EP1477636B2 - Camshaft phasing device for internal combustion engine - Google Patents

Camshaft phasing device for internal combustion engine Download PDF

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Publication number
EP1477636B2
EP1477636B2 EP04010748.4A EP04010748A EP1477636B2 EP 1477636 B2 EP1477636 B2 EP 1477636B2 EP 04010748 A EP04010748 A EP 04010748A EP 1477636 B2 EP1477636 B2 EP 1477636B2
Authority
EP
European Patent Office
Prior art keywords
valve
camshaft adjuster
camshaft
adjuster according
rotor
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.)
Not-in-force
Application number
EP04010748.4A
Other languages
German (de)
French (fr)
Other versions
EP1477636A3 (en
EP1477636B1 (en
EP1477636A2 (en
Inventor
Gerold Sluka
Edwin Palesch
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.)
Hilite Germany GmbH
Original Assignee
Hilite Germany 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
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Application filed by Hilite Germany GmbH filed Critical Hilite Germany GmbH
Publication of EP1477636A2 publication Critical patent/EP1477636A2/en
Publication of EP1477636A3 publication Critical patent/EP1477636A3/en
Publication of EP1477636B1 publication Critical patent/EP1477636B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves
    • 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
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/3444—Oil filters

Definitions

  • the invention relates to a camshaft adjuster for internal combustion engines of motor vehicles according to the preamble of claim 1.
  • camshaft adjusters With camshaft adjusters, the opening time of intake and exhaust valves of the internal combustion engine is controlled as a function of the power required in each case. It sometimes causes problems to install the valve in the internal combustion engine of the motor vehicle, since the space is not sufficient for this.
  • Such a device is generic from the US 6182622 previously known.
  • the invention has the object of providing the generic camshaft adjuster so that it can be used in tight spaces in the vehicle.
  • the valve is arranged on the side facing away from the camshaft connection. Therefore, the valve can be arranged axially outside the motor stationary.
  • the camshaft adjuster according to the invention therefore requires only little installation space.
  • the camshaft adjuster invention can also grow later.
  • the camshaft adjuster according to Fig. 1 to 4 serves to adjust the opening time of intake and exhaust valves of an internal combustion engine of a motor vehicle to the power requirement of the machine.
  • Such camshaft adjusters are known and are therefore only briefly explained.
  • the camshaft adjuster has a rotor 1, which is non-rotatably connected to a camshaft 2.
  • the rotor 1 is surrounded by a stator 3. He has a cylindrical shell 4, projecting radially inwardly webs 5 from the inner wall at uniform intervals. They are of the same design and lie with their end face 6 flat against an outer cylindrical lateral surface 7 of a main body 8 of the rotor 1. From it are at equal intervals radially outwardly from webs 9, which abut with their end faces 10 in a sealing manner on an inner cylindrical jacket surface 11 of the shell 4 of the stator 3.
  • the webs 5, 9 of the stator 3 and the rotor 1 are formed integrally with the jacket 4 and the main body 8.
  • Adjacent stator side webs 5 define pressure chambers 12, which are divided by the rotor-side webs 9 in two pressure chambers 13 and 14, which are sealed from each other by the rotor webs 9.
  • one end position are the radially extending side surfaces 15 of the rotor webs 9 surface on the radially extending side walls 16 of the stator webs 5 at.
  • the rotor 1 can be rotated counterclockwise by introducing a pressure medium into the pressure chambers 14 relative to the stator 3 until the rotor webs 9 abut with their opposite side walls 17 on the adjacent side walls 18 of the stator webs 5. Between these two end positions of the rotor 1 can be rotated by appropriate pressurization of the side walls 15, 17 of the rotor webs 9 in each intermediate position relative to the stator 3.
  • dirt collecting grooves 19 In the inner circumferential surface 11 of the stator 4 are provided at the transition to the side surfaces 16, 18 of the stator 5 dirt collecting grooves 19 in which dirt is collected during operation of the camshaft adjuster, which is located in the pressure medium and due to the centrifugal forces radially outward into the dirt collecting grooves 19 is displaced. This ensures that the rotor webs 9 rest properly in the respective end position on the side walls 16, 18 of the stator webs 9 and are not dirt particles between them. As a result, at any time a precise relative position between the stator 3 and rotor 1 is ensured in the end position.
  • the dirt collecting grooves 19 extend over the axial width of the stator 3.
  • the dirt collecting grooves 19 may for example be arranged distributed along the inner circumferential surface 11 of the stator 4. It is also possible to provide the dirt collecting grooves 19 in the side walls 16, 18 of the stator webs 5 and / or in the side walls 15, 17 of the rotor webs 9. The bottom of the dirt collecting grooves 19 is in radial section according to the Fig. 3 and 4 formed part-circular curved.
  • the stator 3 is closed on one side by a drive wheel 20, which may be a chain or pulley. It is bolted to the stator 3. On the opposite side of the stator 3 is closed by a cover 21. It has the same outer diameter as the stator 3 and lies with its radially inner end against an annular shoulder surface 22 of the rotor 1.
  • the drive wheel 20 and the cover plate 21 through the stator 5 enforcing screws 23 (FIGS. Fig. 3 and 4 ) screwed against each other. With these screws 23, the drive wheel 20 and the cover 21 are pressed axially fixed against the end faces of the stator 3. The drive wheel 20 abuts against an annular shoulder surface 24 of the rotor 1.
  • the drive wheel 20 has a larger outer diameter than the stator. 3
  • the camshaft adjuster is covered by a hood-shaped cap 25, the radial bottom 26 is penetrated centrally by a valve housing 27. It has a radially outwardly directed flange 28, with which the valve housing 27 rests against the underside of the bottom 26 of the cap 25 and is fastened to it, for example, with screws.
  • the cylindrical jacket 29 of the cap 25 extends axially over the drive wheel 20 and surrounds it with a radial distance.
  • the rotor 1 is provided at its end remote from the bottom 26 of the cap 25 end with a central recess 30 into which the camshaft 2 projects with an axial projection 31.
  • the recess 30 in the rotor 1 is separated from a valve housing 27 receiving receiving space 32 by a radially inwardly directed flange 33 which limits the recess 30 axially.
  • Through a central opening 34 in the flange 33 protrudes a central screw 35 which is screwed into an axial and centrally disposed threaded bore 36 of the camshaft 2 in order to connect the camshaft adjuster with the camshaft 2.
  • the head 37 of the screw 35 is supported on the flange 33 of the main body 8 of the rotor 1 axially.
  • the rotor 1 is rotatably connected to the camshaft 2.
  • the valve housing 27 is part of a hydraulic valve 38, via which the hydraulic medium to the pressure chambers 13 and 14 of the camshaft adjuster is supplied in a manner to be described.
  • the valve housing 27 is externally provided with annular grooves 39 for receiving annular seals 40, with which the valve housing 27 is sealed in the receiving space 32 of the rotor 1 sits. As the Fig. 1 and 2 show the valve housing 27 extends close to the screw head 37th
  • a hollow piston 41 which is closed at its end remote from the screw 35 by a bottom 42. At the other end of the hollow piston 41 is open. At this end, the hollow piston 41 is expanded in the inner diameter. In this end protrudes at least one compression spring 43, with which the hollow piston 41 is loaded in the direction of a cover 44 which rests on the flange 28, the valve housing 27 and is secured thereto.
  • the lid 44 has a central recess 45 into which the hollow piston 41 protrudes with its bottom 42.
  • the compression spring 43 is supported at one end on a radial inner shoulder surface 46 in the hollow piston 41.
  • the compression spring 43 abuts against the end face of a bushing 47, which is received in a cup-shaped housing 48 which is screwed into the end of the valve housing 27 facing away from the cover 44.
  • the bush 47 is supported on the bottom 49 of the housing 48. It has at least one opening 50, via which the hydraulic medium can be supplied. It is fed centrally through the camshaft 2 and through an axial through bore 51 in the screw 35 to the phaser.
  • the bushing 47 receives a support body 57 which has on its bottom 49 of the housing 48 facing end face a central recess 52 for receiving a compression spring 53. With her, a valve plate 54 of a check valve 59 is pressed against a radial shoulder surface 55 of the bush 47. The valve disk 54 lies within the bushing 47 and closes a central opening 56 of the bush 47.
  • the support body 57 has a smaller outer diameter than the bushing 47.
  • the bushing 47 On the side remote from the compression spring 53, the bushing 47 is provided with a filter 58, through which the hydraulic medium flows before entering the hollow piston 41. In the filter 58 impurities are retained in the hydraulic medium.
  • the hydraulic valve 38 has two working ports A and B, a tank port T and a pressure port P.
  • the working ports A, B the hydraulic medium is supplied depending on the position of the hollow piston 41 of the pressure chamber 13 or 14 of the camshaft adjuster.
  • the tank port T the hydraulic medium from the respective pressure-free pressure chamber 13 and 14 is returned to the tank.
  • the hydraulic valve 38 is preceded by the check valve 59, which ensures that the hydraulic medium does not pass from the hollow piston 41 back into the camshaft 2.
  • the force exerted by the compression spring 53 of the check valve 59 on the valve disk 54 is less than the force of the compression spring 43, with which the hollow piston 41 is loaded.
  • the camshaft adjuster Since the hydraulic valve 38 is provided centrally on the camshaft adjuster and arranged in alignment with the camshaft 2, the camshaft adjuster requires only little installation space. Therefore, the camshaft adjuster can be retrofitted in the vehicle.
  • the valve housing 27 of the hydraulic valve 38 can be easily inserted from an end face of the camshaft adjuster into the receiving space 32 of the main body 8 of the rotor 1.
  • the installation position of the hydraulic valve 38 can be easily determined that the flange 28 of the valve housing 27 comes to rest on the bottom 26 of the cap 25.
  • the hollow piston 41 is slidably guided in the illustrated embodiment in a valve sleeve 60 which is arranged sealed in the valve housing 27.
  • the valve sleeve 60 has at its end facing the cover 44 a radially outwardly directed flange 61, with which it rests against the bottom of a front-side recess 62 of the valve housing 27. As a result, the axial mounting position of the valve sleeve 60 can be easily set. With the cover 44, the valve sleeve 60 is secured in position by the cover 44 rests against the flange 61 of the valve sleeve 60.
  • the Fig. 3 and 4 show how from the hydraulic valve 38 from the main body 8 of the rotor 1 radially passing holes 63, 64 open into the respective pressure chamber 13, 14 of the camshaft adjuster.
  • the pressure chambers 13 are pressurized with the hydraulic medium. Accordingly, the hydraulic medium via the camshaft 2, the through hole 51 of the screw 35, the check valve 59, the working port A and the bores 63 to the pressure chambers 13, respectively.
  • Each separated by the rotor webs 5 of the pressure chambers 13 pressure chambers 14 are depressurized.
  • the hydraulic medium therein is displaced via the holes 64, the working port B of the hydraulic valve 38 and the tank port T to the tank.
  • the hollow piston 41 of the hydraulic valve 38 is accordingly adjusted so that the pressurized hydraulic fluid can be supplied via the working port A to the pressure chambers 13 and the hydraulic medium from the pressure chambers 14 via the working port B and the tank port T can be returned to the tank. If the rotor 1 from the position according to the Fig. 3 and 4 are rotated counterclockwise relative to the stator 3, the hydraulic valve 38 is switched so that the pressure port P to the working port B and the working port A is connected to the tank port T. The pressurized hydraulic medium is therefore supplied to the pressure chambers 14 via the camshaft 2, the screw 35, the check valve 59, the working port B and the bores 64. The hydraulic medium contained in the pressure chambers 13 is accordingly displaced via the bores 63 and the working port A to the tank port T.
  • the filter 58 in front of the hydraulic valve 38 contributes to the robustness of the camshaft adjuster and to the overall system.
  • the check valve 59 located in front of the hydraulic valve 38 optimizes the overall performance of the system.
  • Fig. 5 shows an enlarged view of the hydraulic valve of the camshaft adjuster.
  • the hydraulic medium supplied via the axial pressure port P from the camshaft 2 flows via the check valve 59 into the hollow piston 41. He assumes such a position that the working port A of the hydraulic valve 38 is connected to the tank port T, while the working port B is in communication with the axial pressure port P.
  • the pressurized hydraulic fluid passes through radial openings 65 from the hollow piston 41 in the working port B. From here, the hydraulic fluid flows into axially extending, located in the valve housing 27 holes 66, which are formed as blind holes and at its the camshaft 2 end facing by a Closure 67 are closed.
  • the holes 66 open holes 68 which are provided in the bottom of an annular groove 69 in the outer surface 70 of the valve housing 27. In the annular groove 69 open the holes 63 in the rotor body. 8
  • a further annular groove 71 is provided, in the bottom distributed over the circumference of holes 72 open, which connect the annular groove 71 with axial bores 73 in the valve housing 27.
  • the holes 73 are shorter than the holes 66.
  • the holes 73 open into the camshaft 2 facing the end face of the valve housing 27 and are closed by a closure member 74.
  • the annular groove 71 the axial distance from the annular groove 69, open the radial holes 64 in the rotor body 8.
  • the axial blind holes 73 open distributed over the circumference arranged radial holes 75 which are provided near the inner end of the blind holes 73 and this connect with the hollow piston 41 radially passing holes 76. About them, the hydraulic medium can be supplied to the tank port T.
  • Fig. 6 shows that in the valve housing 27 of the hydraulic valve 38 at least one axially extending tank bore 77 is provided, which also opens into the camshaft 2 facing end face of the valve housing 27 and is closed there with a closure member 78. At the end facing away from the closure member 78, the tank bore 77 is connected to an annular groove 79 which is provided in the valve housing 27 and open into the radial bores 80, which pass through the valve sleeve 60 and distributed uniformly over the circumference.
  • annular groove 79 is connected to a further annular groove 81 which is provided in the inside of the valve sleeve 60 and open into the radial bores 82 which pass through the hollow piston 41 in the immediate vicinity of its bottom 42.
  • annular band 83 At the bottom of the annular groove 81 is axially secured an elastically deformable annular band 83 under elastic bias. It closes the radial bores 80 of the valve sleeve 60 against the hollow piston 41.
  • the annular band 83 thus forms a check valve that prevents pressurized hydraulic fluid can pass through the interior of the hollow piston 41 and its radial bores 82 in the tank bore 77.
  • the hydraulic medium flows It is elastically bent inwards under the pressure of the medium, so that the radial bores 80 are released in the valve sleeve 60 via the annular groove 79 and the radial bores 80.
  • the hydraulic medium can therefore flow through the annular groove 81 and the radial bores 82 into the hollow piston 41.
  • This displaced medium mixes with the supplied via the pressure port P, pressurized hydraulic medium, which is supplied via the working port B to the respective pressure chambers of the camshaft adjuster.
  • Serving as a check valve ring band 83 prevents the pressurized hydraulic fluid enters the tank bore 77.

Abstract

The rotor (1) has outward projecting vanes, in close sealed contact with the inside diameter of the stator (3) the stator has inward projecting vanes, in close sealed contact with the outside diameter of the rotor forming working chambers (13) supplied with oil under pressure through oil galleries (63,64). The rotor is connected to the camshaft (2) and the stator is connected to a sprocket (20) for a timing chain.

Description

Die Erfindung betrifft einen Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen nach dem Oberbegriff des Anspruches 1.The invention relates to a camshaft adjuster for internal combustion engines of motor vehicles according to the preamble of claim 1.

Mit Nockenwellenverstellern wird der Öffnungszeitpunkt von Ein- und Auslaßventilen der Verbrennungskraftmaschine in Abhängigkeit von der jeweils benötigten Leistung gesteuert. Es bereitet mitunter Probleme, das Ventil in die Verbrennungskraftmaschine des Kraftfahrzeuges einzubauen, da der Platz hierfür nicht ausreicht.With camshaft adjusters, the opening time of intake and exhaust valves of the internal combustion engine is controlled as a function of the power required in each case. It sometimes causes problems to install the valve in the internal combustion engine of the motor vehicle, since the space is not sufficient for this.

Eine derartige Vorrichtung ist gattungsbildend aus der US-6182622 vorbekannt.Such a device is generic from the US 6182622 previously known.

Der Erfindung liegt die Aufgabe zugrunde, den gattungsgemäßen Nockenwellenversteller so auszubilden, daß er auch bei beengten Platzverhältnissen im Kraftfahrzeug eingesetzt werden kann.The invention has the object of providing the generic camshaft adjuster so that it can be used in tight spaces in the vehicle.

Diese Aufgabe wird beim gattungsgemäßen Nockenwellenversteller erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruches 1 gelöst.This object is achieved in the generic camshaft adjuster according to the invention with the characterizing features of claim 1.

Beim erfindungsgemäßen Nockenwellenversteller ist das Ventil an der vom Nockenwellenanschluß abgewandten Seite angeordnet. Darum kann das Ventil axial außerhalb des Motors ortsfest angeordnet werden. Der erfindungsgemäße Nockenwellenversteller benötigt darum nur wenig Einbauraum. Außerdem läßt sich der erfindungsgemäße Nockenwellenversteller auch nachträglich anbauen.In the camshaft adjuster according to the invention, the valve is arranged on the side facing away from the camshaft connection. Therefore, the valve can be arranged axially outside the motor stationary. The camshaft adjuster according to the invention therefore requires only little installation space. In addition, the camshaft adjuster invention can also grow later.

Weitere Merkmale der Erfindung ergeben sich aus den weiteren Ansprüchen, der Beschreibung und den Zeichnungen.Further features of the invention will become apparent from the other claims, the description and the drawings.

Die Erfindung wird anhand einer in den Zeichnungen dargestellter Ausführungsform näher erläutert. Es zeigen

Fig. 1
im Axialschnitt einen erfindungsgemäßen Nockenwellenversteller,
Fig. 2
in einem anderen Axialschnitt den erfindungsgemäßen Nockenwellenversteller gemäß Fig. 1,
Fig. 3
einen Schnitt längs der Linie Y-Y in Fig. 2,
Fig. 4
einen Schnitt längs der Linie Z-Z in Fig. 2,
Fig. 5
in vergrößerter Darstellung sowie im Axialschnitt ein Ventil des erfindungsgemäßen Nockenwellenverstellers,
Fig. 6
in einer Darstellung entsprechend Fig. 5 einen weiteren Axialabschnitt des Ventils des erfindungsgemäßen Nockenwellenverstellers..
The invention will be explained in more detail with reference to an embodiment shown in the drawings. Show it
Fig. 1
in axial section a camshaft adjuster according to the invention,
Fig. 2
in another axial section of the camshaft adjuster according to the invention Fig. 1 .
Fig. 3
a section along the line YY in Fig. 2 .
Fig. 4
a section along the line ZZ in Fig. 2 .
Fig. 5
in an enlarged view and in axial section a valve of the camshaft adjuster according to the invention,
Fig. 6
in a representation accordingly Fig. 5 another axial section of the valve of the camshaft adjuster according to the invention.

Der Nockenwellenversteller gemäß den Fig. 1 bis 4 dient dazu, den Öffnungszeitpunkt von Einlaß- und Auslaßventilen einer Verbrennungskraftmaschine eines Kraftfahrzeuges an den Leistungsbedarf der Maschine anzupassen. Solche Nockenwellenversteller sind bekannt und werden darum nur kurz erläutert.The camshaft adjuster according to Fig. 1 to 4 serves to adjust the opening time of intake and exhaust valves of an internal combustion engine of a motor vehicle to the power requirement of the machine. Such camshaft adjusters are known and are therefore only briefly explained.

Der Nockenwellenversteller hat einen Rotor 1, der drehfest mit einer Nockenwelle 2 verbunden ist. Der Rotor 1 wird von einem Stator 3 umgeben. Er hat einen zylindrischen Mantel 4, von dessen Innenwand in gleichmäßigen Abständen radial nach innen Stege 5 abstehen. Sie sind gleich ausgebildet und liegen mit ihrer Stirnseite 6 flächig an einer äußeren zylindrischen Mantelfläche 7 eines Grundkörpers 8 des Rotors 1 an. Von ihm stehen in gleichen Abständen radial nach außen Stege 9 ab, die mit ihren Stirnseiten 10 flächig an einer inneren zylindrischen Mantelfläche 11 des Mantels 4 des Stators 3 dichtend anliegen. Die Stege 5, 9 des Stators 3 und des Rotors 1 sind einstückig mit dem Mantel 4 bzw. dem Grundkörper 8 ausgebildet.The camshaft adjuster has a rotor 1, which is non-rotatably connected to a camshaft 2. The rotor 1 is surrounded by a stator 3. He has a cylindrical shell 4, projecting radially inwardly webs 5 from the inner wall at uniform intervals. They are of the same design and lie with their end face 6 flat against an outer cylindrical lateral surface 7 of a main body 8 of the rotor 1. From it are at equal intervals radially outwardly from webs 9, which abut with their end faces 10 in a sealing manner on an inner cylindrical jacket surface 11 of the shell 4 of the stator 3. The webs 5, 9 of the stator 3 and the rotor 1 are formed integrally with the jacket 4 and the main body 8.

Einander benachbarte statorseitige Stege 5 begrenzen Druckräume 12, die durch die rotorseitigen Stege 9 in zwei Druckkammern 13 und 14 unterteilt werden, die gegeneinander durch die Rotorstege 9 abgedichtet sind. In der in den Fig. 3 und 4 dargestellten einen Endstellung liegen die radial verlaufenden Seitenflächen 15 der Rotorstege 9 flächig an den radial verlaufenden Seitenwänden 16 der Statorstege 5 an. Aus dieser einen Endstellung kann der Rotor 1 entgegen dem Uhrzeigersinn durch Einführen eines Druckmediums in die Druckkammern 14 relativ zum Stator 3 so weit gedreht werden, bis die Rotorstege 9 mit ihren gegenüberliegenden Seitenwänden 17 an den benachbarten Seitenwänden 18 der Statorstege 5 anliegen. Zwischen diesen beiden Endstellungen kann der Rotor 1 durch entsprechende Druckbeaufschlagung der Seitenwände 15, 17 der Rotorstege 9 in jede Zwischenlage relativ zum Stator 3 gedreht werden.Adjacent stator side webs 5 define pressure chambers 12, which are divided by the rotor-side webs 9 in two pressure chambers 13 and 14, which are sealed from each other by the rotor webs 9. In the in the Fig. 3 and 4 shown one end position are the radially extending side surfaces 15 of the rotor webs 9 surface on the radially extending side walls 16 of the stator webs 5 at. From this one end position, the rotor 1 can be rotated counterclockwise by introducing a pressure medium into the pressure chambers 14 relative to the stator 3 until the rotor webs 9 abut with their opposite side walls 17 on the adjacent side walls 18 of the stator webs 5. Between these two end positions of the rotor 1 can be rotated by appropriate pressurization of the side walls 15, 17 of the rotor webs 9 in each intermediate position relative to the stator 3.

In der inneren Mantelfläche 11 des Statormantels 4 sind am Übergang zu den Seitenflächen 16, 18 der Statorstege 5 Schmutzsammelnuten 19 vorgesehen, in denen im Betrieb des Nockenwellenverstellers Schmutz gesammelt wird, der sich im Druckmedium befindet und der aufgrund der Fliehkräfte radial nach außen in die Schmutzsammelnuten 19 verdrängt wird. Dadurch ist sichergestellt, daß die Rotorstege 9 in der jeweiligen Endlage einwandfrei an den Seitenwänden 16, 18 der Statorstege 9 anliegen und sich zwischen ihnen nicht Schmutzteilchen befinden. Dadurch ist jederzeit eine genaue Relativlage zwischen Stator 3 und Rotor 1 in der Endlage sichergestellt. Die Schmutzsammelnuten 19 erstrecken sich über die axiale Breite des Stators 3. Abweichend vom dargestellten Ausführungsbeispiel können die Schmutzsammelnuten 19 beispielsweise auch längs der inneren Mantelfläche 11 des Statormantels 4 verteilt angeordnet sein. Ebenso ist es möglich, die Schmutzsammelnuten 19 auch in den Seitenwänden 16, 18 der Statorstege 5 und/oder in den Seitenwänden 15, 17 der Rotorstege 9 vorzusehen. Der Boden der Schmutzsammelnuten 19 ist im Radialschnitt gemäß den Fig. 3 und 4 teilkreisförmig gekrümmt ausgebildet.In the inner circumferential surface 11 of the stator 4 are provided at the transition to the side surfaces 16, 18 of the stator 5 dirt collecting grooves 19 in which dirt is collected during operation of the camshaft adjuster, which is located in the pressure medium and due to the centrifugal forces radially outward into the dirt collecting grooves 19 is displaced. This ensures that the rotor webs 9 rest properly in the respective end position on the side walls 16, 18 of the stator webs 9 and are not dirt particles between them. As a result, at any time a precise relative position between the stator 3 and rotor 1 is ensured in the end position. The dirt collecting grooves 19 extend over the axial width of the stator 3. Deviating from the illustrated embodiment, the dirt collecting grooves 19 may for example be arranged distributed along the inner circumferential surface 11 of the stator 4. It is also possible to provide the dirt collecting grooves 19 in the side walls 16, 18 of the stator webs 5 and / or in the side walls 15, 17 of the rotor webs 9. The bottom of the dirt collecting grooves 19 is in radial section according to the Fig. 3 and 4 formed part-circular curved.

Der Stator 3 ist an einer Seite durch ein Antriebsrad 20 geschlossen, das ein Ketten- oder Riemenrad sein kann. Es ist am Stator 3 verschraubt. An der gegenüberliegenden Seite ist der Stator 3 durch eine Abdeckscheibe 21 geschlossen. Sie hat gleichen Außendurchmesser wie der Stator 3 und liegt mit ihrem radial inneren Ende an einer ringförmigen Schulterfläche 22 des Rotors 1 an. Vorteilhaft sind das Antriebsrad 20 und die Abdeckscheibe 21 durch die Statorstege 5 durchsetzende Schrauben 23 (Fig. 3 und 4) gegeneinander verschraubt. Mit diesen Schrauben 23 werden das Antriebsrad 20 und die Abdeckscheibe 21 axial fest gegen die Stirnseiten des Stators 3 gedrückt. Auch das Antriebsrad 20 liegt an einer ringförmigen Schulterfläche 24 des Rotors 1 an. Das Antriebsrad 20 hat größeren Außendurchmesser als der Stator 3.The stator 3 is closed on one side by a drive wheel 20, which may be a chain or pulley. It is bolted to the stator 3. On the opposite side of the stator 3 is closed by a cover 21. It has the same outer diameter as the stator 3 and lies with its radially inner end against an annular shoulder surface 22 of the rotor 1. Advantageously, the drive wheel 20 and the cover plate 21 through the stator 5 enforcing screws 23 (FIGS. Fig. 3 and 4 ) screwed against each other. With these screws 23, the drive wheel 20 and the cover 21 are pressed axially fixed against the end faces of the stator 3. The drive wheel 20 abuts against an annular shoulder surface 24 of the rotor 1. The drive wheel 20 has a larger outer diameter than the stator. 3

Der Nockenwellenversteller wird durch eine haubenförmige Abdeckkappe 25 abgedeckt, deren radialer Boden 26 zentral von einem Ventilgehäuse 27 durchsetzt wird. Es hat einen radial nach außen gerichteten Flansch 28, mit dem das Ventilgehäuse 27 an der Unterseite des Bodens 26 der Abdeckkappe 25 anliegt und an ihm beispielsweise mit Schrauben befestigt ist. Der zylindrische Mantel 29 der Abdeckkappe 25 ragt axial über das Antriebsrad 20 und umgibt es mit radialem Abstand.The camshaft adjuster is covered by a hood-shaped cap 25, the radial bottom 26 is penetrated centrally by a valve housing 27. It has a radially outwardly directed flange 28, with which the valve housing 27 rests against the underside of the bottom 26 of the cap 25 and is fastened to it, for example, with screws. The cylindrical jacket 29 of the cap 25 extends axially over the drive wheel 20 and surrounds it with a radial distance.

Der Rotor 1 ist an seinem vom Boden 26 der Abdeckkappe 25 abgewandten Ende mit einer zentralen Vertiefung 30 versehen, in die die Nockenwelle 2 mit einem axialen Ansatz 31 ragt. Die Vertiefung 30 im Rotor 1 ist von einem das Ventilgehäuse 27 aufnehmenden Aufnahmeraum 32 durch einen radial nach innen gerichteten Flansch 33 getrennt, der die Vertiefung 30 axial begrenzt. Durch eine zentrale Öffnung 34 im Flansch 33 ragt eine zentrale Schraube 35, die in eine axiale und zentral angeordnete Gewindebohrung 36 der Nockenwelle 2 geschraubt wird, um den Nockenwellenversteller mit der Nockenwelle 2 zu verbinden. Der Kopf 37 der Schraube 35 stützt sich am Flansch 33 des Grundkörpers 8 des Rotors 1 axial ab. Über die zentrale Schraube 35 wird der Rotor 1 drehfest mit der Nockenwelle 2 verbunden.The rotor 1 is provided at its end remote from the bottom 26 of the cap 25 end with a central recess 30 into which the camshaft 2 projects with an axial projection 31. The recess 30 in the rotor 1 is separated from a valve housing 27 receiving receiving space 32 by a radially inwardly directed flange 33 which limits the recess 30 axially. Through a central opening 34 in the flange 33 protrudes a central screw 35 which is screwed into an axial and centrally disposed threaded bore 36 of the camshaft 2 in order to connect the camshaft adjuster with the camshaft 2. The head 37 of the screw 35 is supported on the flange 33 of the main body 8 of the rotor 1 axially. About the central screw 35, the rotor 1 is rotatably connected to the camshaft 2.

Das Ventilgehäuse 27 ist Bestandteil eines Hydraulikventils 38, über das das Hydraulikmedium den Druckkammern 13 und 14 des Nockenwellenverstellers in noch zu beschreibender Weise zugeführt wird. Das Ventilgehäuse 27 ist außenseitig mit Ringnuten 39 zur Aufnahme von Ringdichtungen 40 versehen, mit denen das Ventilgehäuse 27 abgedichtet im Aufnahmeraum 32 des Rotors 1 sitzt. Wie die Fig. 1 und 2 zeigen, erstreckt sich das Ventilgehäuse 27 bis nahe an den Schraubenkopf 37.The valve housing 27 is part of a hydraulic valve 38, via which the hydraulic medium to the pressure chambers 13 and 14 of the camshaft adjuster is supplied in a manner to be described. The valve housing 27 is externally provided with annular grooves 39 for receiving annular seals 40, with which the valve housing 27 is sealed in the receiving space 32 of the rotor 1 sits. As the Fig. 1 and 2 show the valve housing 27 extends close to the screw head 37th

Im Ventilgehäuse 27 sitzt axial verschiebbar ein Hohlkolben 41, der an seinem von der Schraube 35 abgewandten Ende durch einen Boden 42 geschlossen ist. Am anderen Ende ist der Hohlkolben 41 offen. An diesem Ende ist der Hohlkolben 41 im Innendurchmesser erweitert. In dieses Ende ragt wenigstens eine Druckfeder 43, mit der der Hohlkolben 41 in Richtung auf einen Deckel 44 belastet ist, der auf dem Flansch 28 das Ventilgehäuses 27 aufliegt und an ihm befestigt ist. Der Deckel 44 hat eine zentrale Vertiefung 45, in die der Hohlkolben 41 mit seinem Boden 42 ragt. Die Druckfeder 43 stützt sich mit einem Ende an einer radialen inneren Schulterfläche 46 im Hohlkolben 41 ab. Mit dem anderen Ende liegt die Druckfeder 43 an der Stirnseite einer Buchse 47 an, die in einem napfförmigen Gehäuse 48 aufgenommen ist, das in das vom Deckel 44 abgewandte Ende des Ventilgehäuses 27 geschraubt ist. Die Buchse 47 stützt sich am Boden 49 des Gehäuses 48 ab. Er hat wenigstens eine Öffnung 50, über die das Hydraulikmedium zugeführt werden kann. Es wird durch die Nockenwelle 2 und durch eine axiale Durchgangsbohrung 51 in der Schraube 35 zentral dem Nockenwellenversteller zugeführt.In the valve housing 27 sits axially displaceable a hollow piston 41, which is closed at its end remote from the screw 35 by a bottom 42. At the other end of the hollow piston 41 is open. At this end, the hollow piston 41 is expanded in the inner diameter. In this end protrudes at least one compression spring 43, with which the hollow piston 41 is loaded in the direction of a cover 44 which rests on the flange 28, the valve housing 27 and is secured thereto. The lid 44 has a central recess 45 into which the hollow piston 41 protrudes with its bottom 42. The compression spring 43 is supported at one end on a radial inner shoulder surface 46 in the hollow piston 41. With the other end, the compression spring 43 abuts against the end face of a bushing 47, which is received in a cup-shaped housing 48 which is screwed into the end of the valve housing 27 facing away from the cover 44. The bush 47 is supported on the bottom 49 of the housing 48. It has at least one opening 50, via which the hydraulic medium can be supplied. It is fed centrally through the camshaft 2 and through an axial through bore 51 in the screw 35 to the phaser.

Die Buchse 47 nimmt einen Stützkörper 57 auf, der an seiner dem Boden 49 des Gehäuses 48 zugewandten Stirnseite eine zentrale Vertiefung 52 zur Aufnahme einer Druckfeder 53 aufweist. Mit ihr wird ein Ventilteller 54 eines Rückschlagventils 59 gegen eine radiale Schulterfläche 55 der Buchse 47 gedrückt. Der Ventilteller 54 liegt innerhalb der Buchse 47 und verschließt eine zentrale Öffnung 56 der Buchse 47.The bushing 47 receives a support body 57 which has on its bottom 49 of the housing 48 facing end face a central recess 52 for receiving a compression spring 53. With her, a valve plate 54 of a check valve 59 is pressed against a radial shoulder surface 55 of the bush 47. The valve disk 54 lies within the bushing 47 and closes a central opening 56 of the bush 47.

Der Stützkörper 57 hat kleineren Außendurchmesser als die Buchse 47. An der von der Druckfeder 53 abgewandten Seite ist die Buchse 47 mit einem Filter 58 versehen, durch den das Hydraulikmedium vor den Eintritt in den Hohlkolben 41 strömt. Im Filter 58 werden Verunreinigungen im Hydraulikmedium zurückgehalten.The support body 57 has a smaller outer diameter than the bushing 47. On the side remote from the compression spring 53, the bushing 47 is provided with a filter 58, through which the hydraulic medium flows before entering the hollow piston 41. In the filter 58 impurities are retained in the hydraulic medium.

Das Hydraulikventil 38 weist zwei Arbeitsanschlüsse A und B, einen Tankanschluß T sowie einen Druckanschluß P auf. Über die Arbeitsanschlüsse A, B wird das Hydraulikmedium je nach Stellung des Hohlkolbens 41 der Druckkammer 13 oder 14 des Nockenwellenverstellers zugeführt. Über den Tankanschluß T wird das Hydraulikmedium aus der jeweiligen drucklosen Druckkammer 13 bzw. 14 in den Tank zurückgeführt.The hydraulic valve 38 has two working ports A and B, a tank port T and a pressure port P. About the working ports A, B, the hydraulic medium is supplied depending on the position of the hollow piston 41 of the pressure chamber 13 or 14 of the camshaft adjuster. About the tank port T, the hydraulic medium from the respective pressure-free pressure chamber 13 and 14 is returned to the tank.

Dem Hydraulikventil 38 ist das Rückschlagventil 59 vorgeschaltet, mit dem sichergestellt wird, daß das Hydraulikmedium nicht aus dem Hohlkolben 41 zurück in die Nockenwelle 2 gelangt. Die von der Druckfeder 53 des Rückschlagventils 59 auf den Ventilteller 54 ausgeübte Kraft ist kleiner als die Kraft der Druckfeder 43, mit welcher der Hohlkolben 41 belastet ist.The hydraulic valve 38 is preceded by the check valve 59, which ensures that the hydraulic medium does not pass from the hollow piston 41 back into the camshaft 2. The force exerted by the compression spring 53 of the check valve 59 on the valve disk 54 is less than the force of the compression spring 43, with which the hollow piston 41 is loaded.

Da das Hydraulikventil 38 zentral am Nockenwellenversteller vorgesehen und fluchtend zur Nockenwelle 2 angeordnet ist, benötigt der Nockenwellenversteller nur wenig Einbauraum. Darum kann der Nockenwellenversteller nachträglich im Kraftfahrzeug eingebaut werden. Das Ventilgehäuse 27 des Hydraulikventils 38 kann von einer Stirnseite des Nockenwellenverstellers aus einfach in den Aufnahmeraum 32 des Grundkörpers 8 des Rotors 1 eingesetzt werden. Die Einbaulage des Hydraulikventils 38 läßt sich dadurch einfach festlegen, daß der Flansch 28 des Ventilgehäuses 27 am Boden 26 der Abdeckkappe 25 zur Anlage kommt. Der Hohlkolben 41 ist im darge-stellten Ausführungsbeispiel in einer Ventilbuchse 60 verschiebbar geführt, die abgedichtet im Ventilgehäuse 27 angeordnet ist. Die Ventilbuchse 60 hat an ihrem dem Deckel 44 zugewandten Ende einen radial nach außen gerichteten Flansch 61, mit dem sie am Boden einer stirnseitigen Vertiefung 62 des Ventilgehäuses 27 anliegt. Dadurch läßt sich die axiale Einbaulage der Ventilbuchse 60 einfach festlegen. Mit dem Deckel 44 wird die Ventilbuchse 60 lagegesichert, indem der Deckel 44 am Flansch 61 der Ventilbuchse 60 anliegt.Since the hydraulic valve 38 is provided centrally on the camshaft adjuster and arranged in alignment with the camshaft 2, the camshaft adjuster requires only little installation space. Therefore, the camshaft adjuster can be retrofitted in the vehicle. The valve housing 27 of the hydraulic valve 38 can be easily inserted from an end face of the camshaft adjuster into the receiving space 32 of the main body 8 of the rotor 1. The installation position of the hydraulic valve 38 can be easily determined that the flange 28 of the valve housing 27 comes to rest on the bottom 26 of the cap 25. The hollow piston 41 is slidably guided in the illustrated embodiment in a valve sleeve 60 which is arranged sealed in the valve housing 27. The valve sleeve 60 has at its end facing the cover 44 a radially outwardly directed flange 61, with which it rests against the bottom of a front-side recess 62 of the valve housing 27. As a result, the axial mounting position of the valve sleeve 60 can be easily set. With the cover 44, the valve sleeve 60 is secured in position by the cover 44 rests against the flange 61 of the valve sleeve 60.

Die Fig. 3 und 4 zeigen, wie vom Hydraulikventil 38 aus den Grundkörper 8 des Rotors 1 radial durchsetzende Bohrungen 63, 64 in die jeweilige Druckkammer 13, 14 des Nockenwellenverstellers münden. In den Fig. 3 und 4 sind die Druckkammern 13 mit dem Hydraulikmedium unter Druck gesetzt. Dementsprechend wird das Hydraulikmedium über die Nockenwelle 2, die Durchgangsbohrung 51 der Schraube 35, das Rückschlagventil 59, den Arbeitsanschluß A und die Bohrungen 63 den Druckkammern 13 zugeführt. Die jeweils durch die Rotorstege 5 von den Druckkammern 13 getrennten Druckkammern 14 sind druckentlastet. Das darin befindliche Hydraulikmedium wird über die Bohrungen 64, den Arbeitsanschluß B des Hydraulikventils 38 und den Tankanschluß T zum Tank verdrängt. Der Hohlkolben 41 des Hydraulikventils 38 ist dementsprechend so eingestellt, daß das unter Druck stehende Hydraulikmedium über den Arbeitsanschluß A den Druckkammern 13 zugeführt und das Hydraulikmedium aus den Druckkammern 14 über den Arbeitsanschluß B und den Tankanschluß T zum Tank zurückgeführt werden kann. Soll der Rotor 1 aus der Stellung gemäß den Fig. 3 und 4 entgegen dem Uhrzeigersinn relativ zum Stator 3 gedreht werden, wird das Hydraulikventil 38 so umgeschaltet, daß der Druckanschluß P mit dem Arbeitsanschluß B und der Arbeitsanschluß A mit dem Tankanschluß T verbunden ist. Das unter Druck stehende Hydraulikmedium wird darum über die Nockenwelle 2, die Schraube 35, das Rückschlagventil 59, den Arbeitsanschluß B und die Bohrungen 64 den Druckkammern 14 zugeführt. Das in den Druckkammern 13 befindliche Hydraulikmedium wird dementsprechend über die Bohrungen 63 und den Arbeitsanschluß A zum Tankanschluß T verdrängt.The Fig. 3 and 4 show how from the hydraulic valve 38 from the main body 8 of the rotor 1 radially passing holes 63, 64 open into the respective pressure chamber 13, 14 of the camshaft adjuster. In the Fig. 3 and 4 the pressure chambers 13 are pressurized with the hydraulic medium. Accordingly, the hydraulic medium via the camshaft 2, the through hole 51 of the screw 35, the check valve 59, the working port A and the bores 63 to the pressure chambers 13, respectively. Each separated by the rotor webs 5 of the pressure chambers 13 pressure chambers 14 are depressurized. The hydraulic medium therein is displaced via the holes 64, the working port B of the hydraulic valve 38 and the tank port T to the tank. The hollow piston 41 of the hydraulic valve 38 is accordingly adjusted so that the pressurized hydraulic fluid can be supplied via the working port A to the pressure chambers 13 and the hydraulic medium from the pressure chambers 14 via the working port B and the tank port T can be returned to the tank. If the rotor 1 from the position according to the Fig. 3 and 4 are rotated counterclockwise relative to the stator 3, the hydraulic valve 38 is switched so that the pressure port P to the working port B and the working port A is connected to the tank port T. The pressurized hydraulic medium is therefore supplied to the pressure chambers 14 via the camshaft 2, the screw 35, the check valve 59, the working port B and the bores 64. The hydraulic medium contained in the pressure chambers 13 is accordingly displaced via the bores 63 and the working port A to the tank port T.

Das Filter 58 vor dem Hydraulikventil 38 trägt zur Robustheit des Nockenwellenverstellers und zum Gesamtsystem bei. Durch das vor dem Hydraulikventil 38 befindliche Rückschlagventil 59 wird die gesamte Performance des Systems optimiert.The filter 58 in front of the hydraulic valve 38 contributes to the robustness of the camshaft adjuster and to the overall system. The check valve 59 located in front of the hydraulic valve 38 optimizes the overall performance of the system.

Fig. 5 zeigt in vergrößerter Darstellung das Hydraulikventil des Nockenwellenverstellers. In Fig. 5 ist der Fall dargestellt, daß das über den axialen Druckanschluß P von der Nockenwelle 2 aus zugeführte Hydraulikmedium über das Rückschlagventil 59 in den Hohlkolben 41 strömt. Er nimmt eine solche Stellung ein, daß der Arbeitsanschluß A des Hydraulikventils 38 mit dem Tankanschluß T verbunden ist, während der Arbeitsanschluß B in Verbindung mit dem axialen Druckanschluß P steht. Das unter Druck stehende Hydraulikmedium gelangt über radiale Öffnungen 65 aus dem Hohlkolben 41 in den Arbeitsanschluß B. Von hier aus strömt das Hydraulikmedium in axial verlaufende, im Ventilgehäuse 27 liegende Bohrungen 66, die als Sacklochbohrungen ausgebildet und an ihrem der Nockenwelle 2 zugewandten Ende durch ein Verschlußteil 67 geschlossen sind. In die Bohrungen 66 münden Bohrungen 68, die im Boden einer Ringnut 69 in der äußeren Mantelfläche 70 des Ventilgehäuses 27 vorgesehen sind. In die Ringnut 69 münden die Bohrungen 63 im Rotorgrundkörper 8. Fig. 5 shows an enlarged view of the hydraulic valve of the camshaft adjuster. In Fig. 5 the case is shown that the hydraulic medium supplied via the axial pressure port P from the camshaft 2 flows via the check valve 59 into the hollow piston 41. He assumes such a position that the working port A of the hydraulic valve 38 is connected to the tank port T, while the working port B is in communication with the axial pressure port P. The pressurized hydraulic fluid passes through radial openings 65 from the hollow piston 41 in the working port B. From here, the hydraulic fluid flows into axially extending, located in the valve housing 27 holes 66, which are formed as blind holes and at its the camshaft 2 end facing by a Closure 67 are closed. In the holes 66 open holes 68 which are provided in the bottom of an annular groove 69 in the outer surface 70 of the valve housing 27. In the annular groove 69 open the holes 63 in the rotor body. 8

In der Mantelfläche 70 des Ventilgehäuses 27 ist eine weitere Ringnut 71 vorgesehen, in deren Boden über den Umfang verteilt Bohrungen 72 münden, die die Ringnut 71 mit axialen Bohrungen 73 im Ventilgehäuse 27 verbinden. Wie Fig. 5 zeigt, sind die Bohrungen 73 kürzer als die Bohrungen 66. Die Bohrungen 73 münden in die der Nockenwelle 2 zugewandte Stirnseite des Ventilgehäuses 27 und sind durch ein Verschlußteil 74 geschlossen. In die Ringnut 71, die axialen Abstand von der Ringnut 69 hat, münden die radialen Bohrungen 64 im Rotorgrundkörper 8. In die axialen Sacklochbohrungen 73 münden über den Umfang verteilt angeordnete radiale Bohrungen 75, die nahe dem inneren Ende der Sacklochbohrungen 73 vorgesehen sind und diese mit den Hohlkolben 41 radial durchsetzende Bohrungen 76 verbinden. Über sie kann das Hydraulikmedium dem Tankanschluß T zugeführt werden.In the lateral surface 70 of the valve housing 27, a further annular groove 71 is provided, in the bottom distributed over the circumference of holes 72 open, which connect the annular groove 71 with axial bores 73 in the valve housing 27. As Fig. 5 shows, the holes 73 are shorter than the holes 66. The holes 73 open into the camshaft 2 facing the end face of the valve housing 27 and are closed by a closure member 74. In the annular groove 71, the axial distance from the annular groove 69, open the radial holes 64 in the rotor body 8. In the axial blind holes 73 open distributed over the circumference arranged radial holes 75 which are provided near the inner end of the blind holes 73 and this connect with the hollow piston 41 radially passing holes 76. About them, the hydraulic medium can be supplied to the tank port T.

Fig. 6 zeigt, daß im Ventilgehäuse 27 des Hydraulikventils 38 wenigstens eine axial verlaufende Tankbohrung 77 vorgesehen ist, die ebenfalls in die der Nockenwelle 2 zugewandte Stirnseite des Ventilgehäuses 27 mündet und dort mit einem Verschlußteil 78 geschlossen ist. An dem vom Verschlußteil 78 abgewandten Ende ist die Tankbohrung 77 mit einer Ringnut 79 verbunden, die im Ventilgehäuse 27 vorgesehen ist und in die Radialbohrungen 80 münden, die die Ventilbuchse 60 durchsetzen und über den Umfang gleichmäßig verteilt angeordnet sind. Über diese Radialbohrungen 80 ist die Ringnut 79 mit einer weiteren Ringnut 81 verbunden, die in der Innenseite der Ventilbuchse 60 vorgesehen ist und in die Radialbohrungen 82 münden, die den Hohlkolben 41 in unmittelbarer Nähe seines Bodens 42 durchsetzen. Fig. 6 shows that in the valve housing 27 of the hydraulic valve 38 at least one axially extending tank bore 77 is provided, which also opens into the camshaft 2 facing end face of the valve housing 27 and is closed there with a closure member 78. At the end facing away from the closure member 78, the tank bore 77 is connected to an annular groove 79 which is provided in the valve housing 27 and open into the radial bores 80, which pass through the valve sleeve 60 and distributed uniformly over the circumference. About these radial bores 80, the annular groove 79 is connected to a further annular groove 81 which is provided in the inside of the valve sleeve 60 and open into the radial bores 82 which pass through the hollow piston 41 in the immediate vicinity of its bottom 42.

Am Boden der Ringnut 81 liegt axialgesichert ein elastisch verformbares Ringband 83 unter elastischer Vorspannung an. Es verschließt die Radialbohrungen 80 der Ventilbuchse 60 gegen den Hohlkolben 41. Das Ringband 83 bildet somit ein Rückschlagventil, das verhindert, daß unter Druck stehendes Hydraulikmedium über den Innenraum des Hohlkolbens 41 und dessen Radialbohrungen 82 in die Tankbohrung 77 gelangen kann.At the bottom of the annular groove 81 is axially secured an elastically deformable annular band 83 under elastic bias. It closes the radial bores 80 of the valve sleeve 60 against the hollow piston 41. The annular band 83 thus forms a check valve that prevents pressurized hydraulic fluid can pass through the interior of the hollow piston 41 and its radial bores 82 in the tank bore 77.

Bei der in Fig. 6 dargestellten Stellung des Hohlkolbens 41 gelangt das von der Nockenwelle 2 dem Hydraulikventil 38 axial zugeführte Hydraulikmedium über den Druckanschluß P in den Hohlkolben 41. Von hier aus strömt das Hydraulikmedium über die ihn durchsetzenden Radialbohrungen 65 (Fig. 5) und die Axialbohrungen 66 zum Arbeitsanschluß B. Von hier aus strömt das Druckmedium in die zugehörigen Druckkammern des Nockenwellenverstellers. Das aus der jeweils anderen Druckkammer verdrängte Hydraulikmedium gelangt gemäß Fig. 6 über den Arbeitsanschluß A und die Bohrungen 75, 76 in die Tankbohrung 77. Von hier aus strömt das Hydraulikmedium über die Ringnut 79 und die Radialbohrungen 80 zum Ringband 83. Es wird unter dem Druck des Mediums elastisch nach innen gebogen, so daß die Radialbohrungen 80 in der Ventilbuchse 60 freigegeben werden. Das Hydraulikmedium kann darum über die Ringnut 81 und die Radialbohrungen 82 in den Hohlkolben 41 strömen. Dieses verdrängte Medium vermischt sich mit dem über den Druckanschluß P zugeführten, unter Druck stehenden Hydraulikmedium, das über den Arbeitsanschluß B den jeweiligen Druckkammern des Nockenwellenverstellers zugeführt wird. Das als Rückschlagventil dienende Ringband 83 verhindert, daß das unter Druck stehende Hydraulikmedium in die Tankbohrung 77 gelangt.At the in Fig. 6 illustrated position of the hollow piston 41 passes from the camshaft 2 to the hydraulic valve 38 axially supplied hydraulic fluid via the pressure port P in the hollow piston 41. From here, the hydraulic medium flows through the radial bores passing through 65 ( Fig. 5 ) and the axial bores 66 to the working port B. From here, the pressure medium flows into the associated pressure chambers of the camshaft adjuster. The displaced from the other pressure chamber hydraulic medium passes according to Fig. 6 via the working port A and the holes 75, 76 in the tank bore 77. From here, the hydraulic medium flows It is elastically bent inwards under the pressure of the medium, so that the radial bores 80 are released in the valve sleeve 60 via the annular groove 79 and the radial bores 80. The hydraulic medium can therefore flow through the annular groove 81 and the radial bores 82 into the hollow piston 41. This displaced medium mixes with the supplied via the pressure port P, pressurized hydraulic medium, which is supplied via the working port B to the respective pressure chambers of the camshaft adjuster. Serving as a check valve ring band 83 prevents the pressurized hydraulic fluid enters the tank bore 77.

Abweichend vom dargestellten Ausführungsbeispiel ist es auch möglich, das Hydraulikmedium außerhalb der Nockenwelle 2 radial dem Hydraulikventil 38 zuzuführen.Deviating from the illustrated embodiment, it is also possible to supply the hydraulic medium outside the camshaft 2 radially to the hydraulic valve 38.

Claims (21)

  1. Camshaft adjuster for combustion engines of motor vehicles, with a stator (3), and a rotor (1) which can be rotated relative to it, between which pressure chambers (13, 14) are provided, and can be connected via conduits to at least one valve (38), via which pressure medium can be fed to the appropriate pressure chambers (13, 14),
    the valve (38) being arranged on the side of the camshaft adjuster facing away from the camshaft connection, in such a way that the rotor (1) is seated rotatably on a housing (27) of the valve (38),
    the rotor (1) having a central receptacle (32) for the valve (38),
    the valve (38) being on the same axis as the camshaft connection.
  2. Camshaft adjuster according to Claim 1,
    characterized in that the valve (38) projects out of the receptacle (32) of the rotor (1), and advantageously is held in a fixed position with its part (28) which projects out of the receptacle (32) of the rotor (1).
  3. Camshaft adjuster according to one of Claims 1 to 2,
    characterized in that the valve housing (27) has a flange (28) which is directed radially outward.
  4. Camshaft adjuster according to one of Claims 1 to 3,
    characterized in that the valve (38) is covered by a cover (44), which advantageously is fixed on the flange (28) of the valve housing (27).
  5. Camshaft adjuster according to Claim 3 or 4,
    characterized in that the flange (28) of the valve housing (27) is fixed to a covering cap (25), which at least partly overlaps the camshaft adjuster.
  6. Camshaft adjuster, in particular according to one of the preceding claims,
    characterized in that the valve (38) is provided as a bearing of the camshaft adjuster.
  7. Camshaft adjuster according to one of the preceding claims,
    characterized in that a filter (58) is connected upstream from the valve (38).
  8. Camshaft adjuster according to one of the preceding claims,
    characterized in that a non-return valve (59) to block against the pressure connection (P) is connected upstream from the valve (38).
  9. Camshaft adjuster according to Claim 8,
    characterized in that the non-return valve (59) is connected upstream from the filter (58).
  10. Camshaft adjuster according to one of Claims 7 to 9,
    characterized in that the filter (58) and the non-return valve (59) are combined into one unit, which advantageously has a housing (48), which preferably is bolted into the valve housing (27).
  11. Camshaft adjuster according to one of Claims 8 to 10,
    characterized in that the unit projects into a bolt (35), which advantageously has an axial hole (51) for feeding the pressure medium, and by which the rotor (1) is fixed to the camshaft (2).
  12. Camshaft adjuster according to Claim 11,
    characterized in that the bolt (35) is bolted into the camshaft (2).
  13. Camshaft adjuster according to one of the preceding claims,
    characterized in that the pressure medium can be fed via the camshaft (2).
  14. Camshaft adjuster according to one of Claims 1 to 11,
    characterized in that the pressure medium can be fed radially to the valve (38) outside the camshaft (2).
  15. Camshaft adjuster according to one of the preceding claims,
    characterized in that the valve (38) has a valve bush (60), which is inserted into the valve housing (27) and advantageously has a flange (61), which is directed radially outward, and with which the valve bush (60) is in an indentation (62) on the face of the valve housing (27).
  16. Camshaft adjuster according to Claim 15,
    characterized in that the flange (61) of the valve bush (60) is secured by the cover (44), which is fixed to the valve housing (27).
  17. Camshaft adjuster according to one of Claims 1 to 16,
    characterized in that the valve housing (27) has at least one axial hole (66, 73), which can be connected to the working connection (A, B) of the valve (38).
  18. Camshaft adjuster according to one of Claims 1 to 17,
    characterized in that the valve housing (27) has at least one axial tank hole (77), which can be connected to the tank connection (T) of the valve (38).
  19. Camshaft adjuster according to Claim 18,
    characterized in that the tank hole (77) is connected to the interior of a tubular piston (41) of the valve (38), and that advantageously, between the tank hole (77) and the interior of the tubular piston (41), at least one non-return valve (83) which closes against the tank hole (77) is arranged.
  20. Camshaft adjuster according to Claim 19,
    characterized in that the non-return valve (83) is arranged within the valve bush (60), which advantageously has an annular band, which when elastically prestressed is adjacent to the interior wall of the valve bush (60) in the region of at least one radial through opening (80).
  21. Camshaft adjuster according to Claim 19 or 20,
    characterized in that the interior of the tubular piston (41) is connected to the pressure connection (P).
EP04010748.4A 2003-05-12 2004-05-06 Camshaft phasing device for internal combustion engine Not-in-force EP1477636B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10322394A DE10322394A1 (en) 2003-05-12 2003-05-12 Camshaft adjuster for internal combustion engines of motor vehicles
DE10322394 2003-05-12

Publications (4)

Publication Number Publication Date
EP1477636A2 EP1477636A2 (en) 2004-11-17
EP1477636A3 EP1477636A3 (en) 2005-08-24
EP1477636B1 EP1477636B1 (en) 2010-02-17
EP1477636B2 true EP1477636B2 (en) 2015-05-27

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ID=33016439

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04010748.4A Not-in-force EP1477636B2 (en) 2003-05-12 2004-05-06 Camshaft phasing device for internal combustion engine

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EP (1) EP1477636B2 (en)
JP (1) JP2004340142A (en)
AT (1) ATE458128T1 (en)
DE (2) DE10322394A1 (en)

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Also Published As

Publication number Publication date
DE502004010755D1 (en) 2010-04-01
JP2004340142A (en) 2004-12-02
DE10322394A1 (en) 2004-12-02
EP1477636A3 (en) 2005-08-24
ATE458128T1 (en) 2010-03-15
EP1477636B1 (en) 2010-02-17
EP1477636A2 (en) 2004-11-17

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