerung nach Anspruch 6, dadurch gekennzeichnet, daß die Lagerverdickung (42) eine Schiebebohrung (60) für einen Axialschieber (61) aufweist.Variable valve control according to claim 6, characterized in that the bearing thickening (42) has a sliding bore (60) for an axial slide (61). Variable Ventilsteuerung nach Anspruch 6, dadurch gekennzeichnet, daß die Lagerverdickung (42) mit einem Hydraulikkolben (63) der Hydraulikeinrichtung (59) verbunden ist.Variable valve control according to claim 6, characterized in that the bearing thickening (42) is connected to a hydraulic piston (63) of the hydraulic device (59). Variable Ventilsteuerung nach Anspruch 8, dadurch gekennzeichnet, daß der Hydraulikkolben (63) in einem Gehäuse (64) untergebracht ist, das an seiner Außenseite Übertragungsmittel (65) für Endlosglieder (65) wie Riemen, Kette oder dergleichen aufweist.Variable valve control according to Claim 8, characterized in that the hydraulic piston (63) is accommodated in a housing (64) which has on its outside transmission means (65) for endless links (65) such as belts, chains or the like. Variable Ventilsteuerung nach einem oder mehreren der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Nockenwelle (1) und die Stellvorrichtung (25), gegebenenfalls nur Teile davon, ein vorgefertigtes Modul bilden.Variable valve control according to one or more of the preceding claims, characterized in that the camshaft (1) and the adjusting device (25), possibly only parts thereof, form a prefabricated module.
EP94112492A 1993-09-21 1994-08-10 Variable valve drive Withdrawn EP0644318A1 (en)

Applications Claiming Priority (2)

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DE4331977A DE4331977A1 (en) 1993-09-21 1993-09-21 Variable valve timing
DE4331977 1993-09-21

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EP (1) EP0644318A1 (en)
JP (1) JPH07150911A (en)
KR (1) KR950008914A (en)
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EP1860286A2 (en) * 2006-05-27 2007-11-28 Mahle International GmbH Camshaft
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EP1860286A2 (en) * 2006-05-27 2007-11-28 Mahle International GmbH Camshaft
EP1860286A3 (en) * 2006-05-27 2008-05-21 Mahle International GmbH Camshaft
WO2008075094A1 (en) * 2006-12-19 2008-06-26 Mechadyne Plc Camshaft and phaser assembly

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KR950008914A (en) 1995-04-19
US5509384A (en) 1996-04-23
DE4331977A1 (en) 1995-03-23
JPH07150911A (en) 1995-06-13

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