EP1025343B1 - Device for changing the relative rotational position of a shaft to the drive wheel - Google Patents

Device for changing the relative rotational position of a shaft to the drive wheel Download PDF

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Publication number
EP1025343B1
EP1025343B1 EP99917979A EP99917979A EP1025343B1 EP 1025343 B1 EP1025343 B1 EP 1025343B1 EP 99917979 A EP99917979 A EP 99917979A EP 99917979 A EP99917979 A EP 99917979A EP 1025343 B1 EP1025343 B1 EP 1025343B1
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EP
European Patent Office
Prior art keywords
pressure
rotational position
changing
control
valve
Prior art date
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Revoked
Application number
EP99917979A
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German (de)
French (fr)
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EP1025343A1 (en
Inventor
Bernd Niethammer
Andreas Knecht
Alfred Trzmiel
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
Hilite Germany GmbH
Original Assignee
Dr Ing HCF Porsche AG
Hydraulik Ring GmbH
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Application filed by Dr Ing HCF Porsche AG, Hydraulik Ring GmbH filed Critical Dr Ing HCF Porsche AG
Priority to EP03009907.1A priority Critical patent/EP1331367B1/en
Publication of EP1025343A1 publication Critical patent/EP1025343A1/en
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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
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • 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 the relative change in the rotational position of a shaft Drive wheel, in particular a camshaft of an internal combustion engine, according to the Genus of the main claim.
  • Such a device is known for example from WO 95/31633.
  • This cell wheel is over a Chain or belt drive driven by the crankshaft of an internal combustion engine.
  • the pressurization of the respective pressure rooms takes place via an as 4/3-way valve designed control valve, via which the pressure chambers in dependence of the desired change in rotational position with a pressure medium pump or Pressure medium tank are connected. This leads to one of these control valves Pressure line to all pressure chambers acting in the same direction.
  • a hydraulically unlockable check valve is arranged, the locking effect can be canceled by the pressure in the other pressure line.
  • These check valves can be used in the neutral position of the control valve Neglecting the leakage losses a hydraulic clamping of the two relative rotatable components can be achieved.
  • such a facility is relatively complex. In addition, it may be due to the adjustment process the almost unthrottled connection of one pressure chamber group to the Pressure medium tank for unwanted position deviations and inaccurate or fluctuating adjustment processes come.
  • US-A 4,858,572 is also a device for changing the rotational position known in which an inner part is rotatably connected to the end of the camshaft and has on its outside a plurality of radial slots distributed over the circumference, in which wing elements are guided radially.
  • This inner part is made by surround a cellular wheel, which has several hydraulically loadable cells, through the wings in two pressure chambers acting against each other be divided. By pressurizing these pressure rooms in Depending on the pressure difference, the cellular wheel relative to the inner part and thus to Camshaft can be turned.
  • These pistons are made by Compression spring elements in the direction of the inner part and are in the opposite direction can be moved by hydraulic loading of the holes in the inner ring.
  • This spring-loaded piston should the device in one of its two end positions be locked as long as the pressure is applied to the pressure chambers defined level not reached. Only when a certain pressure level is reached the pistons are pushed back against the action of the compression springs and allow the inner part to be rotated relative to the cellular wheel.
  • the device is said to make rattling noises when starting up Internal combustion engine can be avoided by changing moment loads can occur during startup and operation of the internal combustion engine.
  • the invention is based on the object, the generic Device for changing the relative rotational position of a shaft to the drive wheel in this regard to improve that this is simple and inexpensive and a fluctuation-free change of the rotation position enables. It should focus on the The use of several complex and expensive control valves can be dispensed with.
  • the device when the engine is at a standstill and in stationary operation the device allows a single-acting hydraulic lock.
  • a damping or throttling acting on the entire adjustment process Drain side is reached when the control cross-section to the pressure medium tank during the adjustment process is always smaller than the opening cross-section to the pressure medium pump is.
  • a particularly advantageous and inexpensive training of the device for relative change in rotational position results when both the inlet control and the Sequence control for the assigned direction of rotation via a common valve element of the control valve is controlled.
  • Such a device for the relative change in rotational position is again Simplified or less expensive if the rotation position change for both directions a common control valve or a common valve member can be used.
  • the control valve can in a particularly advantageous manner as a 4/3-way valve be formed, which for the inflow and outflow control for both Valve member acting in the direction of rotation is designed as a valve slide.
  • 1 denotes the camshaft of an internal combustion engine the end of a device known for example from DE 39 37 644 A1 hydraulic rotation angle adjustment of the camshaft relative to its drive wheel or is arranged to the crankshaft.
  • This adjustment device 2 has a rotationally fixed with the Camshaft connected inner part 3, which is provided with radial webs 4. This divide the cells of a cellular wheel 5, delimited by radial webs 6, into each two opposing pressure rooms.
  • the cellular wheel 5 is also the drive wheel and for example with a chain drive or belt drive with the crankshaft Internal combustion engine connected. By pressurizing the Pressure chambers can be connected to the camshaft 1 inner part 3 relative to Cell wheel 5 are rotated so that the phase position of the gas exchange valves change the actuating cam.
  • the hydraulic control of the pressure chambers takes place via two in the camshaft Separately formed pressure channels 7 and 8, the two in one Camshaft bearings 9 formed ring grooves 9 and 10 each with a control line 11 and 12 are connected.
  • the two control lines 11 and 12 are with one Control valve 13 connected, in this embodiment as a 4/3-way valve is trained.
  • the connection of the control valve 13 to the control line 11 is A designated, the connection to the control line 12 with B.
  • the control valve 13 has a pressure port P and a return port T on.
  • the pressure port P is via a pressure line 14 and a check valve 15 with the pressure medium source serving lubricant pump 16 of the internal combustion engine connected. This is in turn via a suction line with the oil storage tank 17 or the oil pan Internal combustion engine connected.
  • the return port T of the control valve 13 is also connected to this oil storage tank 17.
  • the control valve 13 designed as a 4/3-way proportional valve has a valve housing 18 with a valve bore 19, the five mutually spaced ring grooves is surrounded. These five ring grooves are in the arrangement shown in FIG continuously designated 20 to 24 from left to right.
  • the ring grooves 20 and 24 are connected to the return port T in a manner known per se.
  • the ring groove 21 is connected to the pressure port B, while the annular groove 23 with the Pressure port A is connected.
  • the central annular groove 22 is connected to the pressure connection P connected.
  • In the valve bore 19 is a sealing and longitudinally displaceable as Control piston formed valve member 25 out.
  • the length of the Piston sections 26 and 27 is selected so that the overlap of the annular grooves 21st and 23 is significantly larger on the end face facing away from the pressure connection P. Becomes the valve member 25 from the neutral position II shown in FIG. 2, for example shifted to the right in switching position I, the pressure port P facing Area of the annular groove 23 no longer covered by the piston section 27 or Approved. On the opposite side is due to the greater coverage the annular groove 21 is still completely covered by the piston section 26. At the start the adjustment process can thus be assigned to the pressure port B pressure chamber are applied without the opposite, the pressure connection A assigned pressure chamber is relieved.

Description

Die Erfindung betrifft eine Einrichtung zur relativen Drehlagenänderung einer Welle zum Antriebsrad, insbesondere einer Nockenwelle einer Brennkraftmaschine, nach der Gattung des Hauptanspruches.The invention relates to a device for the relative change in the rotational position of a shaft Drive wheel, in particular a camshaft of an internal combustion engine, according to the Genus of the main claim.

Eine derartige Einrichtung ist beispielsweise aus der WO 95/31633 bekannt. Diese beschreibt eine Einrichtung zur Drehlagenänderung der Nockenwelle einer Brennkraftmaschine, wobei die Nockenwelle drehfest mit einem Innenrad verbunden ist, das radiale Stege aufweist, die zugeordnete Zellen eines Zellenrades in jeweils zwei gegeneinander wirkende Druckräume unterteilt. Dieses Zellenrad wird über einen Ketten- bzw. Riementrieb von der Kurbelwelle einer Brennkraftmaschine angetrieben. Die Druckbeaufschlagung der jeweiligen Druckräume erfolgt dabei über ein als 4/3-Wegeventil ausgebildetes Steuerventil, über das die Druckräume in Abhängigkeit von der erwünschten Drehlagenänderung mit einer Druckmittelpumpe bzw. einem Druckmitteltank verbunden sind. Dazu führt von diesem Steuerventil jeweils eine Druckleitung zu allen gleichsinnig wirkenden Druckräumen. In diesen Druckleitungen ist darüber hinaus jeweils ein hydraulisch entsperrbares Rückschlagventil angeordnet, dessen Sperrwirkung jeweils vom Druck in der anderen Druckleitung aufhebbar ist. Über diese Rückschlagventile kann in der Neutralstellung des Steuerventils bei Vernachlässigung der Leckage-Verluste eine hydraulische Klemmung der beiden relativ zueinander verdrehbaren Bauteile erzielt werden. Eine derartige Einrichtung ist jedoch relativ aufwendig. Darüber hinaus kann es während des Verstellvorganges aufgrund der nahezu ungedrosselten Verbindung der einen Druckraumgruppe zum Druckmitteltank zu ungewollten Lageabweichungen und ungenauen bzw. schwankenden Verstellvorgängen kommen. Such a device is known for example from WO 95/31633. This describes a device for changing the rotational position of the camshaft Internal combustion engine, wherein the camshaft is rotatably connected to an inner wheel is, which has radial webs, the associated cells of a cellular wheel in each subdivided two opposing pressure rooms. This cell wheel is over a Chain or belt drive driven by the crankshaft of an internal combustion engine. The pressurization of the respective pressure rooms takes place via an as 4/3-way valve designed control valve, via which the pressure chambers in dependence of the desired change in rotational position with a pressure medium pump or Pressure medium tank are connected. This leads to one of these control valves Pressure line to all pressure chambers acting in the same direction. In these pressure lines in addition, a hydraulically unlockable check valve is arranged, the locking effect can be canceled by the pressure in the other pressure line. These check valves can be used in the neutral position of the control valve Neglecting the leakage losses a hydraulic clamping of the two relative rotatable components can be achieved. However, such a facility is relatively complex. In addition, it may be due to the adjustment process the almost unthrottled connection of one pressure chamber group to the Pressure medium tank for unwanted position deviations and inaccurate or fluctuating adjustment processes come.

Aus der US-A 4,858,572 ist darüber hinaus eine Einrichtung zur Drehlagenänderung bekannt, bei der ein Innenteil drehfest mit dem Ende der Nockenwelle verbunden ist und an seiner Außenseite mehrere über den Umfang verteilte radiale Schlitze aufweist, in denen Flügelelemente radial verschieblich geführt sind. Dieses Innenteil wird von einem Zellenrad umgeben, das mehrere hydraulisch beaufschlagbare Zellen aufweist, die durch die Flügel in zwei gegeneinander auf diese einwirkende Druckräume unterteilt werden. Durch Druckbeaufschlagung dieser Druckräume kann in Abhängigkeit von der Druckdifferenz das Zellenrad relativ zum Innenteil und damit zur Nockenwelle verdreht werden. Darüber hinaus ist im Zellenrad in zwei radialen Bohrungen in definierten Winkellagen jeweils ein hydraulisch beaufschlagbarer Kolben geführt, der in der zugeordneten Endlage der Vorrichtung in eine radiale Vertiefung des Innenteils eingeschoben werden kann. Diese Kolben werden durch Druckfederelemente in Richtung Innenteil beaufschlagt und sind in Gegenrichtung durch hydraulische Beaufschlagung der Bohrungen im Innenring verschiebbar. Durch diese federbeaufschlagten Kolben soll die Vorrichtung in einer ihrer beiden Endlagen verriegelt werden, so lange der Druck zur Beaufschlagung der Druckräume ein definiertes Niveau nicht erreicht. Erst bei Erreichen eines bestimmten Druckniveaus werden die Kolben gegen die Wirkung der Druckfedern zurückgeschoben und ermöglichen ein Verdrehen des Innenteils relativ zum Zellenrad. Mit einer derartigen Vorrichtung sollen unter anderem Klappergeräusche beim Anlauf der Brennkraftmaschine vermieden werden, die durch wechselnde Momentenbelastungen beim Anlauf und Betrieb der Brennkraftmaschine auftreten können.From US-A 4,858,572 is also a device for changing the rotational position known in which an inner part is rotatably connected to the end of the camshaft and has on its outside a plurality of radial slots distributed over the circumference, in which wing elements are guided radially. This inner part is made by surround a cellular wheel, which has several hydraulically loadable cells, through the wings in two pressure chambers acting against each other be divided. By pressurizing these pressure rooms in Depending on the pressure difference, the cellular wheel relative to the inner part and thus to Camshaft can be turned. It is also in the radial in two radial Bores in defined angular positions each have a hydraulically actuated piston performed, in the assigned end position of the device in a radial recess of the inner part can be inserted. These pistons are made by Compression spring elements in the direction of the inner part and are in the opposite direction can be moved by hydraulic loading of the holes in the inner ring. By this spring-loaded piston should the device in one of its two end positions be locked as long as the pressure is applied to the pressure chambers defined level not reached. Only when a certain pressure level is reached the pistons are pushed back against the action of the compression springs and allow the inner part to be rotated relative to the cellular wheel. With such a Among other things, the device is said to make rattling noises when starting up Internal combustion engine can be avoided by changing moment loads can occur during startup and operation of the internal combustion engine.

Der Erfindung liegt demgegenüber die Aufgabe zugrunde, die gattungsgemäße Einrichtung zur relativen Drehlagenänderung einer Welle zum Antriebsrad dahingehend zu verbessern, daß diese einfacher und kostengünstiger aufgebaut ist und eine schwankungsfreie Drehlagenänderung ermöglicht. Dabei soll vor allem auf die Verwendung mehrerer aufwendiger und teurer Steuerventile verzichtet werden. The invention is based on the object, the generic Device for changing the relative rotational position of a shaft to the drive wheel in this regard to improve that this is simple and inexpensive and a fluctuation-free change of the rotation position enables. It should focus on the The use of several complex and expensive control valves can be dispensed with.

Darüber hinaus soll bei Stillstand der Brennkraftmaschine und im stationären Betrieb der Einrichtung eine einfach wirkende hydraulische Verriegelung ermöglicht werden.In addition, when the engine is at a standstill and in stationary operation the device allows a single-acting hydraulic lock.

Diese Aufgabe wird erfindungsgemäß mit den kennzeichnenden Merkmalen des Hauptanspruches gelöst.This object is achieved with the characterizing features of Main claim solved.

Dadurch daß bei der Einleitung des Verstellvorganges der eine Druckraum mit der Druckmittelpumpe verbunden wird bevor der andere, entgegengerichtet wirksame mit dem Druckmitteltank verbunden wird, wird verhindert, daß der Druckabfall auf der zu entlastenden Seite schneller erfolgt als der Druckanstieg auf der gegenüberliegenden Seite. Dadurch ergibt sich eine Dämpfung bzw. Drosselung auf der Ablaufseite, durch die eine gegenüber dem Druckanstieg vorauseilende Verstellung verhindert wird. Der Verstellvorgang wird damit gedämpft bzw. genauer. Eine derartige Steuerung der Druckbeaufschlagung bzw. Druckentlastung ermöglicht den Verzicht auf aufwendige Dämpfungsmittel und ermöglicht auf einfache Weise ein kontrollierte Ansteuerung bzw. kontrollierte Umsetzung der Verstellbewegung als Folge der Druckansteuerung.Characterized in that when initiating the adjustment process the one pressure chamber with the Pressure medium pump is connected before the other, counter-effective with the pressure medium tank is connected, the pressure drop on the is prevented relieving side occurs faster than the pressure increase on the opposite Page. This results in damping or throttling on the outlet side which prevents an advance in relation to the pressure increase. The The adjustment process is dampened or more precisely. Such control of Pressurization or pressure relief enables the elimination of complex Damping means and enables controlled activation or controlled implementation of the adjustment movement as a result of the pressure control.

Eine über den gesamten Verstellvorgang wirkende Dämpfung bzw. Drosselung auf der Ablaufseite wird erreicht, wenn der Steuerquerschnitt zum Druckmitteltank während des Verstellvorganges stets kleiner als der Öffnungsquerschnitt zur Druckmittelpumpe ist. Dadurch wird über den gesamten Verstellvorgang ein Vorauseilen gegenüber dem Druckanstieg verhindert, so daß über den gesamten Verstellvorgang eine sehr genaue Lagezuordnung und eine weitgehend schwankungsfreie Verstellung möglich ist.A damping or throttling acting on the entire adjustment process Drain side is reached when the control cross-section to the pressure medium tank during the adjustment process is always smaller than the opening cross-section to the pressure medium pump is. As a result, there is an advance over the entire adjustment process Prevents pressure rise, so that a very accurate over the entire adjustment process Location assignment and a largely fluctuation-free adjustment is possible.

Eine besonders vorteilhafte und kostengünstige Ausbildung der Einrichtung zur relativen Drehlagenänderung ergibt sich, wenn sowohl die Zulaufsteuerung als auch die Ablaufsteuerung für die zugeordnete Drehrichtung über ein gemeinsames Ventilglied des Steuerventils gesteuert wird. A particularly advantageous and inexpensive training of the device for relative change in rotational position results when both the inlet control and the Sequence control for the assigned direction of rotation via a common valve element of the control valve is controlled.

Eine derartige Einrichtung zur relativen Drehlagenänderung wird noch einmal vereinfacht bzw. kostengünstiger, wenn für beide Richtungen der Drehlagenänderung ein gemeinsames Steuerventil bzw. ein gemeinsames Ventilglied genutzt werden.Such a device for the relative change in rotational position is again Simplified or less expensive if the rotation position change for both directions a common control valve or a common valve member can be used.

Das Steuerventil kann dabei auf besonders vorteilhafte Weise als 4/3-Wegeventil ausgebildet sein, wobei das für die Zulauf- und Ablaufsteuerung für beide Drehrichtungen wirkende Ventilglied als Ventilschieber ausgebildet ist.The control valve can in a particularly advantageous manner as a 4/3-way valve be formed, which for the inflow and outflow control for both Valve member acting in the direction of rotation is designed as a valve slide.

Weitere Vorteile und vorteilhafte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen und der Beschreibung.Further advantages and advantageous developments of the invention result from the Subclaims and the description.

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert. Letztere zeigt in

Fig. 1
eine schematische Darstellung der Druckmittelversorgung für einen phasenveränderbaren Nockenwellenantrieb und in
Fig. 2
eine schematische Darstellung des Steuerventils.
An embodiment of the invention is explained in more detail in the following description and drawing. The latter shows in
Fig. 1
a schematic representation of the pressure medium supply for a phase-changeable camshaft drive and in
Fig. 2
a schematic representation of the control valve.

In der Zeichnung ist mit 1 die Nockenwelle einer Brennkraftmaschine bezeichnet, an der endseitig eine beispielsweise aus der DE 39 37 644 A1 bekannte Vorrichtung zur hydraulischen Drehwinkelverstellung der Nockenwelle relativ zu ihrem Antriebsrad bzw. zur Kurbelwelle angeordnet ist. Diese Verstellvorrichtung 2 hat ein drehfest mit der Nockenwelle verbundenes Innenteil 3, das mit radialen Stegen 4 versehen ist. Diese unterteilen die durch radiale Stege 6 begrenzten Zellen eines Zellenrades 5 in jeweils zwei gegensinnig wirkende Druckräume. Das Zellenrad 5 ist gleichzeitig Antriebsrad und beispielsweise mit einem Kettentrieb oder Riementrieb mit der Kurbelwelle der Brennkraftmaschine verbunden. Durch entsprechende Druckbeaufschlagung der Druckräume kann das mit der Nockenwelle 1 verbundene Innenteil 3 relativ zum Zellenrad 5 verdreht werden, so daß sich die Phasenlage der die Gaswechselventile betätigenden Nocken ändern.In the drawing, 1 denotes the camshaft of an internal combustion engine the end of a device known for example from DE 39 37 644 A1 hydraulic rotation angle adjustment of the camshaft relative to its drive wheel or is arranged to the crankshaft. This adjustment device 2 has a rotationally fixed with the Camshaft connected inner part 3, which is provided with radial webs 4. This divide the cells of a cellular wheel 5, delimited by radial webs 6, into each two opposing pressure rooms. The cellular wheel 5 is also the drive wheel and for example with a chain drive or belt drive with the crankshaft Internal combustion engine connected. By pressurizing the Pressure chambers can be connected to the camshaft 1 inner part 3 relative to Cell wheel 5 are rotated so that the phase position of the gas exchange valves change the actuating cam.

Die hydraulische Ansteuerung der Druckräume erfolgt über zwei in der Nockenwelle getrennt voneinander ausgebildeten Druckkanäle 7 und 8, die über zwei in einem Nockenwellenlager 9 ausgebildete Ringnuten 9 und 10 jeweils mit einer Steuerleitung 11 bzw. 12 verbunden sind. Die beiden Steuerleitungen 11 und 12 sind mit einem Steuerventil 13 verbunden, das in diesem Ausführungsbeispiel als 4/3-Wegeventil ausgebildet ist. Der Anschluß des Steuerventils 13 an die Steuerleitung 11 ist mit A bezeichnet, der Anschluß an die Steuerleitung 12 mit B. Das Steuerventil 13 weist einen Druckanschluß P und einen Rücklaufanschluß T auf. Der Druckanschluß P ist über eine Druckleitung 14 und ein Rückschlagventil 15 mit der als Druckmittelquelle dienenden Schmiermittelpumpe 16 der Brennkraftmaschine verbunden. Diese wiederum ist über eine Saugleitung mit dem Ölvorratstank 17 bzw. der Ölwanne der Brennkraftmaschine verbunden. Der Rücklaufanschluß T des Steuerventils 13 ist ebenfalls mit diesem Ölvorratstank 17 verbunden.The hydraulic control of the pressure chambers takes place via two in the camshaft Separately formed pressure channels 7 and 8, the two in one Camshaft bearings 9 formed ring grooves 9 and 10 each with a control line 11 and 12 are connected. The two control lines 11 and 12 are with one Control valve 13 connected, in this embodiment as a 4/3-way valve is trained. The connection of the control valve 13 to the control line 11 is A designated, the connection to the control line 12 with B. The control valve 13 has a pressure port P and a return port T on. The pressure port P is via a pressure line 14 and a check valve 15 with the pressure medium source serving lubricant pump 16 of the internal combustion engine connected. This is in turn via a suction line with the oil storage tank 17 or the oil pan Internal combustion engine connected. The return port T of the control valve 13 is also connected to this oil storage tank 17.

In der Neutralstellung II des Steuerventils 13 sind sowohl die Druckleitung 14 als auch der Rücklaufanschluß T und die beiden Steuerleitungen 11 und 12 ventilseitig verschlossen. In der Schaltstellung I des Steuerventils 13 ist die Druckleitung 14 mit der Steuerleitung 11 verbunden (P -> B). Die Steuerleitung 12 wiederum ist über den Rücklaufanschluß T mit dem Ölvorratstank 17 verbunden (A ->T). In der Schaltstellung III des Steuerventils 13 ist die Druckleitung 14 mit der Steuerleitung 12 verbunden (P -> A), während die Steuerleitung 11 zum Ölvorratstank 17 geöffnet ist (B -> T). In den beiden Schaltstellungen I und III des Steuerventils 13 erfolgt aufgrund der in den jeweils angeschlossenen Druckräumen vorherrschenden Druckdifferenzen eine Verdrehung des Innenteils relativ zum Zellenrad. Dabei erfolgt beispielsweise in der Schaltstellung I eine Verdrehung des Innenteils relativ zum Zellenrad im Uhrzeigersinn, während in der Schaltstellung III die relative Verdrehung entgegen dem Uhrzeigersinn erfolgt. In der Neutralstellung II wird die relative Position der beiden verdrehbaren Bauteile der Verstelleinrichtung durch die hydraulische Einspannung beibehalten bzw. festgelegt.In the neutral position II of the control valve 13, both the pressure line 14 and the return port T and the two control lines 11 and 12 on the valve side locked. In the switching position I of the control valve 13, the pressure line 14 is included the control line 11 connected (P -> B). The control line 12 is in turn on the Return port T connected to the oil storage tank 17 (A -> T). In the switch position III of the control valve 13, the pressure line 14 is connected to the control line 12 (P -> A), while the control line 11 to the oil storage tank 17 is open (B -> T). In the two switching positions I and III of the control valve 13 takes place due to the in prevailing pressure differences in each connected pressure chamber Rotation of the inner part relative to the cell wheel. For example, in the Switch position I a rotation of the inner part relative to the cell wheel clockwise, while in switch position III the relative rotation counterclockwise he follows. In the neutral position II, the relative position of the two is rotatable Retain components of the adjustment device through the hydraulic clamping or established.

Das als 4/3-Proportionalwegeventil ausgebildete Steuerventil 13 hat ein Ventilgehäuse 18 mit einer Ventilbohrung 19, die von fünf zueinander beabstandeten Ringnuten umgeben ist. Diese fünf Ringnuten sind in der in Fig. 2 dargestellten Anordnung von links nach rechts fortlaufend mit 20 bis 24 bezeichnet. Die Ringnuten 20 und 24 sind dabei auf an sich bekannte Weise mit dem Rücklaufanschluß T verbunden. Die Ringnut 21 ist mit dem Druckanschluß B verbunden, während die Ringnut 23 mit dem Druckanschluß A verbunden ist. Die mittlere Ringnut 22 ist mit dem Druckanschluß P verbunden. In der Ventilbohrung 19 ist dichtend und längsverschieblich ein als Steuerkolben ausgebildetes Ventilglied 25 geführt. Dieses Ventilglied 25 hat zwei beabstandete, dichtend in der Ventilbohrung 19 geführte Kolbenabschnitte 26 und 27, die über einen Kolbenabschnitt 28 geringeren Durchmessers miteinander verbunden sind. Durch die beiden Kolbenabschnitte 26 und 27 wird der zwischen dem Kolbenabschnitt 25 und der Wandung der Ventilbohrung 19 ausgebildete Ringraum 29 abgeschlossen. Die Länge des Kolbenabschnittes 25 und die Länge der Kolbenabschnitt 26 und 27 sind so auf die Breite und Abstände der Ringnuten 20 bis 24 abgestimmt, daß in der Neutralstellung II des Steuerventils 13 die Ringnuten 21 und 23 durch den Kolbenabschnitt 26 bzw. 27 dicht verschlossen sind. Der Abstand der beiden einander zugewandten Stirnseiten der Kolbenabschnitte 26 und 27 ist dabei um ein für die sichere Abdichtung erforderliches Maß kleiner als der Abstand der einander zugewandten Seiten der Ringnuten 21 und 23. Die Länge der Kolbenabschnitte 26 und 27 ist so gewählt, daß die Überdeckung der Ringnuten 21 und 23 auf der dem Druckanschluß P abgewandten Stirnseite deutlich größer ist. Wird das Ventilglied 25 aus der in Fig. 2 dargestellten Neutralstellung II beispielsweise nach rechts in Schaltstellung I verschoben, wird der dem Druckanschluß P zugewandte Bereich der Ringnut 23 vom Kolbenabschnitt 27 nicht mehr überdeckt bzw. freigegeben. Auf der gegenüberliegenden Seite wird durch die größere Überdeckung die Ringnut 21 noch vollständig durch den Kolbenabschnitt 26 überdeckt. Zu Beginn des Verstellvorganges kann somit der dem Druckanschluß B zugeordnete Druckraum beaufschlagt werden, ohne daß der gegenüberliegende, dem Druckanschluß A zugeordnete Druckraum entlastet wird. Erst wenn das Ventilglied 25 weiter nach rechts verschoben wird, wird auch die Ringnut 21 auf der der Ringnut 20 zugewandten Seite nicht mehr vom Kolbenabschnitt 26 überdeckt bzw. von diesem freigegeben, so daß die Verbindung A nach T geöffnet wird. Die Abmessungen und Abstände der Ringnuten sind dabei so auf die Abmessung des Ventilgliedes abgestimmt, daß der Öffnungsquerschnitt - beim Verschieben des Ventilgliedes nach rechts - an der Ringnut 23 stets größer als an der Ringnut 21 ist (Ablaufkantensteuerung). Wird das Ventilglied 25 in analoger Weise aus der Neutralstellung II nach links in die Schaltstellung III verschoben, wird die dem Druckanschluß P zugewandte Seite der Ringnut 21 nicht mehr vom Kolbenabschnitt 26 überdeckt. Der Kolbenabschnitt 27 dichtet andererseits aufgrund der größeren Überdeckung die Ringnut 23 dabei noch vollständig ab. Erst wenn das Ventilglied 25 weiter nach links verschoben wird, wird die Ringnut 23 in analoger Weise auf der der Ringnut 24 zugewandten Seite nicht mehr überdeckt. Auch hier ist der Öffnungsquerschnitt der Ringnut 21 - bei einer Verschiebung des Ventilgliedes 25 nach links - stets größer als der an der Ringnut 23.The control valve 13 designed as a 4/3-way proportional valve has a valve housing 18 with a valve bore 19, the five mutually spaced ring grooves is surrounded. These five ring grooves are in the arrangement shown in FIG continuously designated 20 to 24 from left to right. The ring grooves 20 and 24 are connected to the return port T in a manner known per se. The ring groove 21 is connected to the pressure port B, while the annular groove 23 with the Pressure port A is connected. The central annular groove 22 is connected to the pressure connection P connected. In the valve bore 19 is a sealing and longitudinally displaceable as Control piston formed valve member 25 out. This valve member 25 has two spaced-apart piston sections 26 and 27 which are sealingly guided in the valve bore 19, which are interconnected via a piston section 28 of smaller diameter are. The two piston sections 26 and 27 between the Piston section 25 and the wall of the valve bore 19 formed annular space 29 completed. The length of the piston portion 25 and the length of the Piston sections 26 and 27 are so on the width and spacing of the annular grooves 20 to 24 coordinated that in the neutral position II of the control valve 13, the annular grooves 21st and 23 are sealed by the piston section 26 and 27, respectively. The distance of the two mutually facing end faces of the piston sections 26 and 27 thereby by an amount necessary for the secure sealing smaller than the distance of the mutually facing sides of the ring grooves 21 and 23. The length of the Piston sections 26 and 27 is selected so that the overlap of the annular grooves 21st and 23 is significantly larger on the end face facing away from the pressure connection P. Becomes the valve member 25 from the neutral position II shown in FIG. 2, for example shifted to the right in switching position I, the pressure port P facing Area of the annular groove 23 no longer covered by the piston section 27 or Approved. On the opposite side is due to the greater coverage the annular groove 21 is still completely covered by the piston section 26. At the start the adjustment process can thus be assigned to the pressure port B pressure chamber are applied without the opposite, the pressure connection A assigned pressure chamber is relieved. Only when the valve member 25 continues after is shifted to the right, the annular groove 21 is also facing the annular groove 20 Side no longer covered by the piston section 26 or released by this, so that the connection A to T is opened. The dimensions and distances of the Ring grooves are matched to the dimension of the valve member so that the Opening cross-section - when moving the valve member to the right - on the ring groove 23 is always larger than at the annular groove 21 (drain edge control). Becomes the valve member 25 in an analogous manner from the neutral position II to the left in the switching position III moved, the side of the annular groove 21 facing the pressure port P is not more covered by the piston section 26. The piston section 27 seals on the other hand due to the greater coverage, the annular groove 23 is still completely off. First if the valve member 25 is moved further to the left, the annular groove 23 in analogously no longer covered on the side facing the annular groove 24. Also here is the opening cross section of the annular groove 21 - when the Valve member 25 to the left - always larger than that on the annular groove 23.

Claims (5)

  1. A device for changing the rotational position of a shaft (1) relative to the driving wheel (5), in particular of a camshaft of an internal-combustion engine, having an adjustment device (3) with two pressure chambers acting contrary to each other, having a pressure-medium pump (16), a pressure-medium tank (17) and at least one control valve (13), wherein one pressure chamber is connected to the pressure-medium pump (16) and the other pressure chamber is connected to the pressure-medium tank (17) during the adjustment procedure, characterized in that at the beginning of an adjustment procedure one pressure chamber is connected to the pressure-medium pump (16) before the other is connected to the pressure-medium tank (17).
  2. A device for changing the rotational position of a shaft relative to the driving wheel according to Claim 1, characterized in that the control cross-section of the connexion (23, 24; 21, 20) of one pressure chamber to the pressure-medium tank during the adjustment procedure is always smaller than the opening cross-section of the connexion (21, 22; 22, 23) of the other pressure chamber to the pressure-medium pump (17).
  3. A device for changing the rotational position of a shaft relative to the driving wheel according to Claim 1 or 2, characterized in that the control cross-section of the connexion (23, 24; 21, 20) of one pressure chamber to the pressure-medium tank and the control cross-section (21, 22; 22, 23) of the connexion of the other pressure chamber to the pressure-medium pump are controlled by way of a common valve member (25) of the control valve (13).
  4. A device for changing the rotational position of a shaft relative to the driving wheel according to Claim 3, characterized in that a common valve member (25) of a control valve (13) is used for the two directions of the change in the rotational position.
  5. A device for changing the rotational position of a shaft relative to the driving wheel according to one of the preceding Claims, characterized in that the control valve is constructed in the form of a 4/3 proportional-way valve (13).
EP99917979A 1998-05-27 1999-04-14 Device for changing the relative rotational position of a shaft to the drive wheel Revoked EP1025343B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP03009907.1A EP1331367B1 (en) 1998-05-27 1999-04-14 Actuating device for relative angular position changing between a shaft and a driving wheel, in particular for a camshaft in an internal combustion engine

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19823619 1998-05-27
DE19823619A DE19823619A1 (en) 1998-05-27 1998-05-27 Device for changing the relative rotational position of a shaft to the drive wheel
PCT/EP1999/002505 WO1999061759A1 (en) 1998-05-27 1999-04-14 Device for changing the relative rotational position of a shaft to the drive wheel

Related Child Applications (1)

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EP03009907.1A Division EP1331367B1 (en) 1998-05-27 1999-04-14 Actuating device for relative angular position changing between a shaft and a driving wheel, in particular for a camshaft in an internal combustion engine

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EP1025343A1 EP1025343A1 (en) 2000-08-09
EP1025343B1 true EP1025343B1 (en) 2003-07-16

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EP03009907.1A Expired - Lifetime EP1331367B1 (en) 1998-05-27 1999-04-14 Actuating device for relative angular position changing between a shaft and a driving wheel, in particular for a camshaft in an internal combustion engine
EP99917979A Revoked EP1025343B1 (en) 1998-05-27 1999-04-14 Device for changing the relative rotational position of a shaft to the drive wheel

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US (1) US6209497B1 (en)
EP (2) EP1331367B1 (en)
JP (1) JP2002516947A (en)
KR (1) KR100530825B1 (en)
CN (1) CN1100197C (en)
DE (2) DE19823619A1 (en)
ES (1) ES2204124T3 (en)
WO (1) WO1999061759A1 (en)

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DE102007035671A1 (en) 2007-07-27 2009-01-29 Hydraulik-Ring Gmbh Oscillating motor phase adjuster for changing control time of valve controller of four-stroke engine, has reverse spring device arranged in pressure chamber that is subjected to pressure, in axial direction
DE102007035672A1 (en) 2007-07-27 2009-01-29 Hydraulik-Ring Gmbh Cam-shaft actuator for use in internal combustion engine i.e. four-stroke engine, has control channel provided in chamber related to one rotary direction, and another control channel provided in chamber related to another rotary direction
DE102007041552A1 (en) 2007-08-31 2009-03-05 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007042046A1 (en) 2007-09-05 2009-03-12 Hydraulik-Ring Gmbh Drive motor, has camshaft adjuster with electromagnetic hydraulic valve, and housing with form fit engaging region and thread for screwing valve with solid casting or forging housing part of motor
DE102007056685A1 (en) 2007-11-24 2009-05-28 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007056683A1 (en) 2007-11-24 2009-05-28 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007057882A1 (en) 2007-11-29 2009-06-10 Hydraulik-Ring Gmbh Electrohydraulic valve e.g. 4/3-way-Valve, for controlling vane cell- cam shaft controller, has additional coil provided to coil in axial movable manner along longitudinal axis, and anchor arranged in additional coil
DE102011051656A1 (en) 2011-07-07 2013-01-10 Hydraulik-Ring Gmbh Slew motor adjuster for internal combustion engine, has rotor rotatably connected with camshaft, where rotor is pivotable in opposite set pivot direction against stator and hydraulic piston that is displaceable within guide bore

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DE102009022869A1 (en) * 2009-05-27 2010-12-09 Hydraulik-Ring Gmbh Vane phaser system
DE102009050779B4 (en) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller with a friction disc and mounting method
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DE102010013777A1 (en) 2010-04-03 2011-10-06 Hydraulik-Ring Gmbh Central valve for oscillating motor adjuster, has hollow piston that is guided within connector which has radial oil supply connection and two radial working connections
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DE102010023864B4 (en) 2010-06-15 2018-03-08 Hilite Germany Gmbh Central valve for a Schwenkmotornockenwellenversteller
DE102010044637A1 (en) 2010-09-07 2012-03-08 Hydraulik-Ring Gmbh Oscillating motor cam shaft adjuster has housing with hollow piston displaceable axially within housing, where borehole leads to recess that is exclusively assigned in hollow piston
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DE19853670B4 (en) * 1998-11-20 2007-07-26 Hydraulik-Ring Gmbh Camshaft adjustment device
DE19853670C5 (en) 1998-11-20 2019-01-10 Hilite Germany Gmbh Camshaft adjustment device
DE102007035672B4 (en) * 2007-07-27 2009-08-06 Hydraulik-Ring Gmbh Phaser
DE102007035671A1 (en) 2007-07-27 2009-01-29 Hydraulik-Ring Gmbh Oscillating motor phase adjuster for changing control time of valve controller of four-stroke engine, has reverse spring device arranged in pressure chamber that is subjected to pressure, in axial direction
DE102007035672A1 (en) 2007-07-27 2009-01-29 Hydraulik-Ring Gmbh Cam-shaft actuator for use in internal combustion engine i.e. four-stroke engine, has control channel provided in chamber related to one rotary direction, and another control channel provided in chamber related to another rotary direction
DE102007051407A1 (en) 2007-07-27 2009-04-30 Hydraulik-Ring Gmbh Valve and method of manufacture of a valve
DE102007035671B4 (en) * 2007-07-27 2009-08-06 Hydraulik-Ring Gmbh Schwenkmotorphasenversteller
DE102007041552A1 (en) 2007-08-31 2009-03-05 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007042046A1 (en) 2007-09-05 2009-03-12 Hydraulik-Ring Gmbh Drive motor, has camshaft adjuster with electromagnetic hydraulic valve, and housing with form fit engaging region and thread for screwing valve with solid casting or forging housing part of motor
DE102007056683A1 (en) 2007-11-24 2009-05-28 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007056685A1 (en) 2007-11-24 2009-05-28 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102007057882A1 (en) 2007-11-29 2009-06-10 Hydraulik-Ring Gmbh Electrohydraulic valve e.g. 4/3-way-Valve, for controlling vane cell- cam shaft controller, has additional coil provided to coil in axial movable manner along longitudinal axis, and anchor arranged in additional coil
DE102007057882B4 (en) * 2007-11-29 2014-03-06 Hilite Germany Gmbh Electrohydraulic valve
DE102011051656A1 (en) 2011-07-07 2013-01-10 Hydraulik-Ring Gmbh Slew motor adjuster for internal combustion engine, has rotor rotatably connected with camshaft, where rotor is pivotable in opposite set pivot direction against stator and hydraulic piston that is displaceable within guide bore

Also Published As

Publication number Publication date
EP1331367B1 (en) 2016-09-28
US6209497B1 (en) 2001-04-03
JP2002516947A (en) 2002-06-11
EP1331367A2 (en) 2003-07-30
EP1331367A3 (en) 2008-11-19
DE59906295D1 (en) 2003-08-21
ES2204124T3 (en) 2004-04-16
CN1100197C (en) 2003-01-29
KR20010022275A (en) 2001-03-15
EP1025343A1 (en) 2000-08-09
WO1999061759A1 (en) 1999-12-02
KR100530825B1 (en) 2005-11-24
CN1266473A (en) 2000-09-13
DE19823619A1 (en) 1999-12-02

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