EP0978638A1 - Phase changing device between a shaft and its driving pulley - Google Patents
Phase changing device between a shaft and its driving pulley Download PDFInfo
- Publication number
- EP0978638A1 EP0978638A1 EP99112226A EP99112226A EP0978638A1 EP 0978638 A1 EP0978638 A1 EP 0978638A1 EP 99112226 A EP99112226 A EP 99112226A EP 99112226 A EP99112226 A EP 99112226A EP 0978638 A1 EP0978638 A1 EP 0978638A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- changing
- drive wheel
- rotational position
- relative rotational
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
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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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
-
- 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
- F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
-
- 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
- F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
- F01L2001/34479—Sealing of phaser devices
-
- 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 EP 0 781 899 A1.
- 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 radially arranged wings, the associated cells of a cellular wheel in divided into two opposing pressure rooms. These are pressure rooms Hydraulically actuated via a control valve.
- the inner wheel is rotated relative to the cellular wheel.
- the radial extending walls of the cellular wheel are in the area of their radial outside Provide depressions that are provided for receiving dirt particles, the are introduced into the pressure chambers via the pressure medium.
- the one in the pressure medium located dirt particles collect depending on the direction of rotation Camshaft due to the accelerations acting on them and due to their Sluggishness essentially in one of the two depressions. This is about around the recess in relation to the direction of rotation.
- the one on the Front of the respective wing or web of the inner part Dirt particles can indeed move into the front recess due to its relative movement of the cellular wheel, but due to their inertia they will not be there remain.
- an entry of dirt particles in these Sealing area lead to a significantly excessive friction.
- the generic Adjustment device to improve that dirt particles from the Can store pressure medium in non-critical areas of the pressure rooms without the Risk of increased friction and / or increased wear in the area of the sealing surface.
- each pressure chamber several depressions are distributed over the circumference Incorporated peripheral surface, the path can be reduced in a particularly advantageous manner the dirt particles have to travel along the circumferential surface until they can be deposited in a depression.
- a particularly simple machining of the cellular wheel and a relatively large volume for the admission of dirt particles arises when the depressions are in axial Direction over the entire length of the pressure chamber.
- a particularly good sealing effect on the peripheral surface is achieved if the width of the depressions and / or the spacing of the depressions is less than 20% of the width of the adjacent web.
- a further improved sealing effect is achieved if the width and / or the The distance between the depressions is less than 10% of the width of the adjacent web.
- the sealing effect is achieved when the width of the depressions is approximately 0.5 to 1 mm.
- the depth (in the radial direction) is preferably in the range between 0.2 and 0.5 mm.
- the depressions can, for example, have a rectangular cross section exhibit. A particularly favorable execution in terms of production results if the depressions have an approximately semicircular cross section with a slightly conical shape Have opening area to the interior.
- a cellular wheel with depressions on its circumferential surface can in particular advantageous and inexpensive way to be produced as a sintered component.
- the Wells for receiving the dirt particles can then already at Sintering process can be created with. Machining the peripheral surface after Sintering is - as with components without a recess - without any additional effort or possible without further costs.
- 1 shows the camshaft of an internal combustion engine the free end of which the inner part 2 of an adjusting device 3 is arranged in a rotationally fixed manner.
- This inner part 2 is arranged in this embodiment with four radially Provide webs 4a to 4d.
- the inner part is surrounded by a cellular wheel 5, which on way not shown connected to the crankshaft of the internal combustion engine is and therefore acts as a drive wheel.
- the cellular wheel 5 is with four inwards projecting radial webs 6a to 6d, between which four cells are formed are, which by the webs of the inner part in two pressure spaces 7a to 7d and 8a are divided up to 8d.
- These pressure rooms are designed so that the sum of the hydraulically effective surfaces in both adjustment directions is the same.
- the pressure rooms 7a to 7d are each with a radial bore 9a to 9d in the inner part Annular groove 10 connected to the camshaft 1.
- the pressure spaces 8a to 8d are in analogously via radial bores 11a to 11d in the inner part with a second one Annular groove 12 connected in the camshaft.
- the annular groove 10 is with the Pressure channel 14 and the annular groove 12 connected to the pressure channel 13.
- This Pressure channels 13 and 14 are in a manner known per se via a camshaft bearing 15 each connected to a control line 16 or 17.
- the two control lines 16 and 17 are connected to a control valve 18 designed, for example, as a 4/3-way valve connected.
- This control valve 18 is on the one hand with a pressure medium pump 19 and secondly connected to an oil tank 20.
- All four connections are in the switching position II (neutral position) shown in FIG. 2 closed on one side to the control valve 18.
- the adjustment device 3 is thus hydraulically locked or clamped and keeps their ingested Position assignment of inner part and cellular wheel at.
- switch position I of the Control valve 18 the pressure chambers 7a to 7d through the holes 9a to 9d Annular groove 10, the pressure channel 14 and the line 17 from the pressure medium pump 19th acted upon.
- the pressure chambers 8a to 8d are through the bores 11a to 11d, the annular groove 12, the pressure channel 13 and the control line 16 to the oil tank 20th relieved.
- the webs 6a to 6d of the cellular wheel 5 each with their end faces sealing on the inner Circumferential surface 21 of the inner part 2.
- the webs 4a to 4d of the inner part lie with their circumferentially curved end faces 23 sealing on the inner Circumferential surface 24 of the cellular wheel 5.
- In this inner peripheral surface 24 are one A plurality of axially extending recesses 25 are incorporated. These are deepenings in this embodiment as longitudinal grooves with a rectangular cross section executed. Other cross-sectional shapes, such as Trapezoidal cross sections, Triangular cross sections or rounded cross sections are easily possible.
- the Recesses 25 extend in the axial direction over the entire width of the Pressure spaces 7a to 7d and 8a to 8d of the width B of the webs 4a to 4d, 6a to 6d. These recesses are distributed over the circumference at regular intervals.
- the width b and the distance d are chosen so that in about thirty wells are arranged in each pressure chamber. With distance d is here the distance between two adjacent side surfaces of the adjacent depressions Are defined. This distance corresponds to the width of the remaining web 26 Circumferential surface, which sealingly abuts the end face 23 of the web.
- the Width D or the arc length of the end face 23 and the width b and the distances d the wells are coordinated in this embodiment so that in each case about ten depressions 25 are covered by the end face 23.
- the width b of the depressions is included in the exemplary embodiment shown here about 0.75 mm. However, it is easily possible to determine the width b Varies between about 0.5 mm and 1 mm vary.
- the depth (in radial The direction of the depressions 25) in the exemplary embodiment shown here is approximately 0.35 mm. However, it is also easily possible to set the depth in the area to vary between about 0.2 mm and 0.5 mm.
- the wells 25 have here embodiment shown an approximately rectangular cross-section. It is however, it is also easily possible to add these recesses with an approx semicircular cross section with slightly conical opening area to the interior train there.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Pulleys (AREA)
Abstract
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 EP 0 781 899 A1 bekannt. Diese beschreibt eine Einrichtung zur Drehlagenänderung der Nockenwelle einer Brennkraftmaschine, wobei die Nockenwelle drehfest mit einem Innenrad verbunden ist, das radial angeordnete Flügel aufweist, die zugeordnete Zellen eines Zellenrades in jeweils zwei gegeneinander wirkende Druckräume unterteilt. Diese Druckräume sind über ein Steuerventil hydraulisch beaufschlagbar. In Abhängigkeit von der jeweiligen Druckbeaufschlagung wird das Innenrad relativ zum Zellenrad verdreht. Die radial verlaufenden Wände des Zellenrades sind im Bereich ihrer radialen Außenseite mit Vertiefungen versehen, die zur Aufnahme von Schmutzpartikeln vorgesehen sind, die über das Druckmittel in die Druckräume eingebracht werden. Die im Druckmittel befindlichen Schmutzpartikel sammeln sich in Abhängigkeit von der Drehrichtung der Nockenwelle aufgrund der auf sie einwirkenden Beschleunigungen und aufgrund ihrer Trägheit im wesentlichen in einer der beiden Vertiefungen an. Bei dieser handelt es sich um die jeweils in Bezug auf die Drehrichtung hintere Vertiefung. Die auf der Vorderseite des jeweiligen Flügels bzw. Steges des Innenteils befindlichen Schmutzpartikel können zwar durch dessen Relativbewegung in die vordere Vertiefung des Zellenrades gedrückt werden, aufgrund ihrer Trägheit werden sie dort jedoch nicht verbleiben. Somit besteht bei einer derartigen Verstellvorrichtung die Gefahr, daß insbesondere kleinere Schmutzpartikel in den Dichtspalt zwischen Flügel bzw. Steg und Zellenrad eindringen und zu erheblichem Verschleiß und auf Dauer nachlassender Dichtwirkung führen. Darüber hinaus kann ein Eintrag von Schmutzpartikel in diesen Dichtbereich zu einer deutlich überhöhten Reibung führen. Dies würde einen wesentlich höheren Druckbedarf zur Erzielung einer ausreichend schnellen Verstellung nach sich ziehen. Darüber hinaus erfordern derartige Vertiefungen in den Wänden zwischen den angrenzenden Zellen eine relativ große Wandstärke und liegen in einem spannungstechnisch ungünstigen Bereich. Die durch die Vertiefungen erforderliche große Wandstärke verringert demzufolge die Breite - in Umfangsrichtung - der angrenzenden Zellen, so daß insgesamt der Verstellwinkel reduziert wird.Such a device is known for example from EP 0 781 899 A1. 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 radially arranged wings, the associated cells of a cellular wheel in divided into two opposing pressure rooms. These are pressure rooms Hydraulically actuated via a control valve. Depending on the particular When pressurized, the inner wheel is rotated relative to the cellular wheel. The radial extending walls of the cellular wheel are in the area of their radial outside Provide depressions that are provided for receiving dirt particles, the are introduced into the pressure chambers via the pressure medium. The one in the pressure medium located dirt particles collect depending on the direction of rotation Camshaft due to the accelerations acting on them and due to their Sluggishness essentially in one of the two depressions. This is about around the recess in relation to the direction of rotation. The one on the Front of the respective wing or web of the inner part Dirt particles can indeed move into the front recess due to its relative movement of the cellular wheel, but due to their inertia they will not be there remain. Thus, with such an adjustment device, there is a risk that in particular smaller dirt particles in the sealing gap between the wing or web and cellular wheel penetrate and cause considerable wear and tear in the long run Lead sealing effect. In addition, an entry of dirt particles in these Sealing area lead to a significantly excessive friction. This would be essential higher pressure requirement to achieve a sufficiently fast adjustment pull. In addition, such depressions in the walls between the adjacent cells have a relatively large wall thickness and are in one unfavorable voltage range. The one required by the wells Large wall thickness therefore reduces the width - in the circumferential direction adjacent cells, so that the adjustment angle is reduced overall.
Demgegenüber ist es die Aufgabe der Erfindung, die gattungsgemäße Verstelleinrichtung dahingehend zu verbessern, daß sich Schmutzpartikel aus dem Druckmittel in unkritischen Bereichen der Druckräume ablagern können, ohne die Gefahr erhöhter Reibung und/oder erhöhten Verschleißes im Bereich der Dichtfläche.In contrast, it is the object of the invention, the generic Adjustment device to improve that dirt particles from the Can store pressure medium in non-critical areas of the pressure rooms without the Risk of increased friction and / or increased wear in the area of the sealing surface.
Diese Aufgabe wird erfindungsgemäß mit den kennzeichnenden Merkmalen des Hauptanspruches gelöst. Durch die Anordnung der Vertiefungen in der radial äußeren Umfangsfläche wird verhindert, daß sich die aufgrund der Beschleunigungswirkung in den Vertiefungen ansammelnden Schmutzpartikel aufgrund ihrer Trägheit wieder in die Dichtfläche zwischen dem Flügel bzw. Steg und der Umfangsfläche des Zellenrades eindringen. Durch die Anordnung der Vertiefungen in der Umfangsfläche wird darüber hinaus die Wandstärke der radialen Zellenwände nicht reduziert, so daß der maximal mögliche Verstellwinkel erhalten bleibt.This object is achieved with the characterizing features of Main claim solved. By arranging the recesses in the radially outer Circumferential surface is prevented that due to the acceleration effect in dirt particles accumulating in the wells due to their inertia Sealing surface between the wing or web and the peripheral surface of the cellular wheel penetration. The arrangement of the depressions in the circumferential surface makes it above addition, the wall thickness of the radial cell walls is not reduced, so that the maximum possible adjustment angle is retained.
Werden in jedem Druckraum über den Umfang verteilt mehrere Vertiefungen in die Umfangsfläche eingearbeitet, kann auf besonders vorteilhafte Weise der Weg reduziert werden, den Schmutzpartikel entlang der Umfangsfläche zurücklegen müssen, bis sie sich in einer Vertiefung ablagern können.In each pressure chamber, several depressions are distributed over the circumference Incorporated peripheral surface, the path can be reduced in a particularly advantageous manner the dirt particles have to travel along the circumferential surface until they can be deposited in a depression.
Eine besonders einfache Bearbeitung des Zellenrades und ein relativ großes Volumen zur Aufnahme von Schmutzpartikeln ergibt sich, wenn sich die Vertiefungen in axialer Richtung über die gesamte Länge des Druckraumes erstrecken. A particularly simple machining of the cellular wheel and a relatively large volume for the admission of dirt particles arises when the depressions are in axial Direction over the entire length of the pressure chamber.
Trotz der Anordnung der Vertiefungen in der Umfangsfläche und demzufolge im Bereich der Dichtfläche zum angrenzenden Steg des Innenteil kann eine gute Abdichtung gewährleistet werden, wenn die Breite der Vertiefungen in Umfangsrichtung gesehen so gewählt ist, daß jeweils mindestens zwei Vertiefungen durch die angrenzende Stirnfläche eines Steges abgedichtet werden. Der zwischen den Vertiefungen befindliche Teil der Umfangsfläche hat dabei eine für den Betrieb der Verstelleinrichtung ausreichende Dichtlänge.Despite the arrangement of the recesses in the peripheral surface and consequently in The area of the sealing surface to the adjacent web of the inner part can be a good one Sealing can be ensured if the width of the depressions is in Seen circumferential direction is chosen so that at least two recesses be sealed by the adjacent end face of a web. The between part of the circumferential surface located in the recesses has one for the operation of the Adjustment device sufficient sealing length.
Eine besonders gute Dichtwirkung an der Umfangsfläche wird erreicht, wenn die Breite der Vertiefungen und/oder der Abstände der Vertiefungen kleiner als 20% der Breite des angrenzenden Steges ist.A particularly good sealing effect on the peripheral surface is achieved if the width of the depressions and / or the spacing of the depressions is less than 20% of the width of the adjacent web.
Eine noch einmal verbesserte Dichtwirkung wird erzielt, wenn die Breite und/oder der Abstand der Vertiefungen kleiner als 10% der Breite des angrenzenden Steges ist.A further improved sealing effect is achieved if the width and / or the The distance between the depressions is less than 10% of the width of the adjacent web.
Eine gute und schnelle Aufnahme von Schmutzpartikeln bei gleichzeitig hoher Dichtwirkung wird erzielt, wenn die Breite der Vertiefungen etwa 0,5 bis 1 mm beträgt. Die Tiefe (in radialer Richtung) liegt vorzugsweise im Bereich zwischen 0,2 und 0,5 mm. Die Vertiefungen können dabei beispielsweise einen Rechteckquerschnitt aufweisen. Eine fertigungstechnisch besonders günstige Ausführung ergibt sich, wenn die Vertiefungen einen etwa halbkreisförmigen Querschnitt mit leicht konischem Öffnungsbereich zum Innenraum aufweisen.A good and quick absorption of dirt particles with a high level at the same time The sealing effect is achieved when the width of the depressions is approximately 0.5 to 1 mm. The depth (in the radial direction) is preferably in the range between 0.2 and 0.5 mm. The depressions can, for example, have a rectangular cross section exhibit. A particularly favorable execution in terms of production results if the depressions have an approximately semicircular cross section with a slightly conical shape Have opening area to the interior.
Ein Zellenrad mit Vertiefungen an seiner Umfangsfläche kann auf besonders vorteilhafte und kostengünstige Weise als Sinterbauteil hergestellt werden. Die Vertiefungen zur Aufnahme der Schmutzpartikel können dann bereits beim Sintervorgang mit erstellt werden. Die Bearbeitung der Umfangsfläche nach dem Sintervorgang ist dabei - wie bei Bauteilen ohne Vertiefung - ohne weiteren Aufwand bzw. ohne weitere Kosten möglich. A cellular wheel with depressions on its circumferential surface can in particular advantageous and inexpensive way to be produced as a sintered component. The Wells for receiving the dirt particles can then already at Sintering process can be created with. Machining the peripheral surface after Sintering is - as with components without a recess - without any additional effort or possible without further costs.
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 Ansicht der Verstelleinrichtung von der der Nockenwelle abgewandten Seite her gesehen und in
- Fig. 2
- einen Schnitt entlang der Linie II-II nach Fig. 1,
- Fig. 3
- einen vergrößerten Ausschnitt der Fig. 1.
- Fig. 1
- a view of the adjusting device seen from the side facing away from the camshaft and in
- Fig. 2
- 2 shows a section along the line II-II according to FIG. 1,
- Fig. 3
- an enlarged section of FIG. 1st
In der Zeichnung ist mit 1 die Nockenwelle einer Brennkraftmaschine dargestellt, an
deren freien Ende das Innenteil 2 einer Verstellvorrichtung 3 drehfest angeordnet ist.
Dieses Innenteil 2 ist in diesem Ausführungsbeispiel mit vier radial angeordneten
Stegen 4a bis 4d versehen. Das Innenteil wird von einem Zellenrad 5 umfaßt, das auf
nicht näher dargestellte Weise mit der Kurbelwelle der Brennkraftmaschine verbunden
ist und demzufolge als Antriebsrad wirkt. Das Zellenrad 5 ist mit vier nach innen
ragenden radialen Stegen 6a bis 6d versehen, zwischen denen vier Zellen ausgebildet
sind, die durch die Stege des Innenteils in jeweils zwei Druckräume 7a bis 7d bzw. 8a
bis 8d unterteilt sind. Diese Druckräume sind so ausgebildet, daß die Summe der
hydraulisch wirksamen Flächen in beide Verstellrichtungen gleich ist. Die Druckräume
7a bis 7d sind jeweils über eine radiale Bohrung 9a bis 9d im Innenteil mit einer
Ringnut 10 an der Nockenwelle 1 verbunden. Die Druckräume 8a bis 8d sind in
analoger Weise über radiale Bohrungen 11a bis 11d im Innenteil mit einer zweiten
Ringnut 12 in der Nockenwelle verbunden. Die Ringnut 10 ist dabei mit dem
Druckkanal 14 und die Ringnut 12 mit dem Druckkanal 13 verbunden. Diese
Druckkanäle 13 und 14 sind auf an sich bekannte Weise über ein Nockenwellenlager
15 mit jeweils einer Steuerleitung 16 bzw. 17 verbunden. Die beiden Steuerleitungen
16 und 17 sind an ein beispielsweise als 4/3-Wegeventil ausgebildetes Steuerventil 18
angeschlossen. Dieses Steuerventil 18 ist zum einen mit einer Druckmittelpumpe 19
und zum anderen mit einem Öltank 20 verbunden.In the drawing, 1 shows the camshaft of an internal combustion engine
the free end of which the
In der in Fig. 2 dargestellten Schaltstellung II (Neutralstellung) sind alle vier Anschlüsse
an das Steuerventil 18 einseitig verschlossen. Die Verstellvorrichtung 3 ist somit
hydraulisch verriegelt bzw. eingespannt und behält ihre eingenommene
Lagezuordnung von Innenteil und Zellenrad bei. In der Schaltstellung I des
Steuerventils 18 werden die Druckräume 7a bis 7d über die Bohrungen 9a bis 9d, die
Ringnut 10, den Druckkanal 14 und die Leitung 17 von der Druckmittelpumpe 19
beaufschlagt. Gleichzeitig sind die Druckräume 8a bis 8d über die Bohrungen 11a bis
11d, die Ringnut 12, den Druckkanal 13 und die Steuerleitung 16 zum Öltank 20
entlastet. Durch diesen Druckaufbau in den Druckräumen 7a bis 7d und die
gleichzeitige Druckentlastung in den Druckräumen 8a bis 8d wird das Innenrad in der
in Fig. 1 gewählten Ansicht im Gegenuhrzeigersinn relativ zum Zellenrad verdreht. In
der Schaltstellung III des Steuerventils 18 ist die Steuerleitung 16 mit der
Druckmittelpumpe 19 und die Steuerleitung 17 mit dem Öltank 20 verbunden. Über
die zuvor beschriebenen Ölführungskanäle werden somit die Druckräume 8a bis 8d
mit Druck beaufschlagt und die Druckräume 7a bis 7d entlastet. Das Innenteil 2 wird
somit relativ zum Zellenrad 5 im Uhrzeigersinn verdreht.All four connections are in the switching position II (neutral position) shown in FIG. 2
closed on one side to the
Wie in Fig. 1 und im vergrößerten Ausschnitt in Fig. 3 dargestellt, liegen die Stege 6a
bis 6d des Zellenrades 5 jeweils mit ihren Stirnseiten dichtend an der inneren
Umfangsfläche 21 des Innenteils 2 an. Die Stege 4a bis 4d des Innenteils liegen mit
ihren in Umfangsrichtung gewölbten Stirnseiten 23 dichtend an der inneren
Umfangsfläche 24 des Zellenrades 5 an. In diese innere Umfangsfläche 24 sind eine
Vielzahl von axial verlaufenden Vertiefungen 25 eingearbeitet. Diese Vertiefungen sind
in diesem Ausführungsbeispiel als Längsnuten mit rechteckigem Querschnitt
ausgeführt. Andere Querschnittsformen, wie z.B. Trapezquerschnitte,
Dreiecksquerschnitte oder abgerundete Querschnitte sind ohne weiteres möglich. Die
Vertiefungen 25 erstrecken sich in axialer Richtung über die gesamte Breite der
Druckräume 7a bis 7d und 8a bis 8d der Breite B der Stege 4a bis 4d, 6a bis 6d.
Diese Vertiefungen sind in regelmäßigen Abständen über den Umfang verteilt. In
diesem Ausführungsbeispiel sind die Breite b und der Abstand d so gewählt, daß in
jedem Druckraum etwa dreißig Vertiefungen angeordnet sind. Mit Abstand d ist hierbei
der Abstand zweier benachbarter Seitenflächen der angrenzenden Vertiefungen
definiert. Dieser Abstand entspricht der Breite des verbleibenden Steges 26 der
Umfangsfläche, der jeweils dichtend an der Stirnseite 23 des Steges anliegt. Die
Breite D bzw. die Bogenlänge der Stirnseite 23 und die Breite b sowie die Abstände d
der Vertiefungen sind in diesem Ausführungsbeispiel so aufeinander abgestimmt, daß
jeweils etwa zehn Vertiefungen 25 durch die Stirnseite 23 abgedeckt sind.As shown in Fig. 1 and in the enlarged detail in Fig. 3, the webs 6a
to 6d of the
Die Breite b der Vertiefungen liegt in dem hier dargestellten Ausführungsbeispiel bei
etwa 0,75 mm. Es ist dabei jedoch ohne weiteres möglich, die Breite b der
Vertiefungen zwischen etwa 0,5 mm und 1 mm zu variieren. Die Tiefe (in radialer
Richtung der Vertiefungen 25) liegt im hier dargestellten Ausführungsbeispiel bei etwa
0,35 mm. Es ist dabei jedoch auch ohne weiteres möglich, die Tiefe im Bereich
zwischen etwa 0,2 mm und 0,5 mm zu variieren. Die Vertiefungen 25 haben im hier
dargestellten Ausführungsbeispiel einen etwa rechteckförmigen Querschnitt. Es ist
jedoch auch ohne weiteres möglich, diese Vertiefungen mit einem etwa
halbkreisförmigen Querschnitt mit leicht konischem Öffnungsbereich zum Innenraum
hin auszubilden.The width b of the depressions is included in the exemplary embodiment shown here
about 0.75 mm. However, it is easily possible to determine the width b
Varies between about 0.5 mm and 1 mm vary. The depth (in radial
The direction of the depressions 25) in the exemplary embodiment shown here is approximately
0.35 mm. However, it is also easily possible to set the depth in the area
to vary between about 0.2 mm and 0.5 mm. The
Claims (15)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19834843 | 1998-08-01 | ||
DE19834843A DE19834843A1 (en) | 1998-08-01 | 1998-08-01 | Device for changing the relative rotational position of a shaft to the drive wheel |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0978638A1 true EP0978638A1 (en) | 2000-02-09 |
EP0978638B1 EP0978638B1 (en) | 2003-09-17 |
Family
ID=7876186
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99112226A Expired - Lifetime EP0978638B1 (en) | 1998-08-01 | 1999-06-25 | Phase changing device between a shaft and its driving pulley |
Country Status (7)
Country | Link |
---|---|
US (1) | US6129063A (en) |
EP (1) | EP0978638B1 (en) |
JP (1) | JP2000055171A (en) |
KR (1) | KR100516423B1 (en) |
CN (1) | CN1089848C (en) |
DE (2) | DE19834843A1 (en) |
ES (1) | ES2204034T3 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100516423B1 (en) * | 1998-08-01 | 2005-09-23 | 독터. 인제니어.하.체.에프.포르쉐악티엔게젤샤프트 | Device for changing the rotational position of a shaft relative to a drive wheel |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6250265B1 (en) | 1999-06-30 | 2001-06-26 | Borgwarner Inc. | Variable valve timing with actuator locking for internal combustion engine |
JP2001055914A (en) * | 1999-08-17 | 2001-02-27 | Unisia Jecs Corp | Valve timing control device for internal combustion engine |
DE19943833A1 (en) * | 1999-09-13 | 2001-03-15 | Volkswagen Ag | Internal combustion engine with hydraulic camshaft adjuster for camshaft adjustment |
JP3477406B2 (en) * | 1999-10-05 | 2003-12-10 | 株式会社日立ユニシアオートモティブ | Valve timing changing device for internal combustion engine |
US6247434B1 (en) * | 1999-12-28 | 2001-06-19 | Borgwarner Inc. | Multi-position variable camshaft timing system actuated by engine oil |
US6477999B1 (en) | 1999-12-28 | 2002-11-12 | Borgwarner Inc. | Vane-type hydraulic variable camshaft timing system with lockout feature |
US6311655B1 (en) | 2000-01-21 | 2001-11-06 | Borgwarner Inc. | Multi-position variable cam timing system having a vane-mounted locking-piston device |
US6263846B1 (en) | 1999-12-28 | 2001-07-24 | Borgwarner Inc. | Control valve strategy for vane-type variable camshaft timing system |
DE10039913C1 (en) * | 2000-08-16 | 2001-10-18 | Porsche Ag | Device to adjust relative rotation angle between camshaft and drive wheel of internal combustion engine; has inner part fixed to cam shaft and driven cellular wheel that can be locked together |
DE50211849D1 (en) | 2001-09-11 | 2008-04-17 | Porsche Ag | VALVE TRANSMISSION FOR AN INTERNAL COMBUSTION ENGINE |
DE102005013141B4 (en) * | 2005-03-22 | 2017-10-19 | Schaeffler Technologies AG & Co. KG | Device for adjusting the camshaft of an internal combustion engine |
GB2431977A (en) * | 2005-11-02 | 2007-05-09 | Mechadyne Plc | Camshaft assembly |
DE102007020526A1 (en) * | 2007-05-02 | 2008-11-06 | Schaeffler Kg | Camshaft adjuster for an internal combustion engine with improved design of the pressure chambers |
DE102010008003A1 (en) * | 2010-02-15 | 2011-08-18 | Schaeffler Technologies GmbH & Co. KG, 91074 | feeder |
DE102010012652B4 (en) | 2010-03-25 | 2018-05-17 | Hilite Germany Gmbh | Pivot camshaft adjuster with a rotor |
DE102011000822B4 (en) | 2011-02-11 | 2012-11-08 | Hydraulik-Ring Gmbh | Housing with a Schwenkmotorversteller |
DE102018113977A1 (en) * | 2018-06-12 | 2019-12-12 | ECO Holding 1 GmbH | Camshaft unit and method for producing a camshaft unit |
DE102019116880A1 (en) * | 2019-06-24 | 2020-12-24 | ECO Holding 1 GmbH | Camshaft adjuster |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0781899A1 (en) | 1995-11-30 | 1997-07-02 | Aisin Seiki Kabushiki Kaisha | Valve timing control device |
DE19745908A1 (en) * | 1997-10-17 | 1999-04-22 | Schaeffler Waelzlager Ohg | Gas reversing valves control for internal combustion engine, especially vane cell adjustment |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5908A (en) * | 1848-11-07 | Richard solis | ||
JPH05113112A (en) * | 1991-10-24 | 1993-05-07 | Toyo A Tec Kk | Valve opening/closing timing changing device for engine |
US5738056A (en) * | 1996-04-04 | 1998-04-14 | Toyota Jidosha Kabushiki Kaisha | Variable valve timing mechanism for internal combustion engine |
US5836276A (en) * | 1996-08-09 | 1998-11-17 | Denso Corporation | Rotational phase adjusting apparatus having fluid reservoir |
US5937816A (en) * | 1998-07-27 | 1999-08-17 | Wincewicz; John Garfield | Combination carburetor backing plate and crankcase breather |
DE19834843A1 (en) * | 1998-08-01 | 2000-02-03 | Porsche Ag | Device for changing the relative rotational position of a shaft to the drive wheel |
-
1998
- 1998-08-01 DE DE19834843A patent/DE19834843A1/en not_active Withdrawn
-
1999
- 1999-06-25 EP EP99112226A patent/EP0978638B1/en not_active Expired - Lifetime
- 1999-06-25 ES ES99112226T patent/ES2204034T3/en not_active Expired - Lifetime
- 1999-06-25 DE DE59906996T patent/DE59906996D1/en not_active Expired - Lifetime
- 1999-07-22 US US09/359,433 patent/US6129063A/en not_active Expired - Lifetime
- 1999-07-29 JP JP11215485A patent/JP2000055171A/en active Pending
- 1999-07-30 CN CN99111850A patent/CN1089848C/en not_active Expired - Lifetime
- 1999-07-31 KR KR10-1999-0031516A patent/KR100516423B1/en active IP Right Grant
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0781899A1 (en) | 1995-11-30 | 1997-07-02 | Aisin Seiki Kabushiki Kaisha | Valve timing control device |
DE19745908A1 (en) * | 1997-10-17 | 1999-04-22 | Schaeffler Waelzlager Ohg | Gas reversing valves control for internal combustion engine, especially vane cell adjustment |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
KR100516423B1 (en) * | 1998-08-01 | 2005-09-23 | 독터. 인제니어.하.체.에프.포르쉐악티엔게젤샤프트 | Device for changing the rotational position of a shaft relative to a drive wheel |
Also Published As
Publication number | Publication date |
---|---|
US6129063A (en) | 2000-10-10 |
KR100516423B1 (en) | 2005-09-23 |
KR20000016991A (en) | 2000-03-25 |
CN1243911A (en) | 2000-02-09 |
DE59906996D1 (en) | 2003-10-23 |
CN1089848C (en) | 2002-08-28 |
EP0978638B1 (en) | 2003-09-17 |
ES2204034T3 (en) | 2004-04-16 |
DE19834843A1 (en) | 2000-02-03 |
JP2000055171A (en) | 2000-02-22 |
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