EP1339953A1 - Device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel - Google Patents

Device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel

Info

Publication number
EP1339953A1
EP1339953A1 EP01997625A EP01997625A EP1339953A1 EP 1339953 A1 EP1339953 A1 EP 1339953A1 EP 01997625 A EP01997625 A EP 01997625A EP 01997625 A EP01997625 A EP 01997625A EP 1339953 A1 EP1339953 A1 EP 1339953A1
Authority
EP
European Patent Office
Prior art keywords
webs
camshaft
blades
cellular wheel
recesses
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
Application number
EP01997625A
Other languages
German (de)
French (fr)
Other versions
EP1339953B1 (en
Inventor
Wolfgang Stephan
Axel-Willi Jochim
Andreas Knecht
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Dr Ing HCF Porsche AG
Hilite Germany GmbH
Original Assignee
Dr Ing HCF Porsche AG
Hydraulik Ring GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Dr Ing HCF Porsche AG, Hydraulik Ring GmbH filed Critical Dr Ing HCF Porsche AG
Publication of EP1339953A1 publication Critical patent/EP1339953A1/en
Application granted granted Critical
Publication of EP1339953B1 publication Critical patent/EP1339953B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices

Definitions

  • the invention relates to a device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel according to the preamble of the main claim.
  • sealing elements are arranged on the end faces of the rotor blades of the camshaft adjuster in a fifth exemplary embodiment (see FIGS. 15 to 18). These sealing elements, which are not described in any more detail, are intended to prevent the hydraulic oil used to adjust the rotor relative to the stator from passing from the pressure chambers charged with hydraulic oil via the end face of the rotor blades to the currently unpressurized adjustment chambers.
  • vane cell camshaft adjuster in which recesses are provided on the end faces of the rotor blades, in which roller-shaped rolling elements are accommodated. These rolling elements serve to reduce the frictional forces between the drive wheel and the impeller (rotor), the rolling elements being supported on one side directly in the recess and on the other side directly on the inner wall of the drive wheel.
  • recesses are also provided on the end faces of the rotor blades, in which rectangular sealing bodies are arranged.
  • hydraulic oil is conveyed into the recesses via a leakage gap formed between the rotor blades and the stator (drive wheel); the rectangular sealing bodies are thus pressed against the stator with a first side surface and against the inner flank of the sealing groove with a second side surface (see, for example, FIG. 7).
  • the rollers provided as sealing bodies in the recesses of the rotor blades ensure a line contact both on the stator (drive wheel) and on the inner surface of the sealing groove, which has a greater contact pressure than a surface contact (see DE 199 22 194 AI) and thus a more reliable sealing of the two of the rotor blades ensure separate pressure chambers.
  • the friction compared to the rectangular sealing elements is significantly lower.
  • Fig. 2 shows a section along the line II-ll in Fig. 1 and
  • Fig. 3 shows an enlarged section of a rotor blade.
  • the camshaft of an internal combustion engine is schematically indicated at 2, at the free end of which an inner part, hereinafter referred to as rotor 4, of an adjusting unit 5 is arranged.
  • the rotor 4 is provided with five radially arranged vanes 6a to 6e, which start from a hub 8 of the rotor 4.
  • the rotor 4 is surrounded in the area of its blades 6a to 6e by a cellular wheel 10, which is provided with five inwardly projecting radial webs 12a to 12e.
  • the cell wheel 10 forming the stator of the adjusting unit 5 is closed on its end face facing the camshaft 2 by a chain wheel 14 which is rotatably and sealingly guided on the hub 8 of the rotor 4.
  • the sprocket 14 serves as a drive for the camshaft 2, which takes place, for example, via a drive chain connected to the crankshaft.
  • the opposite end face of the cellular wheel 10 is closed by a disk 16, the chain wheel 14 and the disk 16 being firmly connected to the cellular wheel 10 by means of fastening screws 18.
  • the through holes 20 provided in the webs 12a to 12e in the cellular wheel 10 serve to receive or guide these fastening screws 18.
  • a signal transmitter disk 30 is attached to the outside of the rotor 4, with the aid of which the rotational position of the camshaft 2 relative to the crankshaft can be detected.
  • the five axial bores 32a to 32e arranged in the hub 8 of the rotor 4 represent part of the oil supply channels for the pressure spaces 24a to 24e.
  • the pressure spaces 22a to 22e are also supplied with hydraulic oil via radial bores (not shown) arranged in the hub ,
  • the hydraulic oil supply for the two pressure chambers 22a to 22e and 24a to 24e takes place via a camshaft bearing 34 the corresponding control lines for the oil pressure supply of the adjustment unit 5 are connected.
  • the way in which the oil is supplied to the pressure chambers 22a to 22e or 24a to 24e is, for. B. from DE 199 30 711 Cl known, so that the more precise design of the oil supply channels to the pressure chambers is not discussed further.
  • Groove-shaped recesses 38 are provided on the free end face 36 of each wing 6a to 6e, in which a sealing body 40 designed as metallic rollers is accommodated.
  • the rollers 40 are provided with a diameter of 3 mm (-0.006 / -0.002) and the groove-shaped recesses 38 are provided with 3 mm H7 (0 / + 0.0D clearance fit.
  • a gap a is formed in the range from 0.01 to 0.1 mm and the inner wall 42 of the cellular wheel 10.
  • the rotor 4 is adjusted in the desired manner in the counterclockwise direction, due to the fact that the gap a is formed between the free end face 36 of the vanes 6a to 6e and the inner wall 42 of the cellular wheel 10, a quantity of leakage oil reaches the groove-shaped recesses via the gap a 38.
  • the pressure chambers 22a to 22e are pressurized with oil.
  • the end faces 36 are sealed off from the inner wall 42 of the cellular wheel 10 in Analogously: the sealing bodies 40 form a line contact LK1 ' with the inner wall 42 and a line contact LK2 ' with the side walls 44 'of the groove-shaped recesses 38, so that it is also ensured here during the adjustment process that the hydraulic oil located in the pressure chambers 22a to 22e cannot get into the pressure chambers 24a to 24e via the gap a.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

The invention relates to a device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel. Said device comprises an inner part (4) that is linked with the camshaft in a rotationally fixed manner and that has at least substantially radially extending webs or blades (6a to 6e). A driven cellular wheel (10) is provided with a plurality of cells distributed across its periphery and delimited by webs (12a to 12e). Said cells are subdivided into two respective pressure compartments (22a to 22e and 24a to 24e) by the webs or blades (6a to 6e) of the inner part (4) that are guided inside said cells in an angularly mobile manner. When the pressure compartments are hydraulically pressurized or depressurized via control lines, the camshaft can be rotated between two end positions relative to the cellular wheel (10) by way of the webs or blades. Sealing elements (40) are disposed on the free front face (36) of the webs or blades and seal the pressure compartments defined by said webs or blades. The device is further characterized in that the front face (36) of the webs or blades (6a to 6e) is provided with recesses (38) in which sealing bodies (40) are disposed that are forced against an internal wall (42) of the cellular wheel (10) by a hydraulically applied force. The sealing bodies are configured as rollers (40) that are received in recesses (38) with a certain assembly clearance. Said rollers (40), during operation of the adjustment unit (5), establish a linear contact (LK1, LK1") with the internal wall (42) of the cellular wheel (10) and a linear contact (LK2, LK2") with the side walls (44, 44") of the recesses (40), thereby sealing the pressure compartments.

Description

Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad Device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel
Die Erfindung betrifft eine Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad nach der Gattung des Hauptanspruchs.The invention relates to a device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel according to the preamble of the main claim.
Aus der DE 196 23 818 AI ist eine gattungsgemäße Vorrichtung bekannt, bei der in einem fünften Ausführungsbeispiel (siehe Fig. 15 bis 18) an den Stirnseiten der Rotorflügel des Nockenwellenverstellers Dichtungselemente angeordnet sind. Diese nicht näher bezeichneten Dichtungselemente sollen verhindern, dass das zum Verstellen des Rotors gegenüber dem Stator verwendete Hydrauliköl nicht von den mit Hydrauliköl beaufschlagten Druckkammern über die Stirnseite der Rotorflügel zu den momentan drucklosen Verstellkammern gelangt.From DE 196 23 818 AI a generic device is known, in which sealing elements are arranged on the end faces of the rotor blades of the camshaft adjuster in a fifth exemplary embodiment (see FIGS. 15 to 18). These sealing elements, which are not described in any more detail, are intended to prevent the hydraulic oil used to adjust the rotor relative to the stator from passing from the pressure chambers charged with hydraulic oil via the end face of the rotor blades to the currently unpressurized adjustment chambers.
Aus der DE 197 45 908 AI ist ebenfalls ein sog. Flügelzellen-Nockenwellenversteller bekannt, bei dem an den Stirnseiten der Rotorflügel Ausnehmungen vorgesehen sind, in denen rollenförmige Wälzkörper Aufnahme finden. Diese Wälzkörper dienen zur Reduzierung der Reibkräfte zwischen dem Antriebsrad und dem Flügelrad (Rotor), wobei sich die Wälzkörper auf der einen Seite direkt in der Ausnehmung und auf der anderen Seite direkt an der Innenwand des Antriebsrades abstützen.From DE 197 45 908 AI a so-called vane cell camshaft adjuster is also known, in which recesses are provided on the end faces of the rotor blades, in which roller-shaped rolling elements are accommodated. These rolling elements serve to reduce the frictional forces between the drive wheel and the impeller (rotor), the rolling elements being supported on one side directly in the recess and on the other side directly on the inner wall of the drive wheel.
Bei der in der DE 199 22 194 AI dargestellten Verstelleinheit sind ebenfalls an den Stirnseiten der Rotorflügel Ausnehmungen vorgesehen, in denen rechteckförmige Dichtkörper angeordnet sind. Im Betrieb der Brennkraftmaschine wird über einen zwischen den Rotorflügeln und dem Stator (Antriebsrad) ausgebildeten Leckagespalt Hydrauliköl in die Ausnehmungen gefördert; damit werden die rechteckförmigen Dichtkörper mit einer ersten Seitenfläche an den Stator und mit einer zweiten Seitenfläche an die Innenflanke der Dichtungsnut gedrückt (siehe z.B. Fig. 7). Es ist die Aufgabe der Erfindung, eine gattungsgemäße Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle zur ihrem Antriebsrad dahingehend zu verbessern, dass eine einfache, und gegenüber dem Stand der Technik verbesserte Abdichtung der beiden von einem Rotorflügel abgetrennten Druckräume des Nockenwellenverstellers erfolgt.In the adjustment unit shown in DE 199 22 194 AI, recesses are also provided on the end faces of the rotor blades, in which rectangular sealing bodies are arranged. During operation of the internal combustion engine, hydraulic oil is conveyed into the recesses via a leakage gap formed between the rotor blades and the stator (drive wheel); the rectangular sealing bodies are thus pressed against the stator with a first side surface and against the inner flank of the sealing groove with a second side surface (see, for example, FIG. 7). It is the object of the invention to improve a generic device for the relative rotation angle adjustment of a camshaft to its drive wheel in such a way that a simple and, compared with the prior art, improved sealing of the two pressure spaces of the camshaft adjuster separated from a rotor blade takes place.
Diese Aufgabe wird erfindungsgemäß durch die Merkmale des Haupanspruchs gelöst.This object is achieved by the features of the main claim.
Die als Dichtungskörper in den Ausnehmungen der Rotorflügel vorgesehenen Rollen gewährleisten sowohl am Stator (Antriebsrad) als auch an der Innenfläche der Dichtungsnut einen Linienkontakt, der gegenüber einem Flächenkontakt (siehe DE 199 22 194 AI) eine größere Anpreßkraft und damit ein zuverlässigeres Abdichten der beiden von den Rotorflügeln getrennten Druckräume gewährleistet. Darüber hinaus ist aufgrund der beiden Linienberührungen der verwendeten Rollen die Reibung gegenüber den rechteckförmigen Dichtungselementen wesentlich geringer.The rollers provided as sealing bodies in the recesses of the rotor blades ensure a line contact both on the stator (drive wheel) and on the inner surface of the sealing groove, which has a greater contact pressure than a surface contact (see DE 199 22 194 AI) and thus a more reliable sealing of the two of the rotor blades ensure separate pressure chambers. In addition, due to the two line contacts of the rollers used, the friction compared to the rectangular sealing elements is significantly lower.
Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Beschreibung und Zeichnung näher erläutert.An embodiment of the invention is explained in more detail in the following description and drawing.
Es zeigenShow it
Fig. 1 einen Schnitt durch einen Nockenwellenversteller,1 shows a section through a camshaft adjuster,
Fig. 2 einen Schnitt entlang der Linie ll-ll in Fig. 1 undFig. 2 shows a section along the line II-ll in Fig. 1 and
Fig. 3 einen vergrößerten Ausschnitt eines Rotorflügels.Fig. 3 shows an enlarged section of a rotor blade.
Beschreibung des Ausführungsbeispiels In der Zeichnung ist mit 2 schematisch die Nockenwelle einer Brennkraftmaschine angedeutet, an deren freien Ende ein Innenteil, im folgenden als Rotor 4 bezeichnet, einer Verstelleinheit 5 angeordnet ist. Der Rotor 4 ist in diesem Ausführungsbeispiel mit fünf radial angeordneten Flügel 6a bis 6e versehen, die von einer Nabe 8 des Rotors 4 ausgehen. Der Rotor 4 wird im Bereich seiner Flügel 6a bis 6e von einem Zellenrad 10 umfasst, dass mit fünf nach innen ragenden radialen Stegen 12a bis 12e versehen ist. Das den Stator der Verstelleinheit 5 bildende Zellenrad 10 wird auf seiner der Nockenwelle 2 zugewandten Stirnseite von einem Kettenrad 14 abgeschlossen, das drehbeweglich und dichtend auf der Nabe 8 des Rotors 4 geführt ist. Das Kettenrad 14 dient als Antrieb für die Nockenwelle 2, der beispielsweise über eine mit der Kurbelwelle verbundene Antriebskette erfolgt. Die gegenüberliegende Stirnseite des Zellenrades 10 wird von einer Scheibe 16 verschlossen, wobei das Kettenrad 14 und die Scheibe 16 über Befestigungsschrauben 18 mit dem Zellenrad 10 fest verbunden sind. Die in den Stegen 12a bis 12e im Zellenrad 10 vorgesehenen Durchgangsbohrungen 20 dienen der Aufnahme bzw. der Führung dieser Befestigungsschrauben 18. Durch die Stege 12a bis 12e des Zellenrades 10 werden fünf durch das Kettenrad 14 und die Scheibe 16 in axialer Richtung begrenzte Zellen ausgebildet, die durch die Flügel 6a bis 6e des Rotors 4 in jeweils zwei Druckräume 22a bis 22e bzw. 24a bis 24e unterteilt sind. Der Rotor 4 und das auf diesem drehbar geführte Zellenrad 10 sind mit Hilfe einer Zylinderschraube (nicht dargestellt) an der Nockenwelle 2 befestigt. Zur Aufnahme der Zylinderschraube weist die Nabe 10 eine zentrale Bohrung 26 auf.Description of the embodiment In the drawing, the camshaft of an internal combustion engine is schematically indicated at 2, at the free end of which an inner part, hereinafter referred to as rotor 4, of an adjusting unit 5 is arranged. In this exemplary embodiment, the rotor 4 is provided with five radially arranged vanes 6a to 6e, which start from a hub 8 of the rotor 4. The rotor 4 is surrounded in the area of its blades 6a to 6e by a cellular wheel 10, which is provided with five inwardly projecting radial webs 12a to 12e. The cell wheel 10 forming the stator of the adjusting unit 5 is closed on its end face facing the camshaft 2 by a chain wheel 14 which is rotatably and sealingly guided on the hub 8 of the rotor 4. The sprocket 14 serves as a drive for the camshaft 2, which takes place, for example, via a drive chain connected to the crankshaft. The opposite end face of the cellular wheel 10 is closed by a disk 16, the chain wheel 14 and the disk 16 being firmly connected to the cellular wheel 10 by means of fastening screws 18. The through holes 20 provided in the webs 12a to 12e in the cellular wheel 10 serve to receive or guide these fastening screws 18. Five webs delimited in the axial direction by the chain wheel 14 and the disk 16 are formed by the webs 12a to 12e of the cellular wheel 10, which are divided into two pressure chambers 22a to 22e and 24a to 24e by the blades 6a to 6e of the rotor 4. The rotor 4 and the cell wheel 10 rotatably guided on it are attached to the camshaft 2 by means of a cylinder screw (not shown). The hub 10 has a central bore 26 for receiving the cylinder screw.
Mit Hilfe von zwei Spannstiften 28 und der Zylinderschraube ist an der Außenseite des Rotors 4 eine Signalgeberscheibe 30 befestigt, mit deren Hilfe die Drehlageposition der Nockenwelle 2 gegenüber der Kurbelwelle erfasst werden kann. Die fünf in der Nabe 8 des Rotors 4 angeordneten axialen Bohrungen 32a bis 32e stellen einen Teil der Ölversorgungskanäle für die Druckräume 24a bis 24e dar. Die Druckräume 22a bis 22e werden ebenfalls über in der Nabe angeordnete radial verlaufende Bohrungen (nicht dargestellt) mit Hydrauliköl versorgt. Die Hydraulikölversorgung für die beiden Druckräume 22a bis 22e bzw. 24a bis 24e erfolgt über ein Nockenwellenlager 34, an dem entsprechende Steuerleitungen für die Öldruckversorgung der Verstelleinheit 5 angeschlossen sind. Die Art und Weise wie die Olzufuhr zu den Druckräumen 22a bis 22e bzw. 24a bis 24e erfolgt ist z. B. aus der DE 199 30 711 Cl bekannt, so dass auf die genauere Ausbildung der Ölzufuhrkanäle zu den Druckräumen nicht weiter eingegangen wird.With the help of two dowel pins 28 and the cylinder screw, a signal transmitter disk 30 is attached to the outside of the rotor 4, with the aid of which the rotational position of the camshaft 2 relative to the crankshaft can be detected. The five axial bores 32a to 32e arranged in the hub 8 of the rotor 4 represent part of the oil supply channels for the pressure spaces 24a to 24e. The pressure spaces 22a to 22e are also supplied with hydraulic oil via radial bores (not shown) arranged in the hub , The hydraulic oil supply for the two pressure chambers 22a to 22e and 24a to 24e takes place via a camshaft bearing 34 the corresponding control lines for the oil pressure supply of the adjustment unit 5 are connected. The way in which the oil is supplied to the pressure chambers 22a to 22e or 24a to 24e is, for. B. from DE 199 30 711 Cl known, so that the more precise design of the oil supply channels to the pressure chambers is not discussed further.
An der freien Stirnseite 36 jedes Flügels 6a bis 6e sind nutenförmige Ausnehmungen 38 vorgesehen, in denen ein als metallische Rollen ausgebildete Dichtkörper 40 Aufnahme finden. Im vorliegenden Ausführungsbeispiel sind die Rollen 40 mit einem Durchmesser von 3 mm (- 0,006/ - 0,002) und die nutenförmigen Ausnehmungen 38 mit 3 mm H7 (0/+0,0D- Spielpassung versehen. Zwischen der freien Stirnseite 36 der Flügel 6a bis 6e und der Innenwand 42 des Zellenrades 10 ist ein Spalt a ausgebildet, der im Bereich von 0,01 bis 0,1 mm toleriert ist. Wenn zur Verstellung des Rotors 4 gegenüber dem Zellenrad 10 die Öldruckzufuhr zu den Druckräumen 24a bis 24e erfolgt, so wird der Rotor 4 entgegen dem Uhrzeigersinn in gewünschter Weise verstellt. Dadurch, dass zwischen der freien Stirnseite 36 der Flügel 6a bis 6e und der Innenwand 42 des Zellenrades 10 der Spalt a ausgebildet ist, gelangt eine Leckage-Ölmenge über den Spalt a in die nutenförmigen Ausnehmungen 38. Da die Rollen 40 als Spielpassung in den Nuten 38 Aufnahme finden, werden durch das in die Nuten 38 einströmende Hydrauliköl die Dichtkörper 40 gegen die Innenwand 42 des Zellenrades 10 gedrückt. Durch den Linienkontakt LKl zwischen den Rollen 40 und der Innenwand 42 und dem Linienkontakt LK2 zwischen den Rollen 40 und den Seitenwänden 44 der nutenförmigen Ausnehmungen 38 wird sicher gestellt, dass das in den Druckkammern 24a bis 24e befindliche Hydrauliköl nicht über den Spalt a in die Druckkammern 22a bis 22e gelangt, wobei letztgenannte zu diesem Zeitpunkt drucklos sind.Groove-shaped recesses 38 are provided on the free end face 36 of each wing 6a to 6e, in which a sealing body 40 designed as metallic rollers is accommodated. In the present exemplary embodiment, the rollers 40 are provided with a diameter of 3 mm (-0.006 / -0.002) and the groove-shaped recesses 38 are provided with 3 mm H7 (0 / + 0.0D clearance fit. Between the free end face 36 of the wings 6a to 6e and a gap a is formed in the range from 0.01 to 0.1 mm and the inner wall 42 of the cellular wheel 10. If the oil pressure is supplied to the pressure spaces 24a to 24e in order to adjust the rotor 4 relative to the cellular wheel 10 the rotor 4 is adjusted in the desired manner in the counterclockwise direction, due to the fact that the gap a is formed between the free end face 36 of the vanes 6a to 6e and the inner wall 42 of the cellular wheel 10, a quantity of leakage oil reaches the groove-shaped recesses via the gap a 38. Since the rollers 40 are accommodated in the grooves 38 as a clearance fit, the sealing bodies 40 are pressed against the inner wall 42 of the cellular wheel 10 by the hydraulic oil flowing into the grooves 38 A line contact LKl between the rollers 40 and the inner wall 42 and the line contact LK2 between the rollers 40 and the side walls 44 of the groove-shaped recesses 38 ensures that the hydraulic oil in the pressure chambers 24a to 24e does not pass through the gap a into the pressure chambers 22a to 22e, the latter being depressurized at this time.
Wenn eine Verstellung des Rotors 4 gegenüber dem Zellenrad 10 bzw. dem Kettenrad 14 in entgegengesetzter Richtung, d.h. im Uhrzeigersinn erfolgen soll, so findet eine Druckölbeaufschlagung der Druckräume 22a bis 22e statt. In diesem Fall erfolgt die Abdichtung der Stirnseiten 36 gegenüber der Innenwand 42 des Zellenrades 10 in analoger Weise: die Dichtkörper 40 bilden einen Linienkontakt LKl' mit der Innenwand 42 und einen Linienkontakt LK2' mit den Seitenwänden 44' der nutenförmigen Ausnehmungen 38, so dass auch hier während des Verstellvorgangs sichergestellt ist, dass das in den Druckkammern 22a bis 22e befindliche Hydrauliköl nicht über den Spalt a in die Druckkammern 24a bis 24e gelangen kann. If an adjustment of the rotor 4 with respect to the cellular wheel 10 or the chain wheel 14 is to take place in the opposite direction, ie clockwise, the pressure chambers 22a to 22e are pressurized with oil. In this case, the end faces 36 are sealed off from the inner wall 42 of the cellular wheel 10 in Analogously: the sealing bodies 40 form a line contact LK1 ' with the inner wall 42 and a line contact LK2 ' with the side walls 44 'of the groove-shaped recesses 38, so that it is also ensured here during the adjustment process that the hydraulic oil located in the pressure chambers 22a to 22e cannot get into the pressure chambers 24a to 24e via the gap a.

Claims

Patentanspruchclaim
Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad, mit einem drehfest mit der Nockenwelle verbundenen Innenteil (4), das zumindest annähernd radial verlaufende Stege oder Flügel (6a bis 6e) aufweist, und mit einem angetriebenen Zellenrad (10), das mehrere über den Umfang verteilte, durch Stege (12a bis 12e) begrenzte Zellen aufweist, die von den darin winkelbeweglich geführten Stegen oder Flügeln (6a bis 6e) des Innenteils (4) in jeweils zwei Druckräume (22a bis 22e bzw. 24a bis 24e) unterteilt sind, bei deren hydraulischer Druckbeaufschlagung bzw. Druckentlastung über Steuerleitungen die Nockenwelle über die Stege oder Flügel zwischen zwei Endstellungen relativ zum Zellenrad (10) verdrehbar ist, sowie mit an der freien Stirnseite (36) der Stege oder Flügel angeordneten Dichtungselementen (40), die zur Abdichtung der beiden von den Stegen oder Flügeln begrenzten Druckräumen dienen, dadurch gekennzeichnet, dass an der Stirnseite (36) der Stege oder Flügel (6a bis 6e) Ausnehmungen (38) vorgesehen sind, in denen Dichtkörper (40) angeordnet sind, die zur Abdichtung der Druckräume durch eine hydraulische Beaufschlagung gegen eine Innenwand (42) des Zellenrades (10) gedrückt werden, dadurch gekennzeichnet, dass die Dichtkörper als Rollen (40) ausgebildet sind, die mit einem Einbauspiel versehen, in den Ausnehmungen (38) Aufnahme finden, wobei die Rollen (40) während des Betriebs der Verstelleinheit (5) zur Abdichtung einen Linienkontakt (LKl, LKl') mit der Innenwand (42) des Zellenrades (10) und einen Linienkontakt (LK2, LK2') mit den Seitenwänden (44, 44') der Ausnehmungen (40) bilden. Device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel, with an inner part (4) connected in a rotationally fixed manner to the camshaft, which has at least approximately radially extending webs or wings (6a to 6e), and with a driven cellular wheel (10), which has several Cells distributed over the circumference and delimited by webs (12a to 12e), each of which is divided into two pressure chambers (22a to 22e or 24a to 24e) by the webs or wings (6a to 6e) of the inner part (4) which are guided angularly therein are, with their hydraulic pressurization or pressure relief via control lines, the camshaft can be rotated via the webs or wings between two end positions relative to the cellular wheel (10), and with sealing elements (40) arranged on the free end face (36) of the webs or wings serve to seal the two pressure spaces delimited by the webs or wings, characterized in that On the end face (36) of the webs or wings (6a to 6e) there are recesses (38) in which sealing bodies (40) are arranged, which are used to seal the pressure chambers by hydraulic action against an inner wall (42) of the cellular wheel (10). are pressed, characterized in that the sealing bodies are designed as rollers (40) which are provided with an installation clearance and are accommodated in the recesses (38), the rollers (40) making a line contact during the operation of the adjusting unit (5) for sealing (LKl, LKl ' ) with the inner wall (42) of the cellular wheel (10) and a line contact (LK2, LK2 ' ) with the side walls (44, 44 ' ) of the recesses (40).
EP01997625A 2000-11-25 2001-11-06 Device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel Expired - Lifetime EP1339953B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10058707 2000-11-25
DE10058707A DE10058707C2 (en) 2000-11-25 2000-11-25 Device for the relative rotation angle adjustment of a camshaft of an internal combustion engine to a drive wheel
PCT/EP2001/012802 WO2002042614A1 (en) 2000-11-25 2001-11-06 Device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel

Publications (2)

Publication Number Publication Date
EP1339953A1 true EP1339953A1 (en) 2003-09-03
EP1339953B1 EP1339953B1 (en) 2006-09-06

Family

ID=7664742

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01997625A Expired - Lifetime EP1339953B1 (en) 2000-11-25 2001-11-06 Device for adjusting the angle of rotation of a camshaft of an internal combustion engine relative to a drive wheel

Country Status (5)

Country Link
US (1) US6679208B2 (en)
EP (1) EP1339953B1 (en)
JP (1) JP2004514819A (en)
DE (2) DE10058707C2 (en)
WO (1) WO2002042614A1 (en)

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US8215292B2 (en) * 1996-07-17 2012-07-10 Bryant Clyde C Internal combustion engine and working cycle
JP2004143971A (en) * 2002-10-22 2004-05-20 Aisin Seiki Co Ltd Valve timing controller
DE102005038364A1 (en) * 2005-08-13 2007-02-15 Schaeffler Kg Device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine
DE102006019607B4 (en) * 2006-04-25 2008-01-31 Hydraulik-Ring Gmbh Phaser
JP6106660B2 (en) * 2011-04-04 2017-04-05 コロンビア・パワー・テクノロジーズ・インコーポレーテッドＣｏｌｕｍｂｉａ Ｐｏｗｅｒ Ｔｅｃｈｎｏｌｏｇｉｅｓ，Ｉｎｃ． Mechanical assembly that maintains a gap between the stator and rotor of an electromechanical energy converter
DE102014208598B4 (en) 2014-05-08 2020-10-29 Schaeffler Technologies AG & Co. KG Camshaft adjuster with a hydraulic chamber sealing element that can be switched back and forth to achieve a hydraulic freewheel

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DE4237193A1 (en) * 1992-11-04 1994-05-05 Bosch Gmbh Robert Method for controlling a device for the relative rotation of a shaft and device for the relative rotation of the shaft of an internal combustion engine
US5823152A (en) * 1995-06-14 1998-10-20 Nippondenso Co., Ltd. Control apparatus for varying a rotational or angular phase between two rotational shafts, preferably applicable to a valve timing control apparatus for an internal combustion engine
DE19740215B4 (en) * 1996-09-13 2006-02-09 Denso Corp., Kariya Drehphaseneinstellvorrichtung with a synthetic resin seal
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
JPH11141313A (en) * 1997-11-07 1999-05-25 Toyota Motor Corp Valve timing varying device for internal combustion engine
JP3174297B2 (en) * 1998-12-07 2001-06-11 三菱電機株式会社 Vane type hydraulic actuator
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DE19951391A1 (en) * 1999-10-26 2001-07-05 Schaeffler Waelzlager Ohg Device for changing the control times of gas exchange valves of an internal combustion engine, in particular hydraulic camshaft adjusting device in the direction of rotation
DE10020120A1 (en) * 2000-04-22 2001-10-25 Schaeffler Waelzlager Ohg Device for changing valve timings of internal combustion engine has pressure chambers in vaned rotor sealed by axial pendulum type sealing strips which can pivot in both rotational directions of rotor vanes

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Title
See references of WO0242614A1 *

Also Published As

Publication number Publication date
DE10058707C2 (en) 2003-10-16
JP2004514819A (en) 2004-05-20
DE50110959D1 (en) 2006-10-19
US6679208B2 (en) 2004-01-20
WO2002042614A1 (en) 2002-05-30
DE10058707A1 (en) 2002-06-13
US20030127065A1 (en) 2003-07-10
EP1339953B1 (en) 2006-09-06

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