EP0978638B1 - 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
- EP0978638B1 EP0978638B1 EP99112226A EP99112226A EP0978638B1 EP 0978638 B1 EP0978638 B1 EP 0978638B1 EP 99112226 A EP99112226 A EP 99112226A EP 99112226 A EP99112226 A EP 99112226A EP 0978638 B1 EP0978638 B1 EP 0978638B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- depressions
- width
- inner part
- webs
- equal
- 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.)
- Expired - Lifetime
Links
Images
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 relative rotational angle adjustment a camshaft of an internal combustion engine to the drive wheel after the Genus of the main claim.
- Such a device is known, for example, from EP 0 781 899 A1.
- EP 0 781 899 A1 describes a means for changing the rotational position of the camshaft a Internal combustion engine, wherein the camshaft rotatably connected to an internal gear , which has radially arranged wings, the associated cells of a cellular wheel in each divided two opposing pressure chambers.
- These pressure chambers are Hydraulically acted upon by a control valve.
- the radial extending walls of the cellular wheel are in the region of its radial outside with Wells provided for receiving dirt particles, the be introduced via the pressure medium in the pressure chambers.
- the in the pressure medium located dirt particles accumulate depending on the direction of rotation of the Camshaft due to the accelerations acting on them and due to their Inertia essentially in one of the two wells. This is it around the respective rear in relation to the direction of rotation.
- the on the Front of the respective wing or web of the inner part located Although dirt particles can by its relative movement in the front recess the cell wheel are pressed, but because of their inertia, they will not be there remain. Thus, there is the danger in such an adjustment that especially smaller dirt particles in the sealing gap between the wing or web and cellular wheel penetrate and considerable wear and permanently diminishing Perform sealing effect. In addition, an entry of dirt particles in these Sealing lead to a significantly excessive friction.
- a particularly simple processing of the cell wheel and a relatively large volume for receiving dirt particles results when the wells in the axial Direction extend over the entire length of the pressure chamber.
- a particularly good sealing effect on the circumferential surface is achieved when the width the recesses and / or the distances of the recesses less than 20% of the width the adjacent footbridge is.
- a good and fast absorption of dirt particles at the same time high Sealing effect is achieved when the width of the recesses is about 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, a rectangular cross section exhibit.
- a manufacturing technology particularly favorable design results when the depressions have an approximately semicircular cross section with slightly conical Have opening area to the interior.
- a cellular wheel with recesses on its peripheral surface can be particularly advantageous and inexpensive way to be produced as a sintered component.
- the Wells for receiving the dirt particles can then already at Sintering process to be created with.
- the processing of the peripheral surface after the Sintering process is - as with components without recess - without further effort or without further costs possible.
- the camshaft of an internal combustion engine is shown at whose free end the inner part 2 of an adjusting device 3 is arranged rotationally fixed.
- This inner part 2 is arranged radially in this embodiment with four Webs 4a to 4d provided.
- the inner part is surrounded by a cellular wheel 5, the on not shown manner connected to the crankshaft of the internal combustion engine is and therefore acts as a drive wheel.
- the bucket 5 is four inwards projecting radial webs 6a to 6d, between which four cells formed are, through the webs of the inner part in each case two pressure chambers 7a to 7d and 8a are subdivided to 8d. These pressure chambers are designed so that the sum of hydraulically effective surfaces in both adjustment directions is the same.
- the pressure chambers 7a to 7d are in each case via a radial bore 9a to 9d in the inner part with a Ring groove 10 connected to the camshaft 1.
- the pressure chambers 8a to 8d are in analogous manner via radial holes 11a to 11d in the inner part with a second Ring 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.
- These Pressure channels 13 and 14 are known per se via a camshaft bearing 15 connected to a respective control line 16 and 17 respectively.
- the two control lines 16 and 17 are formed on a control valve 18, for example designed as a 4/3-way valve connected. This control valve 18 is on the one hand with a pressure medium pump 19th and on the other hand connected to an oil tank 20.
- the webs are 6a to 6d of the cellular wheel 5 each with their end faces sealingly on the inner Peripheral surface 21 of the inner part 2 at.
- the webs 4a to 4d of the inner part are with their circumferentially curved end faces 23 sealingly on the inner Peripheral surface 24 of the cellular wheel 5 at.
- In this inner peripheral surface 24 are a Variety of axially extending recesses 25 incorporated. These wells are in this embodiment as longitudinal grooves with a rectangular cross-section executed. Other cross-sectional shapes, such as e.g. Trapezoidal cross-sections, Triangular cross sections or rounded cross sections are readily possible.
- the Recesses 25 extend in the axial direction over the entire width of Pressure chambers 7a to 7d and 8a to 8d of the width B of the webs 4a to 4d, 6a to 6d. These depressions are distributed over the circumference at regular intervals.
- the width b and the distance d are selected so that in each pressure chamber about thirty wells are arranged.
- At a 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 of the Peripheral surface, each 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 recesses are coordinated in this embodiment so that each about ten wells 25 are covered by the end face 23.
- the width b of the recesses is in the embodiment shown here about 0.75 mm. However, it is readily possible, the width b of To vary wells between about 0.5 mm and 1 mm.
- the depth (in radial Direction of the recesses 25) is in the illustrated embodiment at about 0.35 mm. However, it is also readily possible, the depth in the area between about 0.2 mm and 0.5 mm.
- the recesses 25 have in here illustrated embodiment has an approximately rectangular cross-section. It is also readily possible, these wells with an approximately semicircular cross-section with slightly conical opening to the interior to train.
Landscapes
- 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)
Description
Die Erfindung betrifft eine Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zum Antriebsrad nach der Gattung des Hauptanspruches.The invention relates to a device for relative rotational angle adjustment a camshaft of an internal combustion engine to the drive wheel after 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. These describes a means for changing the rotational position of the camshaft a Internal combustion engine, wherein the camshaft rotatably connected to an internal gear , which has radially arranged wings, the associated cells of a cellular wheel in each divided two opposing pressure chambers. These pressure chambers are Hydraulically acted upon by a control valve. Depending on the particular Pressurizing the inner wheel is rotated relative to the feeder. The radial extending walls of the cellular wheel are in the region of its radial outside with Wells provided for receiving dirt particles, the be introduced via the pressure medium in the pressure chambers. The in the pressure medium located dirt particles accumulate depending on the direction of rotation of the Camshaft due to the accelerations acting on them and due to their Inertia essentially in one of the two wells. This is it around the respective rear in relation to the direction of rotation. The on the Front of the respective wing or web of the inner part located Although dirt particles can by its relative movement in the front recess the cell wheel are pressed, but because of their inertia, they will not be there remain. Thus, there is the danger in such an adjustment that especially smaller dirt particles in the sealing gap between the wing or web and cellular wheel penetrate and considerable wear and permanently diminishing Perform sealing effect. In addition, an entry of dirt particles in these Sealing lead to a significantly excessive friction. This would be essential higher pressure requirement to achieve a sufficiently fast adjustment by itself pull. In addition, such depressions in the walls between the require adjacent cells have a relatively large wall thickness and lie in one voltage-technically unfavorable range. The required by the wells large wall thickness therefore reduces the width - in the circumferential direction - the adjacent cells, so that overall the displacement is reduced.
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 to provide the generic Adjusting to improve effect that dirt particles from the Can deposit pressure medium in non-critical areas of the pressure chambers, without the Risk of increased friction and / or increased wear in the area of the sealing surface.
Diese Aufgabe wird erfindungsgemäß mit den Merkmalen des Hauptanspruches gelöst. Durch die Anordnung der Vertiefungen in der den Stirnseiten der Flügel des Innenteils gegenüberliegenden Umfangsfläche des Zellenrades 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 features of the main claim. Due to the arrangement of the recesses in the end faces of the wings of the inner part opposite peripheral surface of the cellular wheel is prevented that the due to the acceleration effect accumulating in the wells Dirt particles due to their inertia back into the sealing surface between the wing or web and the peripheral surface of the cellular wheel penetrate. By the arrangement of Recesses in the peripheral surface is beyond the wall thickness of the radial Cell walls not reduced, so that the maximum possible adjustment angle is maintained.
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.Are distributed in each pressure chamber over the circumference several wells in the Peripheral surface incorporated, can be reduced in a particularly advantageous manner, the way need to cover the dirt particles along the peripheral surface until they can deposit in a well.
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 processing of the cell wheel and a relatively large volume for receiving dirt particles results when the wells in the axial Direction extend 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 Sealing be ensured when the width of the recesses in Seen in the circumferential direction is chosen so that in each case at least two recesses be sealed by the adjacent end face of a web. The between The recesses located part of the peripheral surface has one for the operation of the Adjustment 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 circumferential surface is achieved when the width the recesses and / or the distances of the recesses less than 20% of the width the adjacent footbridge is.
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.An even better sealing effect is achieved when the width and / or the Distance of the recesses 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 fast absorption of dirt particles at the same time high Sealing effect is achieved when the width of the recesses is about 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, a rectangular cross section exhibit. A manufacturing technology particularly favorable design results when the depressions have an approximately semicircular cross section with slightly conical 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 recesses on its peripheral surface can be particularly advantageous and inexpensive way to be produced as a sintered component. The Wells for receiving the dirt particles can then already at Sintering process to be created with. The processing of the peripheral surface after the Sintering process is - as with components without recess - without further effort or without further costs possible.
Weitere Vorteile und vorteilhafte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen und der Beschreibung.Further advantages and advantageous developments of the invention will become apparent 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 of the camshaft side facing away and in
- Fig. 2
- a section along the line II-II of Fig. 1,
- Fig. 3
- an enlarged detail of FIG. 1.
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, the camshaft of an internal combustion engine is shown at
whose free end 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.In the switching position II (neutral position) shown in Fig. 2, all four ports
closed 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 section in Fig. 3, the webs are 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 recesses is in the embodiment shown here
about 0.75 mm. However, it is readily possible, the width b of
To vary wells between about 0.5 mm and 1 mm. The depth (in radial
Direction of the recesses 25) is in the illustrated embodiment at about
0.35 mm. However, it is also readily possible, the depth in the area
between about 0.2 mm and 0.5 mm. The
Claims (15)
- A device for adjusting the rotational angle of a camshaft of an internal-combustion engine relative to a drive wheel, with an inner part (2) which is connected to the camshaft in a rotationally fixed manner and which has webs or vanes (4a to 4d) extending at least substantially radially, and with a driven cell wheel (5) which has a plurality of cells which are distributed over the periphery and are bounded by webs (6a to 6d) and which are subdivided in each case into two pressure chambers (7a to 7d and 8a to 8d respectively) by the webs or vanes (4a to 4d) guided in an angularly movable manner therein, and with at least one depression (25) in the wall region of the pressure chambers (7a to 7d and 8a to 8d respectively) in each case, characterized in that the depressions (25) are formed in the peripheral face (24) of the cell wheel (5) opposite the end faces (23) of the webs or vanes (4a to 4d) of the inner part (2).
- A device according to Claim 1, characterized in that a plurality of depressions (25) are formed - distributed over the periphery - in the peripheral face (24) in each pressure chamber (7a to 7d, 8a to 8d).
- A device according to Claim 1 or 2, characterized in that the depressions (25) are formed at regular intervals in the peripheral face (24).
- A device according to Claim 3, characterized in that the depressions (25) extend in the axial direction over the entire width B of the pressure chamber (7a to 7d, 8a to 8d).
- A device according to one of the preceding Claims, characterized in that the depressions (25) are constructed in the form of axially extending grooves.
- A device according to one of the preceding Claims, characterized in that the width b and the intervals d of the depressions (25) are selected to be such that at least two respective depressions are covered by the adjacent end face (23) of a web (4a to 4d) of the inner part (2).
- A device according to one of the preceding Claims, characterized in that the width b of the depressions (25) - as viewed in the peripheral direction - is less than 1/5 of the width D of the adjacent web (4a to 4d) of the inner part (2).
- A device according to one of the preceding Claims, characterized in that the interval d of the depressions (25) is less than 1/5 of the width D of the adjacent web (4a to 4d) of the inner part (2).
- A device according to one of the preceding Claims, characterized in that the width b of the depressions - as viewed in the peripheral direction - is less than 1/10 of the width D of the adjacent web (4a to 4d) of the inner part (2).
- A device according to one of the preceding Claims, characterized in that the interval d of the depressions (25) is less than 1/10 of the width D of the adjacent web (4a to 4d) of the inner part (2).
- A device according to one of the preceding Claims, characterized in that the cell wheel (5) is constructed in the form of a sintered component, and the depressions (25) are jointly formed during the sintering process.
- A device according to one of the preceding Claims, characterized in that the width b of the depressions (25) is smaller [than or] equal to 1 mm.
- A device according to one of the preceding Claims, characterized in that the width b of the depressions (25) is greater [than or] equal to 0·5 mm.
- A device according to one of the preceding Claims, characterized in that the depth of the depressions (25) is smaller [than or] equal to 0·5 mm.
- A device according to one of the preceding Claims, characterized in that the depth of the depressions is greater [than or] equal to 0·2 mm.
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 EP0978638A1 (en) | 2000-02-09 |
EP0978638B1 true 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 (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010012652A1 (en) | 2010-03-25 | 2011-09-29 | Hydraulik-Ring Gmbh | Oscillating motor camshaft adjuster for changing angle position between crankshaft and camshaft during operation of combustion engine, has chambers supplied by hole that passes from area of wing to area of another wing |
DE102011000822A1 (en) | 2011-02-11 | 2012-08-16 | Hydraulik-Ring Gmbh | Housing for internal combustion engine e.g. petrol engine, stator whose exterior wall has openings through which oil is introduced into pressure chambers in associated opposite pivoting directions |
Families Citing this family (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19834843A1 (en) * | 1998-08-01 | 2000-02-03 | Porsche Ag | Device for changing the relative rotational position of a shaft to the drive wheel |
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 |
US6263846B1 (en) | 1999-12-28 | 2001-07-24 | Borgwarner Inc. | Control valve strategy for vane-type variable camshaft timing system |
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 |
US6247434B1 (en) * | 1999-12-28 | 2001-06-19 | Borgwarner Inc. | Multi-position variable camshaft timing system actuated by engine oil |
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 |
WO2003023197A1 (en) | 2001-09-11 | 2003-03-20 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Valve mechanism 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 |
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 |
Family Cites Families (8)
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 |
EP0781899B1 (en) * | 1995-11-30 | 2000-02-09 | Aisin Seiki Kabushiki Kaisha | Valve timing control device |
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 |
DE19745908B4 (en) * | 1997-10-17 | 2004-03-04 | Ina-Schaeffler Kg | Device for changing the control times of gas exchange valves of an internal combustion engine, the device being designed as a vane adjustment device |
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 DE DE59906996T patent/DE59906996D1/en not_active Expired - Lifetime
- 1999-06-25 ES ES99112226T patent/ES2204034T3/en not_active Expired - Lifetime
- 1999-06-25 EP EP99112226A patent/EP0978638B1/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
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010012652A1 (en) | 2010-03-25 | 2011-09-29 | Hydraulik-Ring Gmbh | Oscillating motor camshaft adjuster for changing angle position between crankshaft and camshaft during operation of combustion engine, has chambers supplied by hole that passes from area of wing to area of another wing |
DE102010012652B4 (en) | 2010-03-25 | 2018-05-17 | Hilite Germany Gmbh | Pivot camshaft adjuster with a rotor |
DE102011000822A1 (en) | 2011-02-11 | 2012-08-16 | Hydraulik-Ring Gmbh | Housing for internal combustion engine e.g. petrol engine, stator whose exterior wall has openings through which oil is introduced into pressure chambers in associated opposite pivoting directions |
DE102011000822B4 (en) * | 2011-02-11 | 2012-11-08 | Hydraulik-Ring Gmbh | Housing with a Schwenkmotorversteller |
Also Published As
Publication number | Publication date |
---|---|
DE19834843A1 (en) | 2000-02-03 |
KR20000016991A (en) | 2000-03-25 |
JP2000055171A (en) | 2000-02-22 |
ES2204034T3 (en) | 2004-04-16 |
US6129063A (en) | 2000-10-10 |
KR100516423B1 (en) | 2005-09-23 |
CN1089848C (en) | 2002-08-28 |
CN1243911A (en) | 2000-02-09 |
EP0978638A1 (en) | 2000-02-09 |
DE59906996D1 (en) | 2003-10-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0978638B1 (en) | Phase changing device between a shaft and its driving pulley | |
EP1844216B1 (en) | Adjustable camshaft, in particular for internal combustion engines of motor vehicles, comprising a hydraulic adjusting system | |
EP2210005B1 (en) | Axial bearing, particularly for a turbocharger | |
DE3206068C2 (en) | Clutch disc | |
DE102005013141A1 (en) | Device for camshaft adjustment in internal combustion (IC) engine, has labyrinth seals for suppressing oil leakage between device components, including inner and outer rotors, side panels, and extension elements | |
DE3732572C2 (en) | ||
EP1076762B1 (en) | Device for hydraulically adjusting the angle of rotation of a shaft in relation to a driving wheel | |
DE4345273C2 (en) | Hydraulic gear machine (pump or motor), in particular internal gear machine | |
DE19882271B4 (en) | Device for changing the timing of gas exchange valves of an internal combustion engine, in particular for a vane-adjusting device with a designed as a locking element wings | |
DE60220099T2 (en) | RADIAL PISTON HYDRAULIC ENGINE | |
EP3810963A1 (en) | Hydrodynamically effective sealing ring and rotary feedthrough with such a sealing ring | |
DE4143466C2 (en) | Control disc for vane pump | |
DE10082316B4 (en) | Device for varying the valve timing of an internal combustion engine, in particular camshaft adjusting device with swivel impeller | |
DE102004046934B4 (en) | Hydraulic machine | |
EP1979143A1 (en) | Mixing head | |
DE4109149C2 (en) | Control disc for vane pump | |
WO1998046864A1 (en) | Inner seal for a camshaft adjusting device in an internal combustion engine, specially a blade cell adjusting device | |
DE4225804C2 (en) | Gear machine | |
DE4338349C2 (en) | gear machine | |
DE3102509A1 (en) | Gear machine (pump or motor) | |
EP0910760B1 (en) | Internal combustion piston engine | |
DE3022090A1 (en) | PRESSURE-OPERATED ROTARY PISTON ENGINE | |
DE4230185C2 (en) | Directional spool for hydraulic controls | |
EP3276127B1 (en) | Geared fluid machine | |
DE10139896A1 (en) | Differential with two cam parts |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE ES FR GB IT SE |
|
AX | Request for extension of the european patent |
Free format text: AL;LT;LV;MK;RO;SI |
|
17P | Request for examination filed |
Effective date: 20000614 |
|
AKX | Designation fees paid |
Free format text: DE ES FR GB IT SE |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
17Q | First examination report despatched |
Effective date: 20030122 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE ES FR GB IT SE |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) | ||
REF | Corresponds to: |
Ref document number: 59906996 Country of ref document: DE Date of ref document: 20031023 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2204034 Country of ref document: ES Kind code of ref document: T3 |
|
ET | Fr: translation filed | ||
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20040618 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TQ |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: CD |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20110310 AND 20110316 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20110331 AND 20110406 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TQ |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 18 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 19 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20180625 Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20180620 Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20180620 Year of fee payment: 20 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20180620 Year of fee payment: 20 Ref country code: ES Payment date: 20180720 Year of fee payment: 20 Ref country code: IT Payment date: 20180627 Year of fee payment: 20 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 59906996 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: PE20 Expiry date: 20190624 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION Effective date: 20190624 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20200902 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION Effective date: 20190626 |