EP1331367A2 - Actuating device for relative angular position changing between a shaft and a driving wheel, in particular for a camshaft in an internal combustion engine - Google Patents

Actuating device for relative angular position changing between a shaft and a driving wheel, in particular for a camshaft in an internal combustion engine Download PDF

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Publication number
EP1331367A2
EP1331367A2 EP03009907A EP03009907A EP1331367A2 EP 1331367 A2 EP1331367 A2 EP 1331367A2 EP 03009907 A EP03009907 A EP 03009907A EP 03009907 A EP03009907 A EP 03009907A EP 1331367 A2 EP1331367 A2 EP 1331367A2
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EP
European Patent Office
Prior art keywords
connection
pressure
valve
adjusting device
control
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EP03009907A
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German (de)
French (fr)
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EP1331367B1 (en
EP1331367A3 (en
Inventor
Bernd Niethammer
Andreas Knecht
Alfred Trzmiel
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Dr Ing HCF Porsche AG
Hilite Germany GmbH
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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
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Publication of EP1331367A3 publication Critical patent/EP1331367A3/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 an adjusting device for a device for relative Change of rotational position of a shaft to a drive wheel, in particular a camshaft an internal combustion engine, according to the preamble of claim 1.
  • An adjusting device is known (WO 95/31633) with which the rotational position of the Camshaft of an internal combustion engine can be changed.
  • the camshaft carries rotatably an inner wheel, which has radial webs, the assigned cells one Cell wheel divided into two opposing pressure chambers. This The cellular wheel is driven by the crankshaft via a chain or belt drive Internal combustion engine driven.
  • the pressurization of the respective pressure rooms takes place via a control valve designed as a 4/3-way valve, via which the Pressure rooms depending on the desired change in rotational position with a Pressure medium pump or a pressure medium tank are connected. This leads to this Control valve one pressure line each to all pressure chambers acting in the same direction.
  • each of these pressure lines is also hydraulically unlockable Check valve arranged, the blocking effect of each pressure in the other Pressure line can be canceled.
  • These check valves can be in the neutral position of the Control valve if the leakage losses are neglected, a hydraulic clamping of the two components rotatable relative to each other can be achieved.
  • Such a facility is however relatively expensive.
  • it can during the adjustment process due to the almost unthrottled connection of one pressure chamber group to the Pressure medium tank to 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 the outside a plurality of radial slots distributed over the circumference, in which wing elements are guided radially.
  • This inner part is made by one Surround cell wheel, which has several hydraulically actuated cells, which by the wings are divided into two pressure chambers acting against each other. By pressurizing these pressure spaces, depending on the Pressure difference rotates the cellular wheel relative to the inner part and thus to the camshaft become.
  • two radial bores are defined in the cellular wheel Angular positions each guided a hydraulically loaded piston, which in the assigned end position of the device in a radial recess of the inner part can be inserted.
  • These pistons are directed towards by compression spring elements Inner part acted upon and are in the opposite direction by hydraulic action on the Bores in the inner ring can be moved.
  • This spring-loaded piston Device can be locked in one of its two end positions, as long as the pressure to Loading of the pressure rooms did not reach a defined level. Only when reached a certain pressure level, the pistons are against the action of the compression springs pushed back and allow rotation of the inner part relative to the cellular wheel.
  • Such a device should include rattling noises when starting the 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 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 A simple-acting hydraulic locking device can be set up.
  • a damping or throttling acting on the entire adjustment process Drainage side is reached when the control cross section via the tank connection to a Pressure medium tank is always smaller than that during the adjustment process Opening cross-section of the connection of the pressure connection to the pressure medium pump.
  • a particularly advantageous and inexpensive training of the device for the relative Rotation change occurs when both the inflow control and the Sequence control for the assigned direction of rotation via a common valve member of the Control valve is controlled.
  • Such a device for the relative change in rotational position is simplified once again or less expensive if that for both directions of the change in rotational position common control valve or the common valve member can be used.
  • the control valve can in a particularly advantageous manner as a 4/3-way valve be designed, which for the inlet and outlet control for both directions of rotation acting valve member is designed as a valve slide.
  • 1 denotes the camshaft of an internal combustion engine on which At the end, a device for, for example, known 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 both the drive wheel and for example with a chain drive or belt drive with the crankshaft Internal combustion engine connected.
  • the inner part 3 connected to the camshaft 1 can have pressure spaces relative to the cellular wheel 5 are rotated so that the phase position of the gas exchange valves are actuated Change cams.
  • 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 annular grooves 9 and 10 each with a control line 11 or 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 over a Pressure line 14 and a check valve 15 with the serving as a pressure medium source Lubricant pump 16 connected to the internal combustion engine. This in turn is over a suction line with the oil storage tank 17 or the oil pan of the internal combustion engine connected.
  • the return port T of the control valve 13 is also with this Oil storage tank 17 connected.
  • This valve member 25 has two spaced, sealing in the Valve bore 19 guided piston sections 26 and 27, which have a piston section 28 smaller diameter are interconnected.
  • annular space 29 Through 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 section 25 and the length of the piston section 26 and 27 are so on the Width and spacing of the ring grooves 20 to 24 matched that in the neutral position II of the control valve 13, the annular grooves 21 and 23 through the piston portion 26 and 27th are tightly closed.
  • the distance between the two facing ends of the Piston sections 26 and 27 is necessary for a secure seal Dimension smaller than the distance between the mutually facing sides of the annular grooves 21 and 23.
  • the length of the piston sections 26 and 27 is chosen so that the coverage of the Ring grooves 21 and 23 clearly on the end facing away from the pressure port P. is bigger.
  • the valve member 25 from the neutral position shown in Fig. 2 II, for example, shifted to the right in switching position I, the pressure connection P facing region of the annular groove 23 no longer covered by the piston section 27 or released.
  • the larger one Coverage of the annular groove 21 is still completely covered by the piston section 26.
  • the one assigned to the pressure connection B can thus be used Pressure chamber are applied without the opposite, the pressure connection A assigned pressure chamber is relieved.
  • the annular groove 21 is on the side facing the annular groove 20 no longer covered by the piston section 26 or released by this, so that the Connection A to T is opened.
  • the dimensions and spacing 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 - always larger than at the annular groove 23 the annular groove 21 is (drain edge control).
  • the valve member 25 is made in an analogous manner the neutral position II moved to the left in the switching position III, the Pressure port P facing side of the annular groove 21 no longer from the piston section 26 covered.
  • the piston section 27 on the other hand seals due to the larger Cover the annular groove 23 still completely.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

To commence an adjustment process, one pressure chamber is connected to the pressurised medium pump(16) before the other chamber is connected to the reservoir(17). The control flow passage of the connection of one pressure chamber to the reservoir during the adjustment process is constantly smaller than the opening flow passage of the connection of the other pressure chamber to the pump. The respective control flow passages of the two connections are controlled by a common valve component in the control valve(13).

Description

Die Erfindung betrifft eine Verstelleinrichtung für eine Einrichtung zur relativen Drehlagenveränderung einer Welle zu einem Antriebsrad, insbesondere einer Nockenwelle einer Brennkraftmaschine, nach dem Oberbegriff des Anspruches 1.The invention relates to an adjusting device for a device for relative Change of rotational position of a shaft to a drive wheel, in particular a camshaft an internal combustion engine, according to the preamble of claim 1.

Es ist eine Verstelleinrichtung bekannt (WO 95/31633), mit der die Drehlage der Nockenwelle einer Brennkraftmaschine geändert werden kann. Die Nockenwelle trägt drehfest ein Innenrad, 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.An adjusting device is known (WO 95/31633) with which the rotational position of the Camshaft of an internal combustion engine can be changed. The camshaft carries rotatably an inner wheel, which has radial webs, the assigned cells one Cell wheel divided into two opposing pressure chambers. This The cellular wheel is driven by the crankshaft via a chain or belt drive Internal combustion engine driven. The pressurization of the respective pressure rooms takes place via a control valve designed as a 4/3-way valve, via which the Pressure rooms depending on the desired change in rotational position with a Pressure medium pump or a pressure medium tank are connected. This leads to this Control valve one pressure line each to all pressure chambers acting in the same direction. In each of these pressure lines is also hydraulically unlockable Check valve arranged, the blocking effect of each pressure in the other Pressure line can be canceled. These check valves can be in the neutral position of the Control valve if the leakage losses are neglected, a hydraulic clamping of the two components rotatable relative to each other can be achieved. Such a facility is however relatively expensive. In addition, it can during the adjustment process due to the almost unthrottled connection of one pressure chamber group to the Pressure medium tank to 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 the outside a plurality of radial slots distributed over the circumference, in which wing elements are guided radially. This inner part is made by one Surround cell wheel, which has several hydraulically actuated cells, which by the wings are divided into two pressure chambers acting against each other. By pressurizing these pressure spaces, depending on the Pressure difference rotates the cellular wheel relative to the inner part and thus to the camshaft become. In addition, two radial bores are defined in the cellular wheel Angular positions each guided a hydraulically loaded piston, which in the assigned end position of the device in a radial recess of the inner part can be inserted. These pistons are directed towards by compression spring elements Inner part acted upon and are in the opposite direction by hydraulic action on the Bores in the inner ring can be moved. Through this spring-loaded piston Device can be locked in one of its two end positions, as long as the pressure to Loading of the pressure rooms did not reach a defined level. Only when reached a certain pressure level, the pistons are against the action of the compression springs pushed back and allow rotation of the inner part relative to the cellular wheel. With Such a device should include rattling noises when starting the 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 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 internal combustion engine is stationary and in stationary operation, the A simple-acting hydraulic locking device can be set up.

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

Dadurch, daß bei der Einleitung des Verstellvorganges der eine Druckraum mit der Druckmittelpumpe verbunden wird bevor der andere, entgegengerichtet wirksame mit dem Tankanschluß 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 is connected to the tank connection, the pressure drop on the is prevented relieving side occurs faster than the pressure increase on the opposite Page. This results in a damping or throttling on the outlet side through which an advance leading to the pressure increase is prevented. 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 über den Tankanschluß zu einem Druckmitteltank während des Verstellvorganges stets kleiner ist als der Öffnungsquerschnitt der Verbindung des Druckanschlusses zur Druckmittelpumpe. 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 Drainage side is reached when the control cross section via the tank connection to a Pressure medium tank is always smaller than that during the adjustment process Opening cross-section of the connection of the pressure connection to the pressure medium pump. 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 the relative Rotation change occurs when both the inflow control and the Sequence control for the assigned direction of rotation via a common valve member of the Control valve is controlled.

Eine derartige Einrichtung zur relativen Drehlagenänderung wird noch einmal vereinfacht bzw. kostengünstiger, wenn für beide Richtungen der Drehlagenänderung das gemeinsame Steuerventil bzw. das gemeinsame Ventilglied genutzt werden. Such a device for the relative change in rotational position is simplified once again or less expensive if that for both directions of the change in rotational position common control valve or the 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 designed, which for the inlet and outlet control for both directions of rotation acting valve member 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 on which At the end, a device for, for example, known 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 both the drive wheel and for example with a chain drive or belt drive with the crankshaft Internal combustion engine connected. By pressurizing the The inner part 3 connected to the camshaft 1 can have pressure spaces relative to the cellular wheel 5 are rotated so that the phase position of the gas exchange valves are actuated Change cams.

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 annular grooves 9 and 10 each with a control line 11 or 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 over a Pressure line 14 and a check valve 15 with the serving as a pressure medium source Lubricant pump 16 connected to the internal combustion engine. This in turn is over a suction line with the oil storage tank 17 or the oil pan of the internal combustion engine connected. The return port T of the control valve 13 is also with this Oil storage tank 17 connected.

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 with 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 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 both Switch positions I and III of the control valve 13 take place on the basis of the in each case prevailing pressure differences connected pressure rooms a rotation of the Inner part relative to the cellular wheel. This takes place, for example, in switch position I. Rotation of the inner part relative to the cell wheel clockwise while in the Switch position III the relative rotation takes place counterclockwise. In the Neutral position II is the relative position of the two rotatable components of the Adjustment device maintained or fixed by the hydraulic clamping.

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, which is designed as a 4/3 proportional directional control valve, has a valve housing 18 with a valve bore 19, which are surrounded by five spaced-apart annular grooves is. These five ring grooves are in the arrangement shown in Fig. 2 from left to right consecutively labeled 20 to 24 on the right. The ring grooves 20 and 24 are on known way connected to the return port T. The annular groove 21 is with the Pressure port B connected, while the annular groove 23 with the pressure port A connected is. The central annular groove 22 is connected to the pressure port P. In the Valve bore 19 is sealing and longitudinally displaceable as a control piston Valve member 25 out. This valve member 25 has two spaced, sealing in the Valve bore 19 guided piston sections 26 and 27, which have a piston section 28 smaller diameter are interconnected. Through 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 section 25 and the length of the piston section 26 and 27 are so on the Width and spacing of the ring grooves 20 to 24 matched that in the neutral position II of the control valve 13, the annular grooves 21 and 23 through the piston portion 26 and 27th are tightly closed. The distance between the two facing ends of the Piston sections 26 and 27 is necessary for a secure seal Dimension smaller than the distance between the mutually facing sides of the annular grooves 21 and 23. The length of the piston sections 26 and 27 is chosen so that the coverage of the Ring grooves 21 and 23 clearly on the end facing away from the pressure port P. is bigger. The valve member 25 from the neutral position shown in Fig. 2 II, for example, shifted to the right in switching position I, the pressure connection P facing region of the annular groove 23 no longer covered by the piston section 27 or released. On the opposite side is the larger one Coverage of the annular groove 21 is still completely covered by the piston section 26. At the beginning of the adjustment process, the one assigned to the pressure connection B can thus be used Pressure chamber are applied without the opposite, the pressure connection A assigned pressure chamber is relieved. Only when the valve member 25 continues to the right is shifted, the annular groove 21 is on the side facing the annular groove 20 no longer covered by the piston section 26 or released by this, so that the Connection A to T is opened. The dimensions and spacing 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 - always larger than at the annular groove 23 the annular groove 21 is (drain edge control). The valve member 25 is made in an analogous manner the neutral position II moved to the left in the switching position III, the Pressure port P facing side of the annular groove 21 no longer from the piston section 26 covered. The piston section 27 on the other hand seals due to the larger Cover the annular groove 23 still completely. Only when the valve member 25 is moved further to the left, the annular groove 23 is in an analogous manner on the Ring groove 24 facing side no longer covered. Here too is the Opening cross section of the annular groove 21 - after a displacement of the valve member 25 after left - always larger than that on the ring groove 23.

Claims (8)

Verstelleinrichtung (2) für eine Einrichtung zur relativen Drehlagenveränderung einer Welle (1) zu einem Antriebsrad (5), insbesondere einer Nockenwelle einer Brennkraftmaschine, mit zwei gegeneinander wirkenden Druckräumen, die über Steuerleitungen (11, 12) mit jeweils einem Anschluß (A, B) eines Steuerventils (13) verbunden sind, in dem ein Ventilglied (25) verschiebbar ist, das mimt Ventilgliedabschnitten (26, 27) versehen ist, mit denen die Anschlüsse (A, B) mit einem Druckanschluß (P) sowie einem Tankanschluß (T) verbindbar sind, dadurch gekennzeichnet, daß der eine Anschluß (A, B) zu Beginn des Verstellvorganges durch Verstellen des Ventilgliedes (25) mit dem Druckanschluß (P) verbunden wird, bevor der andere Anschluß (B, A) mit dem Tankanschluß (T) verbunden wird.Adjusting device (2) for a device for changing the relative rotational position of a shaft (1) to a drive wheel (5), in particular a camshaft of an internal combustion engine, with two pressure chambers acting against each other, which are controlled by control lines (11, 12), each with a connection (A, B ) A control valve (13) are connected, in which a valve member (25) is displaceable, which is provided with valve member sections (26, 27) with which the connections (A, B) with a pressure connection (P) and a tank connection (T ) are connectable, characterized in that one connection (A, B) is connected to the pressure connection (P) at the beginning of the adjustment process by adjusting the valve member (25) before the other connection (B, A) is connected to the tank connection (T ) is connected. Verstelleinrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Steuerquerschnitt einer Verbindung (23, 24; 21, 20) des einen Druckraumes zum Tankanschluß (T) während des Verstellvorganges stets kleiner ist als der Öffnungsquerschnitt der Verbindung (21, 22; 22, 23) des anderen Druckraumes zum Druckanschluß (P).Adjusting device according to claim 1, characterized in that the control cross section of a connection (23, 24; 21, 20) of the one pressure chamber to the tank connection (T) is always smaller than the opening cross section of the connection (21, 22; 22, 23) during the adjustment process. the other pressure chamber to the pressure connection (P). Verstelleinrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Steuerquerschnitt der Verbindung (23, 24; 21, 20) des einen Druckraumes zum Tankanschluß (T) und der Steuerquerschnitt (21, 22; 22, 23) der Verbindung des anderen Druckraumes zum Druckanschluß (P) über das gemeinsame Ventilglied (25) des Steuerventils (13) gesteuert wird.Adjusting device according to claim 1 or 2, characterized in that the control cross section of the connection (23, 24; 21, 20) of the one pressure chamber to the tank connection (T) and the control cross section (21, 22; 22, 23) of the connection of the other pressure chamber Pressure connection (P) is controlled via the common valve member (25) of the control valve (13). Verstelleinrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Verbindungen (20 bis 24) durch Ringnuten in einem Ventilgehäuse (18) gebildet sind. Adjusting device according to one of claims 1 to 3, characterized in that the connections (20 to 24) are formed by annular grooves in a valve housing (18). Verstelleinrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Ventilglied (25) für beide Richtungen der Drehlagenänderung genutzt wird.Adjusting device according to one of claims 1 to 4, characterized in that the valve member (25) is used for both directions of the change in rotational position. Verstelleinrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Steuerventil (13) ein 4/3-Proportionalwegeventil ist.Adjusting device according to one of claims 1 to 5, characterized in that the control valve (13) is a 4/3-way proportional valve. Verstelleinrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Abstand der einander zugewandten Stirnseiten der Ventilgliedabschnitte (26, 27) kleiner ist als der Abstand der einander zugewandten Seiten der mit den Anschlüssen (A, B) verbundenen Ringnuten (21, 23) des Steuerventil (13).Adjusting device according to one of Claims 1 to 6, characterized in that the distance between the mutually facing end faces of the valve member sections (26, 27) is smaller than the distance between the mutually facing sides of the annular grooves (21, 23) connected to the connections (A, B) ) of the control valve (13). Verstelleinrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß die Ventilgliedabschnitte (26, 27) eine solche Länge haben, daß die Überdeckung der mit den Anschlüssen (A, B) verbundenen Ringnuten (21, 23) auf der dem Druckanschluß (P) zugewandten Seite größer ist als auf der anderen Seite.Adjusting device according to one of claims 1 to 7, characterized in that the valve member sections (26, 27) have a length such that the overlap of the annular grooves (21, 23) connected to the connections (A, B) on the pressure connection (P ) facing side is larger than on the other side.
EP03009907.1A 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 Expired - Lifetime EP1331367B1 (en)

Applications Claiming Priority (3)

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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
EP99917979A 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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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

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ES2204124T3 (en) 2004-04-16
EP1331367B1 (en) 2016-09-28
EP1331367A3 (en) 2008-11-19
KR20010022275A (en) 2001-03-15
KR100530825B1 (en) 2005-11-24
DE59906295D1 (en) 2003-08-21
CN1100197C (en) 2003-01-29
EP1025343A1 (en) 2000-08-09
DE19823619A1 (en) 1999-12-02
WO1999061759A1 (en) 1999-12-02
JP2002516947A (en) 2002-06-11
EP1025343B1 (en) 2003-07-16
US6209497B1 (en) 2001-04-03
CN1266473A (en) 2000-09-13

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