EP0911492B1 - Device to modify the angular phase of an internal combustion engine camshaft - Google Patents

Device to modify the angular phase of an internal combustion engine camshaft Download PDF

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Publication number
EP0911492B1
EP0911492B1 EP98890293A EP98890293A EP0911492B1 EP 0911492 B1 EP0911492 B1 EP 0911492B1 EP 98890293 A EP98890293 A EP 98890293A EP 98890293 A EP98890293 A EP 98890293A EP 0911492 B1 EP0911492 B1 EP 0911492B1
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EP
European Patent Office
Prior art keywords
camshaft
driving member
housing
axis
pumping member
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Expired - Fee Related
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EP98890293A
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German (de)
French (fr)
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EP0911492A1 (en
Inventor
Siegfried Heer
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TCG Unitech AG
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TCG Unitech AG
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Publication of EP0911492A1 publication Critical patent/EP0911492A1/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
    • F01L1/34—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
    • 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 device for adjusting a camshaft Internal combustion engine according to the preamble of claim 1.
  • the camshaft one Internal combustion engine is usually driven by a sprocket connected to the crankshaft is connected via a drive chain, or one designed as a pulley Drive wheel connected to the crankshaft via a toothed belt stands, driven.
  • DE 41 10 088 C1 and DE 39 29 619 A1 are adjustment devices known in which between one connected to the camshaft Component and a component connected to the drive wheel an adjusting element is provided which has two helical teeth, which with corresponding toothing of the camshaft or the drive wheel in Stand by.
  • An axial displacement of this adjusting element can Rotation of the camshaft relative to the drive wheel can be caused.
  • a The possibility of axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is activated.
  • the disadvantage of this solution is that to achieve the necessary Forces a relatively large hydraulic piston is required, which is a represents great construction effort.
  • an electrical adjustment device is known from DE 41 01 676 A1, in which an electric motor is provided which has a thread play Adjustment element moves.
  • the adjustment element is essentially with camshaft speed, must be between the electric motor and the Adjustment element an axial thrust bearing can be provided, which the relative movement between the sales-resistant and the rotating component.
  • This Axial thrust bearing is practically throughout the known solution Engine operation is burdened by the acting between the drive wheel and camshaft Torsional moments always have an axial force on the Adjustment element is exercised.
  • This thrust bearing is therefore a critical one Component that limits the life of the engine.
  • EP 363 600 A shows an adjusting device for a camshaft has hydraulic transmission element with two vane wheels, of which one is arranged in a slider that is displaceable relative to the housing is. Such a device is due to a variety of sealing surfaces complex and prone to errors. There is also space due to the axial offset saving construction is difficult.
  • the object of the present invention is to avoid the disadvantages and a simple, reliable and compact device for adjusting the camshaft to accomplish.
  • the adjustment should be carried out with a minimal supply from external energy.
  • this object is characterized by the features of the partially solved by claim 1.
  • the relative rotation of the camshaft in Reference to the drive wheel is made by the drive part to the camshaft Work done, the driving part hydraulically by a pumping part pumped working fluid is driven.
  • the pump part is driven via the camshaft drive wheel.
  • a particularly simple control of the relative rotation of the camshaft with respect to the Driving wheel can be reached when controlling the flow rate and / or the pressure of the working fluid conveyed from the pump part to the driving part by moving the common housing is transverse to the direction of the camshaft axis.
  • By the shift of the housing are the displacement volumes in the pump section and in the drive section enlarged or reduced to each other, causing a phase shift between the Camshaft and the drive wheel is done.
  • the maximum phase shift is determined by limited a rotation stop between the drive wheel and the camshaft.
  • the hydraulic Adjusting element has a housing in which a pump part coaxial with the camshaft Vane impeller is arranged, which is also a vane impeller coaxial with the camshaft hydraulically drives as a driving part, the output side of the pump part with the input side of the driving part is connected to the flow, and the flow rate and / or the pressure of the working fluid delivered from the pump part to the driving part is controllable, and that the Control of the flow rate and / or the pressure of the pumped to the driving part Working fluids by rotating the common housing about one to the axis of the Camshaft parallel axis takes place.
  • the twisting can have an effect similar to that of the linear displacement can be achieved.
  • the housing is driven in the direction of rotation easier to display in some cases.
  • the housing Due to the eccentric rotation of the housing about a parallel to the camshaft axis, however, it is arranged at a distance from it that the housing extends along of a circular arc twisted. Depending on the design of the overflow openings, this can be done Be achieved that the torque transmitted from the drive wheel to the camshaft exerts a small moment on the housing to twist it in a certain direction. This effect can be used to increase any frictional forces and moments compensate, or to facilitate the camshaft adjustment in a certain direction and thereby accelerate. If necessary, this effect can be achieved by a spring element, which is designed as a torsion spring, reinforced or weakened.
  • the device according to the invention eliminates the need for adjusting devices acting in the axial direction required helical gearing, which increases the manufacturing costs reduced.
  • the adjustment energy is provided by the camshaft drive itself, whereby external energy sources, such as additional electric motors or hydraulic pumps, are eliminated.
  • the adjustment can be controlled mechanically using the simplest means, for example or electrically, with extremely small adjustment forces.
  • Another advantage is that the Adjustment device universally used for motors of different sizes and performance can be. This significantly reduces the manufacturing effort.
  • a camshaft 1 is partially shown schematically. About an oil supply 2, a bore 3 inside the camshaft 1 is supplied with lubricating oil.
  • a drive wheel 4 is fixed in the axial direction but rotatably on the camshaft 1, the drive wheel 4 has a toothing 5, for example driven by a chain drive, not shown to become.
  • a hydraulic adjustment element is generally designated 6.
  • the adjusting element 6 is made consisting of a pump part 7 and a drive part 8.
  • a vane wheel 9 arranged, which is firmly connected to the drive wheel 4.
  • a Analog vane wheel 10 is provided, which is firmly connected to the camshaft 1.
  • Pump part 7 and drive part 8 have a common housing 11, which is not rotatable, however is arranged movable back and forth transversely to the axis of rotation.
  • the housing 11 has a Partition wall 12, which separates the pump part 7 from the drive part 8.
  • Overflow openings 13a, 13b connect the pump part 7 to the drive part 8.
  • the oil supply for the adjusting element 6 takes place via a bore 14 which communicates with the longitudinal bore 3 of the camshaft stands.
  • a screw part 15 mechanically secures the adjusting element 6 on the camshaft 1.
  • a bore 16 of the housing 11 of the adjusting element 6 has a pin 17 inserted with it an operating rod 18 communicates with the housing 11 in the direction of the Double arrow 19 to move back and forth.
  • the adjustment is made by a not shown Adjustment element that can be operated electrically, pneumatically or hydraulically. The adjustment forces required are very low, since essentially only frictional forces must be overcome. The actual adjustment energy is derived from the Drive wheel 4 transmitted moment gained.
  • a driver 20 is provided on the pump part 7, which in a corresponding recess 21 engages on the driving part 8. Through the game between driver 20 and recess 21, the adjustment range of the camshaft 1 is defined.
  • Fig. 2 is a section through the driving part 8 is shown.
  • the housing 11 is eccentric a working space 22 is formed for the vane wheel 10 of the drive part 8.
  • Slider 23 of the Vane wheel 10 slide on the inner peripheral surface 22a of the working space 22. Zur To simplify the illustration, only two slides 23 are shown in FIG. 2. Indeed a plurality of sliders are formed on the impeller 10 at equal circumferential intervals.
  • the working space 22 has the shape of a circular cylinder, the axis 22m of the working space 22 relative to the axis 10m of the vane wheel 10, which is also the axis the camshaft 1 is at a distance.
  • the direction of rotation of the camshaft is through indicated the arrow 24.
  • the working space 22 becomes the vane wheel 10 through the opening 13a sucked oil, while through the opening 13b oil in the Working space 22 is pressed.
  • the vane wheel 9 of the pump part 7 is coaxial with the vane wheel 10 of the drive part 8 arranged and not visible in FIG. 2.
  • a working space 25 of the pump part 7 is with a broken line shown in FIG. 2.
  • the working space 25 is opposite the vane wheel 9 offset, its axis 25m in the neutral position of the housing 11 the same Has a distance from the axis 10m, like the axis 22m of the working space 22.
  • the direction of the transfer is opposite.
  • the housing 11 If the housing 11 is now moved downward from the neutral position, the increases Eccentricity of the pump part 7, so that the pumping effect is increased per revolution. At the same time, the oil absorption in the driving part 8 is reduced per revolution. This will causes a leading movement of the driving part 8 relative to the pump part 7, so that a Pre-adjustment of the camshaft 1 relative to the drive wheel 4 takes place. An ending the pre-adjustment is achieved in that the housing 11 is returned to the neutral position becomes. It is essential that the housing 11 essentially in the direction of adjustment no forces act, so that only minimal forces are required for the adjustment are.
  • the respective adjustment state of the camshaft 1 with respect to the drive wheel 4 can be seen in known to be detected by a Hall element, so that even when different Inaccuracies an exact adjustment of the adjustment angle is possible.
  • a drive wheel 4a is arranged coaxially but rotatably has a toothing 5.
  • the drive wheel 4a is with a screw 15a in the axial direction secured.
  • a vane 9, which with the drive wheel 4a is fixedly connected, and a vane wheel 10, which is fixedly connected to the camshaft 1a, arranged.
  • the vane wheels 9, 10 form the essential elements for the pump part 7 or the driving part 8.
  • the housing 11a is eccentric by a roller bearing 30 via holding elements 31 attached to the cylinder head of an internal combustion engine, which is only roughly indicated by 32 is.
  • the axis 30a of the roller bearing 30 is parallel to the axis 1b of the camshaft 1a offset a distance d.
  • the hydraulic Adjusting element 6a is moved out of the neutral position shown in FIG. 3 become.
  • a relative movement between the vane wheels 9 and 10 causes what results in an adjustment of the camshaft 1a.
  • the angle by which the housing 11a is rotated about the axis 30a can vary depending on the design variant and size of the eccentricity d are between 60 and 240 degrees.
  • the drive in the direction of rotation can be done by various means, preferably an electrical one Stepper motor or a hydraulic adjustment by an adjusting element that by the Pressure is driven by engine oil.
  • an electric drive it is particularly preferred when the housing 11a is firmly connected to the rotor of an electric motor, not shown is or is integrally formed with this. This is a particularly simple one and robust construction possible.
  • the particular advantage of the present invention is that the drive energy for Adjustment of the camshaft is provided by the camshaft drive itself.
  • the externally applied adjustment forces are therefore minimal, so that small and poorly performing Adjusting elements can be used that require little space and are inexpensive to manufacture.

Abstract

Adjustment member (6) includes a hydraulic pump part (7) driven by the drive gear and a hydraulic drive part (8) connected to the camshaft (1a). The pump output has a flow connection to the drive part input and the flow rate and/or pressure of the working fluid delivered by the pump part can be controlled. Preferably pump and drive part are displacement machines.

Description

Die Erfindung betrifft eine Vorrichtung zur Verstellung einer Nockenwelle einer Brennkraftmaschine gemäß dem Oberbegriff von Patentanspruch 1.The invention relates to a device for adjusting a camshaft Internal combustion engine according to the preamble of claim 1.

Um in verschiedenen Bereichen des Motorkennfeldes optimale Verbrauchs- und Abgaswerte zu erzielen, ist es erforderlich, die Ventilsteuerzeiten in Abhängigkeit verschiedener Betriebsparameter zu verändern. Eine solche Veränderung der Steuerzeiten kann in eleganter Weise durch eine Verdrehung der Nockenwelle in Bezug auf das sie antreibende Rad bewirkt werden. Die Nockenwelle einer Brennkraftmaschine wird üblicherweise durch ein Kettenrad, das mit der Kurbelwelle über eine Antriebskette verbunden ist, oder ein als Riemenscheibe ausgebildetes Antriebsrad, das über einen Zahnriemen mit der Kurbelwelle in Verbindung steht, angetrieben.In order to optimize consumption and consumption in various areas of the engine map To achieve exhaust gas values, it is necessary to depend on the valve timing to change various operating parameters. Such a change in Timing can be elegantly twisted in by turning the camshaft Regarding the wheel driving them. The camshaft one Internal combustion engine is usually driven by a sprocket connected to the crankshaft is connected via a drive chain, or one designed as a pulley Drive wheel connected to the crankshaft via a toothed belt stands, driven.

Aus der US 4 091 776 A ist eine Nockenwellenantriebsvorrichtung bekannt, bei der die Nockenwelle durch Einpressen von Öl in den Zwischenraum zwischen zwei Drehkolben verstellt werden kann. Bei der Verstellung muss jedoch das gesamte Antriebsmoment der Nockenwelle überwunden werden, was eine starke Belastung des Ölkreislaufs darstellt. Um eine sichere Schmierölversorgung der Brennkraftmaschine in allen Betriebsbedingungen zu gewährleisten, muss die Ölpumpe in einem außerordentlich großen Ausmaß verstärkt werden, was aufwändig ist und den Kraftstoffverbrauch erhöht.From US 4 091 776 A a camshaft drive device is known from which the camshaft by injecting oil into the space between two rotary pistons can be adjusted. When adjusting, however, the entire Drive torque of the camshaft can be overcome, which is a strong one Represents load on the oil circuit. To ensure a reliable supply of lubricating oil To ensure the internal combustion engine in all operating conditions, the Oil pump to be reinforced to an extraordinarily large extent, which is expensive and increases fuel consumption.

Ähnliches gilt auch für Vorrichtungen, wie sie aus der EP 0 781 899 A oder der US 3 103 209 A bekannt sind.The same also applies to devices such as those from EP 0 781 899 A or US 3 103 209 A are known.

Aus der DE 41 10 088 C1 und aus der DE 39 29 619 A1 sind Verstelleinrichtungen bekannt, bei denen zwischen einem mit der Nockenwelle in Verbindung stehenden Bauteil und einem mit dem Antriebsrad in Verbindung stehenden Bauteil ein Verstellelement vorgesehen ist, das zwei Schrägverzahnungen aufweist, die mit entsprechenden Verzahnungen der Nockenwelle bzw. des Antriebsrades in Eingriff stehen. Durch eine Axialverschiebung dieses Verstellelementes kann eine Verdrehung der Nockenwelle gegenüber dem Antriebsrad bewirkt werden. Eine Möglichkeit der Axialverschiebung des Verstellelementes ist dabei die Betätigung durch einen Hydraulikkolben, der in Abhängigkeit von der erforderlichen Verstellung aktiviert wird. Nachteilig bei dieser Lösung ist, dass zur Erzielung der erforderlichen Kräfte ein relativ großer Hydraulikkolben erforderlich ist, was einen großen baulichen Aufwand darstellt. DE 41 10 088 C1 and DE 39 29 619 A1 are adjustment devices known in which between one connected to the camshaft Component and a component connected to the drive wheel an adjusting element is provided which has two helical teeth, which with corresponding toothing of the camshaft or the drive wheel in Stand by. An axial displacement of this adjusting element can Rotation of the camshaft relative to the drive wheel can be caused. A The possibility of axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is activated. The disadvantage of this solution is that to achieve the necessary Forces a relatively large hydraulic piston is required, which is a represents great construction effort.

Weiters ist aus der DE 41 01 676 A1 eine elektrische Verstellvorrichtung bekannt, bei der ein Elektromotor vorgesehen ist, der über ein Gewindespiel das Verstellelement verschiebt. Da sich jedoch das Verstellelement im wesentlichen mit Nockenwellendrehzahl dreht, muss zwischen dem Elektromotor und dem Verstellelement ein Axialdrucklager vorgesehen sein, das die Relativbewegung zwischen dem vertriebfesten und dem sich drehenden Bauteil aufnimmt. Dieses Axialdrucklager ist bei der bekannten Lösung praktisch während des gesamten Motorbetriebes belastet, da durch die zwischen Antriebsrad und Nockenwelle wirkenden Torsionsmomente stets eine in Axialrichtung wirkende Kraft auf das Verstellelement ausgeübt wird. Dieses Axialdrucklager ist daher ein kritischer Bauteil, der die Lebensdauer des Motors einschränkt.Furthermore, an electrical adjustment device is known from DE 41 01 676 A1, in which an electric motor is provided which has a thread play Adjustment element moves. However, since the adjustment element is essentially with camshaft speed, must be between the electric motor and the Adjustment element an axial thrust bearing can be provided, which the relative movement between the sales-resistant and the rotating component. This Axial thrust bearing is practically throughout the known solution Engine operation is burdened by the acting between the drive wheel and camshaft Torsional moments always have an axial force on the Adjustment element is exercised. This thrust bearing is therefore a critical one Component that limits the life of the engine.

Sowohl die oben beschriebenen hydraulischen, als auch die elektrischen Verstelleinrichtungen haben den Nachteil, dass eine externe Energiequelle - sei es in Form einer Hydraulikpumpe oder in Form eines Elektromotors - erforderlich ist. Dies erhöht die Herstellungskosten, vergrößert das Bauvolumen und verschlechtert den Gesamtwirkungsgrad der Brennkraftmaschine.Both the hydraulic and electrical adjustment devices described above have the disadvantage that an external energy source - be it in Form of a hydraulic pump or in the form of an electric motor - is required. This increases the manufacturing costs, increases the construction volume and worsens the overall efficiency of the internal combustion engine.

Die EP 363 600 A zeigt eine Verstellvorrichtung für eine Nockenwelle, die ein hydraulisches Übertragungselement mit zwei Flügelzellenrädern aufweist, von denen eines in einem gegenüber dem Gehäuse verschiebbaren Schieber angeordnet ist. Eine solche Vorrichtung ist aufgrund einer Vielzahl von Dichtflächen aufwändig und fehleranfällig. Außerdem ist durch den axialen Versatz eine Platz sparende Konstruktion nur schwer möglich.EP 363 600 A shows an adjusting device for a camshaft has hydraulic transmission element with two vane wheels, of which one is arranged in a slider that is displaceable relative to the housing is. Such a device is due to a variety of sealing surfaces complex and prone to errors. There is also space due to the axial offset saving construction is difficult.

Aufgabe der vorliegenden Erfindung ist es, die Nachteile zu vermeiden und eine einfache, zuverlässige und kompakte Vorrichtung zur Verstellung der Nockenwelle zu schaffen. Insbesondere soll die Verstellung mit einer minimalen Zufuhr von Fremdenergie möglich sein.The object of the present invention is to avoid the disadvantages and a simple, reliable and compact device for adjusting the camshaft to accomplish. In particular, the adjustment should be carried out with a minimal supply from external energy.

Erfindungsgemäß wird diese Aufgabe durch die Merkmale des kennzeichnenden teils von Patentanspruch 1 gelöst. Die Relatiwerdrehung der Nockenwelle in Bezug auf das Antriebsrad erfolgt dabei durch die vom Treibteil an die Nockenwelle abgegebene Arbeit, wobei der Treibteil hydraulisch durch ein vom Pumpteil gefördertes Arbeitsfluid angetrieben wird. Der Antrieb des Pumpteiles erfolgt dabei über das Antriebsrad der Nockenwelle. According to the invention, this object is characterized by the features of the partially solved by claim 1. The relative rotation of the camshaft in Reference to the drive wheel is made by the drive part to the camshaft Work done, the driving part hydraulically by a pumping part pumped working fluid is driven. The pump part is driven via the camshaft drive wheel.

Eine besonders einfache Steuerung der Relativverdrehung der Nockenwelle bezüglich des Antriebsrades ist zu erreichen, wenn die Steuerung der Durchflußmenge und/oder des Druckes des vom Pumpteil zum Treibteil geförderten Arbeitsfluids durch geradliniges Verschieben des gemeinsamen Gehäuses quer zur Richtung der Nockenwellenachse erfolgt. Durch die Verschiebung des Gehäuses werden die Verdrängungsvolumina im Pumpteil und im Treibteil zueinander vergrößert oder verkleinert, wodurch eine Phasenverschiebung zwischen der Nockenwelle und dem Antriebsrad erfolgt. Die maximale Phasenverschiebung wird durch einen Verdrehanschlag zwischen Antriebsrad und Nockenwelle begrenzt.A particularly simple control of the relative rotation of the camshaft with respect to the Driving wheel can be reached when controlling the flow rate and / or the pressure of the working fluid conveyed from the pump part to the driving part by moving the common housing is transverse to the direction of the camshaft axis. By the shift of the housing are the displacement volumes in the pump section and in the drive section enlarged or reduced to each other, causing a phase shift between the Camshaft and the drive wheel is done. The maximum phase shift is determined by limited a rotation stop between the drive wheel and the camshaft.

In einer alternativen Ausführungsvariante der Erfindung ist vorgesehen, daß das hydraulische Verstellelement ein Gehäuse aufweist, in dem als Pumpteil ein zur Nockenwelle koaxiales Flügelzellenlaufrad angeordnet ist, das ein ebenfalls mit der Nockenwelle koaxiales Flügelzellenlaufrad als Treibteil hydraulisch antreibt, wobei die Ausgangsseite des Pumpteils mit der Eingangsseite des Treibteils strömungsverbunden ist, und die Durchflußmenge und/oder der Druck des vom Pumpteil zum Treibteil geförderten Arbeitsfluids steuerbar ist, und daß die Steuerung der Durchflußmenge und/oder des Drucks des vom Pumpteil zum Treibteil geförderten Arbeitsfluids durch Verdrehung des gemeinsamen Gehäuses um eine zu der Achse der Nockenwelle parallele Achse erfolgt. Durch die Verdrehung kann ein analoger Effekt wie bei der linearen Verschiebung erreicht werden. Der Antrieb des Gehäuses in Drehrichtung ist jedoch in manchen Fällen einfacher darstellbar.In an alternative embodiment of the invention it is provided that the hydraulic Adjusting element has a housing in which a pump part coaxial with the camshaft Vane impeller is arranged, which is also a vane impeller coaxial with the camshaft hydraulically drives as a driving part, the output side of the pump part with the input side of the driving part is connected to the flow, and the flow rate and / or the pressure of the working fluid delivered from the pump part to the driving part is controllable, and that the Control of the flow rate and / or the pressure of the pumped to the driving part Working fluids by rotating the common housing about one to the axis of the Camshaft parallel axis takes place. The twisting can have an effect similar to that of the linear displacement can be achieved. However, the housing is driven in the direction of rotation easier to display in some cases.

Durch die exzentrische Verdrehung des Gehäuses um eine zu der Nockenwellenachse parallele, jedoch von ihr im Abstand angeordnete Achse wird erreicht, daß sich das Gehäuse entlang eines Kreisbogens verdreht. Je nach Ausbildung der Überströmöffnungen kann auf diese Weise erreicht werden, daß das vom Antriebsrad auf die Nockenwelle übertragene Moment ein kleines Moment auf das Gehäuse ausübt, um dieses in eine bestimmte Richtung zu verdrehen. Dieser Effekt kann ausgenützt werden, um etwaige Reibungskräfte und -momente zu kompensieren, oder um die Nockenwellenverstellung in eine bestimmte Richtung zu erleichtern und dadurch zu beschleunigen. Gegebenenfalls kann dieser Effekt durch ein Federelement, das als Torsionsfeder ausgebildet ist, verstärkt oder abgeschwächt werden.Due to the eccentric rotation of the housing about a parallel to the camshaft axis, however, it is arranged at a distance from it that the housing extends along of a circular arc twisted. Depending on the design of the overflow openings, this can be done Be achieved that the torque transmitted from the drive wheel to the camshaft exerts a small moment on the housing to twist it in a certain direction. This effect can be used to increase any frictional forces and moments compensate, or to facilitate the camshaft adjustment in a certain direction and thereby accelerate. If necessary, this effect can be achieved by a spring element, which is designed as a torsion spring, reinforced or weakened.

Um das maximale Drehmoment zwischen Antriebsrad und Nockenwelle zu begrenzen ist weiters vorgesehen, daß die Strömungsverbindung zwischen Pumpteil und Treibteil über ein Überdruckventil mit einer Leckölleitung verbunden ist.In order to limit the maximum torque between the drive wheel and the camshaft further provided that the flow connection between the pump part and the driving part via a Pressure relief valve is connected to a drain line.

Durch die erfindungsgemäße Vorrichtung entfällt die bei in axialer Richtung wirkenden Verstellvorrichtungen erforderliche Schrägverzahnung, wodurch sich der Herstellungsaufwand verringert. Die Verstellenergie wird durch den Nockenwellenantrieb selbst bereitgestellt, wodurch externe Energiequellen, wie zusätzliche Elektromotoren oder Hydraulikpumpen entfallen. Die Steuerung der Verstellung kann mit einfachsten Mitteln beispielsweise mechanisch oder elektrisch, mit äußerst kleinen Verstellkräften erfolgen. Ein weiterer Vorteil ist, daß die Verstellvorrichtung universell auch bei Motoren verschiedener Größe und Leistung eingesetzt werden kann. Dies verringert den Herstellungsaufwand entscheidend.The device according to the invention eliminates the need for adjusting devices acting in the axial direction required helical gearing, which increases the manufacturing costs reduced. The adjustment energy is provided by the camshaft drive itself, whereby external energy sources, such as additional electric motors or hydraulic pumps, are eliminated. The adjustment can be controlled mechanically using the simplest means, for example or electrically, with extremely small adjustment forces. Another advantage is that the Adjustment device universally used for motors of different sizes and performance can be. This significantly reduces the manufacturing effort.

Besonders bevorzugt ist es, wenn in dem Gehäuse ein Arbeitsraum für den Pumpteil und ein Arbeitsraum für den Treibteil vorgesehen ist, welche Arbeitsräume gegenüber der Nockenwellenachse gegensinnig versetzt angeordnet sind. Besonders vorteilhaft ist es dabei, wenn die Strömungsverbindung zwischen Pumpenteil und Treibteil durch Öffnungen in einer Trennwand zwischen Pumpe und Treibteil gebildet ist. In einer Neutralstellung des Gehäuses wird dabei pro Umdrehung der Nockenwelle der Pumpteil über die eine Öffnung eine vorbestimmte Ölmenge in den Treibteil fördern, und gleichzeitig über die andere Öffnung die gleiche Ölmenge aus dem Treibteil ansaugen. Beim Treibteil liegen die Verhältnisse genau umgekehrt, wobei die durchgesetzte Ölmenge gleich ist. Pumpteil und Treibteil werden sich daher mit der gleichen Drehzahl drehen. Es findet kein Verstellvorgang statt. Bei einer Verschiebung aus der Neutralstellung ändern sich die Verhältnisse insofern, als die im Pumpteil pro Umdrehung durchgesetzte Ölmenge im Ausmaß der Verschiebung verändert, während sich die im Treibteil durchgesetzte Menge gegenläufig dazu verändert. Auf diese Weise wird eine Relativbewegung zwischen Pumpteil und Treibteil bewirkt, was zu einer Veränderung der Phasenlage der Nockenwelle führt. Diese Ausführungsvariante hat gegenüber einer theoretisch möglichen vereinfachten Ausführungsvariante, bei der in einer Neutralstellung die Arbeitsräume vom Pumpenteil und Treibteil konzentrisch mit der Nockenwellenachse sind, den Vorteil, daß geringere Druckspitzen auftreten. Weiters ist die Ölführung zwischen Pumpteil und Treibteil besonders einfach, und es wird eine gleichmäßigere Wärmeverteilung bewirkt.It is particularly preferred if there is a working space for the pumping part and in the housing Work space is provided for the drive part, which work spaces with respect to the camshaft axis are arranged offset in opposite directions. It is particularly advantageous if the Flow connection between pump part and drive part through openings in a partition is formed between the pump and the driving part. In a neutral position of the housing per revolution of the camshaft, the pump part has a predetermined opening through one Pump the amount of oil into the drive part and at the same time the same through the other opening Aspirate the oil quantity from the driving part. The conditions are exact for the drive part vice versa, the amount of oil passed through is the same. Pump part and drive part will therefore turn at the same speed. There is no adjustment process. With a shift from the neutral position, the situation changes insofar as that in the pump part amount of oil passed through per revolution changed in the extent of the shift, while the quantity penetrated in the blowing part changes in the opposite direction. That way a relative movement between the pumping part and the driving part causes a change leads the phase position of the camshaft. This variant has a theoretical one possible simplified design variant, in which in a neutral position Working spaces of the pump part and drive part are concentric with the camshaft axis, the advantage that lower pressure peaks occur. Furthermore, the oil flow is between Pump part and drive part particularly simple, and it becomes a more even heat distribution causes.

Die Erfindung wird im Folgenden anhand der Figuren näher erläutert.The invention is explained in more detail below with reference to the figures.

Es zeigen:

Fig. 1
einen Schnitt durch eine Ausführungsvariante, die den grundsätzlichen Aufbau der Erfindung zeigt,
Fig. 2
einen Schnitt nach Linie II-II in Fig. 1 und
Fig. 3
zeigt eine besonders bevorzugte Ausführungsvariante der Erfindung.
Show it:
Fig. 1
3 shows a section through an embodiment variant which shows the basic structure of the invention,
Fig. 2
a section along line II-II in Fig. 1 and
Fig. 3
shows a particularly preferred embodiment of the invention.

In der Fig. 1 ist eine Nockenwelle 1 schematisch teilweise dargestellt. Über eine Ölversorgung 2 wird eine Bohrung 3 im Inneren der Nockenwelle 1 mit Schmieröl versorgt. Ein Antriebsrad 4 sitzt in Axialrichtung fixiert jedoch verdrehbar auf der Nockenwelle 1, wobei das Antriebsrad 4 eine Verzahnung 5 aufweist, um etwa über einen nicht dargestellten Kettentrieb angetrieben zu werden.In Fig. 1, a camshaft 1 is partially shown schematically. About an oil supply 2, a bore 3 inside the camshaft 1 is supplied with lubricating oil. A drive wheel 4 is fixed in the axial direction but rotatably on the camshaft 1, the drive wheel 4 has a toothing 5, for example driven by a chain drive, not shown to become.

Ein hydraulisches Verstellelement ist allgemein mit 6 bezeichnet. Das Verstellelement 6 besteht aus einem Pumpteil 7 und einem Treibteil 8. In dem Pumpteil 7 ist ein Flügelzellenrad 9 angeordnet, das fest mit dem Antriebsrad 4 in Verbindung steht. In dem Treibteil 8 ist ein analoges Flügelzellenrad 10 vorgesehen, das mit der Nockenwelle 1 fest verbunden ist. Pumpteil 7 und Treibteil 8 besitzen ein gemeinsames Gehäuse 11, das nicht drehbar ist, jedoch quer zur Drehachse hin und her beweglich angeordnet ist. Das Gehäuse 11 besitzt eine Trennwand 12, die den Pumpteil 7 von dem Treibteil 8 trennt. Überströmöffnungen 13a, 13b verbinden den Pumpteil 7 mit dem Treibteil 8. Die Ölversorgung für das Verstellelement 6 erfolgt über eine Bohrung 14, die mit der Längsbohrung 3 der Nockenwelle in Verbindung steht. Ein Schraubteil 15 sichert mechanisch das Verstellelement 6 auf der Nockenwelle 1. In einer Bohrung 16 des Gehäuses 11 des Verstellelementes 6 ist ein Stift 17 eingesetzt, der mit einer Betätigungsstange 18 in Verbindung steht, um das Gehäuse 11 in der Richtung des Doppelpfeiles 19 hin und her zu bewegen. Die Verstellung erfolgt dabei durch ein nicht dargestelltes Verstellelement, das elektrisch, pneumatisch oder hydraulisch betätigt werden kann. Die erforderlichen Verstellkräfte sind dabei sehr gering, da im wesentlichen nur Reibungskräfte überwunden werden müssen. Die eigentliche Verstellenergie wird aus dem über das Antriebsrad 4 übertragenen Moment gewonnen.A hydraulic adjustment element is generally designated 6. The adjusting element 6 is made consisting of a pump part 7 and a drive part 8. In the pump part 7 there is a vane wheel 9 arranged, which is firmly connected to the drive wheel 4. In the driving part 8 is a Analog vane wheel 10 is provided, which is firmly connected to the camshaft 1. Pump part 7 and drive part 8 have a common housing 11, which is not rotatable, however is arranged movable back and forth transversely to the axis of rotation. The housing 11 has a Partition wall 12, which separates the pump part 7 from the drive part 8. Overflow openings 13a, 13b connect the pump part 7 to the drive part 8. The oil supply for the adjusting element 6 takes place via a bore 14 which communicates with the longitudinal bore 3 of the camshaft stands. A screw part 15 mechanically secures the adjusting element 6 on the camshaft 1. In A bore 16 of the housing 11 of the adjusting element 6 has a pin 17 inserted with it an operating rod 18 communicates with the housing 11 in the direction of the Double arrow 19 to move back and forth. The adjustment is made by a not shown Adjustment element that can be operated electrically, pneumatically or hydraulically. The adjustment forces required are very low, since essentially only frictional forces must be overcome. The actual adjustment energy is derived from the Drive wheel 4 transmitted moment gained.

Um den möglichen Verstellbereich zu begrenzen, und um einen sicheren Betrieb auch dann zu ermöglichen, wenn das Verstellelement 6 nach einem Kaltstart noch nicht vollständig mit Öl gefüllt ist, ist am Pumpteil 7 ein Mitnehmer 20 vorgesehen, der in eine entsprechende Ausnehmung 21 am Treibteil 8 eingreift. Durch das Spiel zwischen Mitnehmer 20 und Ausnehmung 21 wird der Verstellbereich der Nockenwelle 1 definiert.To limit the possible adjustment range and to ensure safe operation enable if the adjusting element 6 is not completely filled with oil after a cold start is filled, a driver 20 is provided on the pump part 7, which in a corresponding recess 21 engages on the driving part 8. Through the game between driver 20 and recess 21, the adjustment range of the camshaft 1 is defined.

In der Folge wird der Betrieb der erfindungsgemäßen Vorrichtung erklärt werden. In der Fig. 2 ist ein Schnitt durch den Treibteil 8 dargestellt. In dem Gehäuse 11 ist dabei exzentrisch zu dem Flügelzellenrad 10 des Treibteils 8 ein Arbeitsraum 22 ausgebildet. Schieber 23 des Flügelzellenrades 10 gleiten an der inneren Umfangsfläche 22a des Arbeitsraumes 22. Zur Vereinfachung der Darstellung sind in der Fig. 2 nur zwei Schieber 23 dargestellt. Tatsächlich ist eine Vielzahl von Schiebern in gleichen Umfangsabständen an dem Flügelrad 10 ausgebildet. Der Arbeitsraum 22 besitzt die Form eines Kreiszylinders, wobei die Achse 22m des Arbeitsraumes 22 gegenüber der Achse 10m des Flügelzellenrades 10, die gleichzeitig die Achse der Nockenwelle 1 ist, einen Abstand aufweist. Die Drehrichtung der Nockenwelle ist durch den Pfeil 24 bezeichnet. Bei dieser Drehrichtung wird aus dem Arbeitsraum 22 des Flügelzellenrades 10 durch die Öffnung 13a Öl abgesaugt, während durch die Öffnung 13b Öl in den Arbeitsraum 22 eingepreßt wird. Dadurch wird das Flügelzellenrad 10 in Drehung versetzt. Das Flügelzellenrad 9 des Pumpteils 7 ist koaxial mit dem Flügelzellenrad 10 des Treibteils 8 angeordnet und in der Fig. 2 nicht sichtbar. Ein Arbeitsraum 25 des Pumpteils 7 ist mit einer unterbrochenen Linie in der Fig. 2 dargestellt. Der Arbeitsraum 25 ist gegenüber dem Flügelzellenrad 9 versetzt, wobei seine Achse 25m in der Neutralstellung des Gehäuses 11 den gleichen Abstand gegenüber der Achse 10m aufweist, wie die Achse 22m des Arbeitsraumes 22. Die Richtung der Versetzung ist jedoch entgegengesetzt. Durch die Drehung des Flügelzellenrades 9 des Pumpteils 7 entsprechend der Richtung des Pfeiles 24, wird der Ölstrom durch die Öffnung 13a vom Pumpteil 7 in den Treibteil 8 sowie der Ansaugstrom durch die Öffnung 13b aus dem Treibteil 8 in den Pumpteil 7 hervorgerufen. In der Neutralstellung des Gehäuses 11 herrscht dabei ein Gleichgewichtszustand, wenn die Drehzahl vom Pumpteil 7 und Treibteil 8 gleich sind. Es findet daher in dieser Stellung keine Verstellung der Nockenwelle 1 gegenüber dem Antriebsrad 4 statt. Nach einem Kaltstart kann man daher davon ausgehen, daß die Nockenwelle 1 im wesentlichen durch den Vorsprung 20 mitgenommen wird, der an einer Flanke der Ausnehmung 21 anliegt. Die Ventilverstellung ist daher auf "spät" eingestellt. Wird nun das Gehäuse 11 aus der neutralen Stellung nach unten bewegt, dann erhöht sich die Exzentrizität des Pumpteils 7, so daß die Pumpwirkung pro Umdrehung gesteigert wird. Gleichzeitig wird die Ölaufnahme im Treibteil 8 pro Umdrehung verringert. Dadurch wird eine vorauseilende Bewegung des Treibteils 8 gegenüber dem Pumpteil 7 bewirkt, so daß eine Vorverstellung der Nockenwelle 1 gegenüber dem Antriebsrad 4 stattfindet. Eine Beendigung der Vorverstellung wird dadurch erreicht, daß das Gehäuse 11 wieder in die Neutrallage zurückgeführt wird. Es ist wesentlich, daß auch das Gehäuse 11 in der Verstellrichtung im wesentlichen keine Kräfte einwirken, so daß für die Verstellung nur minimale Kräfte erforderlich sind.The operation of the device according to the invention will be explained below. In the Fig. 2 is a section through the driving part 8 is shown. The housing 11 is eccentric a working space 22 is formed for the vane wheel 10 of the drive part 8. Slider 23 of the Vane wheel 10 slide on the inner peripheral surface 22a of the working space 22. Zur To simplify the illustration, only two slides 23 are shown in FIG. 2. Indeed a plurality of sliders are formed on the impeller 10 at equal circumferential intervals. The working space 22 has the shape of a circular cylinder, the axis 22m of the working space 22 relative to the axis 10m of the vane wheel 10, which is also the axis the camshaft 1 is at a distance. The direction of rotation of the camshaft is through indicated the arrow 24. In this direction of rotation, the working space 22 becomes the vane wheel 10 through the opening 13a sucked oil, while through the opening 13b oil in the Working space 22 is pressed. This causes the vane wheel 10 to rotate. The vane wheel 9 of the pump part 7 is coaxial with the vane wheel 10 of the drive part 8 arranged and not visible in FIG. 2. A working space 25 of the pump part 7 is with a broken line shown in FIG. 2. The working space 25 is opposite the vane wheel 9 offset, its axis 25m in the neutral position of the housing 11 the same Has a distance from the axis 10m, like the axis 22m of the working space 22. However, the direction of the transfer is opposite. By rotating the vane wheel 9 of the pump part 7 according to the direction of arrow 24, the oil flow through the Opening 13a from the pump part 7 in the driving part 8 and the suction flow through the opening 13b from the drive part 8 into the pump part 7. In the neutral position of the housing 11 there is a state of equilibrium when the speed of the pump part 7 and drive part 8 are the same. There is therefore no adjustment of the camshaft 1 in this position the drive wheel 4 instead. After a cold start you can therefore assume that the camshaft 1 is essentially entrained by the projection 20, which on a Flank of the recess 21 is present. The valve adjustment is therefore set to "late". If the housing 11 is now moved downward from the neutral position, the increases Eccentricity of the pump part 7, so that the pumping effect is increased per revolution. At the same time, the oil absorption in the driving part 8 is reduced per revolution. This will causes a leading movement of the driving part 8 relative to the pump part 7, so that a Pre-adjustment of the camshaft 1 relative to the drive wheel 4 takes place. An ending the pre-adjustment is achieved in that the housing 11 is returned to the neutral position becomes. It is essential that the housing 11 essentially in the direction of adjustment no forces act, so that only minimal forces are required for the adjustment are.

Der jeweilige Verstellzustand der Nockenwelle 1 gegenüber dem Antriebsrad 4 kann in an sich bekannter Weise durch ein Hallelement erfaßt werden, so daß auch bei Vorliegen verschiedener Ungenauigkeiten eine genaue Einstellung des Verstellwinkels möglich ist.The respective adjustment state of the camshaft 1 with respect to the drive wheel 4 can be seen in known to be detected by a Hall element, so that even when different Inaccuracies an exact adjustment of the adjustment angle is possible.

In der Fig. 3 ist eine besonders bevorzugte Ausführungsvariante der Erfindung dargestellt, wobei gleiche Bauteile oder funktionell ähnliche Bauteile mit den gleichen Bezugszeichen bezeichnet sind.3 shows a particularly preferred embodiment variant of the invention, the same components or functionally similar components with the same reference numerals are designated.

Auf der Nockenwelle 1a ist koaxial, jedoch verdrehbar, ein Antriebsrad 4a angeordnet, das eine Verzahnung 5 aufweist. Das Antriebsrad 4a ist mit einer Verschraubung 15a in Axialrichtung gesichert. In dem Gehäuse 11a des hydraulischen Verstellelements 6a ist analog zur oben beschriebenen Ausführungsvariante ein Flügelzellenrad 9, das mit dem Antriebsrad 4a fest verbunden ist, und ein Flügelzellenrad 10, das mit der Nockenwelle 1a fest verbunden ist, angeordnet. Die Flügelzellenräder 9, 10 bilden die wesentlichen Elemente für den Pumpteil 7 bzw. den Treibteil 8. Das Gehäuse 11a ist exzentrisch durch ein Wälzlager 30 über Halteelemente 31 am Zylinderkopf einer Brennkraftmaschine befestigt, der mit 32 nur grob angedeutet ist. Die Achse 30a des Wälzlagers 30 ist parallel zur Achse 1b der Nockenwelle 1a jedoch um einen Abstand d versetzt. Auf diese Weise kann durch Verdrehen des Gehäuses 11a das hydraulische Verstellelement 6a aus der in der Fig. 3 dargestellten Neutralstellung herausbewegt werden. In Abhängigkeit von der Wegstrecke, um die das Gehäuse 11a aus der Neutralstellung herausbewegt wird, wird somit eine Relativbewegung zwischen den Flügelzellenrädern 9 und 10 bewirkt, was eine Verstellung der Nockenwelle 1a zur Folge hat.On the camshaft 1a, a drive wheel 4a is arranged coaxially but rotatably has a toothing 5. The drive wheel 4a is with a screw 15a in the axial direction secured. In the housing 11a of the hydraulic adjusting element 6a is analogous to Design variant described above, a vane 9, which with the drive wheel 4a is fixedly connected, and a vane wheel 10, which is fixedly connected to the camshaft 1a, arranged. The vane wheels 9, 10 form the essential elements for the pump part 7 or the driving part 8. The housing 11a is eccentric by a roller bearing 30 via holding elements 31 attached to the cylinder head of an internal combustion engine, which is only roughly indicated by 32 is. However, the axis 30a of the roller bearing 30 is parallel to the axis 1b of the camshaft 1a offset a distance d. In this way, the hydraulic Adjusting element 6a is moved out of the neutral position shown in FIG. 3 become. Depending on the distance by which the housing 11a from the neutral position is moved out, a relative movement between the vane wheels 9 and 10 causes what results in an adjustment of the camshaft 1a.

Der Winkel, um den das Gehäuse 11a um die Achse 30a verdreht wird, kann je nach Ausführungsvariante und Größe der Exzentrizität d zwischen 60 und 240 Grad betragen. Der Antrieb in Drehrichtung kann durch verschiedene Mittel erfolgen, bevorzugt sind ein elektrischer Schrittmotor oder eine hydraulische Verstellung durch eine Verstellelement, das durch den Druck von Motoröl angetrieben wird. Bei einem elektrischen Antrieb ist es besonders bevorzugt, wenn das Gehäuse 11a fest mit dem Rotor eines nicht dargestellten Elektromotors verbunden ist oder einstückig mit diesem ausgebildet ist. Auf diese Weise ist eine besonders einfache und robuste Konstruktion möglich.The angle by which the housing 11a is rotated about the axis 30a can vary depending on the design variant and size of the eccentricity d are between 60 and 240 degrees. The drive in the direction of rotation can be done by various means, preferably an electrical one Stepper motor or a hydraulic adjustment by an adjusting element that by the Pressure is driven by engine oil. In the case of an electric drive, it is particularly preferred when the housing 11a is firmly connected to the rotor of an electric motor, not shown is or is integrally formed with this. This is a particularly simple one and robust construction possible.

Der besondere Vorteil der vorliegenden Erfindung besteht darin, daß die Antriebsenergie zur Verstellung der Nockenwelle durch den Nockenwellenantrieb selbst bereitgestellt wird. Die extern aufzubringenden Verstellkräfte sind daher minimal, so daß kleine und leistungsschwache Verstellglieder eingesetzt werden können, die einen geringen Platzbedarf aufweisen und kostengünstig herstellbar sind.The particular advantage of the present invention is that the drive energy for Adjustment of the camshaft is provided by the camshaft drive itself. The externally applied adjustment forces are therefore minimal, so that small and poorly performing Adjusting elements can be used that require little space and are inexpensive to manufacture.

Claims (10)

  1. Device for adjusting the phase angle of a camshaft (1) of an internal combustion engine relative to the camshaft drive gear (4), comprising a hydraulic adjusting element (6) which is connected to both a member supporting the drive gear (4) and a member rigidly connected to the camshaft (1), the hydraulic adjusting element (6) being provided with a hydraulic pumping member (7) driven by the drive gear (4), and with a driving member (8) connected to the camshaft (1) and hydraulically driven by the pumping member (7), which members are configured as vane-type impellers, the outlet end of the pumping member (7) being flow-connected to the inlet end of the driving member (8) and the flow volume and/or pressure of the working fluid delivered from the pumping member (7) to the driving member (8) being regulated, characterized in that both pumping member (7) and driving member (8) are coaxial with the camshaft axis and share a common housing (11, 11a).
  2. Device according to claim 1, characterized in that the flow volume and/or pressure of the working fluid delivered from the pumping member (7) to the driving member (8) are regulated by linearly shifting the common housing (11) transversely to the axis (10m) of the camshaft (1).
  3. Device according to claim 1, characterized in that regulation of the flow volume and/or pressure of the working fluid delivered from the pumping member (7) to the driving member (8) is effected by rotating the common housing (11a) about an axis (30a) parallel to the axis (1b) of the camshaft (1a).
  4. Device according to claim 3, characterized in that a spring element is provided to preload the housing (11a) in the direction of rotation.
  5. Device according to any of claims 1 to 4, characterized in that the flow connection between pumping member (7) and driving member (8) is connected with an overflow oil line via a pressure relief valve.
  6. Device according to any of claims 1 to 5, characterized in that the housing (11) includes a working chamber (25) for the pumping member (7) and a working chamber (22) for the driving member (8), which working chambers (25, 22) are arranged so as to be displaced in opposite directions relative to the camshaft axis (10m).
  7. Device according to any of claims 1 to 6, characterized in that the flow connection between pumping member (7) and driving member (8) is established by openings (13a, 13b) in a partition (12) between pumping member (7) and driving member (8).
  8. Device according to any of claims 1 to 7, characterized in that the shifting or rotation of the common housing (11a) is actuated electrically, i.e. preferably by a stepper motor.
  9. Device according to in claim 8, characterized in that the housing (11a) is rigidly connected to the rotor of an electric motor.
  10. Device according to any of claims 1 to 7, characterized in that the shifting or rotation of the common housing (11a) is actuated hydraulically, preferably via the engine oil pressure.
EP98890293A 1997-10-21 1998-10-13 Device to modify the angular phase of an internal combustion engine camshaft Expired - Fee Related EP0911492B1 (en)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AT177897 1997-10-21
AT177897 1997-10-21
AT1778/97 1997-10-21
AT142298 1998-08-20
AT1422/98 1998-08-20
AT142298 1998-08-20

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Publication number Priority date Publication date Assignee Title
HUP0101674A3 (en) * 1998-05-12 2002-01-28 Trochocentric Internat Ag Device for adjusting the phase position of a shaft
US6328006B1 (en) * 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6302073B1 (en) * 1999-03-23 2001-10-16 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6257186B1 (en) * 1999-03-23 2001-07-10 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6277045B1 (en) * 1999-12-08 2001-08-21 Daimlerchrysler Corporation Thin profile cam sprocket with integrated timing target

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Publication number Priority date Publication date Assignee Title
US3103209A (en) 1961-03-10 1963-09-10 Gen Motors Corp Phase adjusting servo mechanism for internal combustion engine and the like
US4091776A (en) 1974-04-04 1978-05-30 Rockwell International Corporation Fluid actuated timing mechanism
DE3415861A1 (en) * 1984-04-28 1985-10-31 Pierburg Gmbh & Co Kg, 4040 Neuss DEVICE FOR CONTROLLING A COUPLING DEVICE
EP0363600B1 (en) * 1988-10-13 1992-07-29 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Device for varying the angular position of a camshaft
DE3929621A1 (en) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag DEVICE FOR RELATIVELY ADJUSTING A SHAFT TO A DRIVE WHEEL, IN PARTICULAR CAMSHAFT OF AN INTERNAL COMBUSTION ENGINE
DE3929619A1 (en) 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Connecting rod for shafts pivot angle - has adjustment between drive wheel and shaft, cam shaft with disc flange
DE4101676A1 (en) 1991-01-22 1992-07-23 Schaeffler Waelzlager Kg Rotary connection adjuster for camshaft to drive wheel - involves electric motor with thread section axially displaceable on fixed thread section for relative setting
DE4110088C1 (en) 1991-03-27 1992-07-09 Bayerische Motoren Werke Ag, 8000 Muenchen, De Relative shaft bearing position changing mechanism - has annular coupler with inner and outer toothing linked to axially displaceable piston
JPH04132414U (en) * 1991-05-29 1992-12-08 株式会社アツギユニシア Internal combustion engine valve timing control device
US5293845A (en) * 1991-09-02 1994-03-15 Toyota Jidosha Kabushiki Kaisha Control mechanism for engine valve timing
DE4135380A1 (en) * 1991-10-26 1993-04-29 Bosch Gmbh Robert HYDRAULIC CONTROL DEVICE
DE4237193A1 (en) * 1992-11-04 1994-05-05 Bosch Gmbh Robert Method for controlling a device for the relative rotation of a shaft and device for the relative rotation of the shaft of an internal combustion engine
DE69606613T2 (en) 1995-11-30 2000-07-13 Aisin Seiki Valve timing device

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EP0911492A1 (en) 1999-04-28
US6138623A (en) 2000-10-31
DE59803257D1 (en) 2002-04-11

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