EP1477636B1 - Dispositif de déphasage d'arbre à cames pour moteur à combustion interne - Google Patents

Dispositif de déphasage d'arbre à cames pour moteur à combustion interne Download PDF

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Publication number
EP1477636B1
EP1477636B1 EP04010748A EP04010748A EP1477636B1 EP 1477636 B1 EP1477636 B1 EP 1477636B1 EP 04010748 A EP04010748 A EP 04010748A EP 04010748 A EP04010748 A EP 04010748A EP 1477636 B1 EP1477636 B1 EP 1477636B1
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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.)
Expired - Lifetime
Application number
EP04010748A
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German (de)
English (en)
Other versions
EP1477636B2 (fr
EP1477636A2 (fr
EP1477636A3 (fr
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
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.)
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Publication date
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Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP1477636A2 publication Critical patent/EP1477636A2/fr
Publication of EP1477636A3 publication Critical patent/EP1477636A3/fr
Publication of EP1477636B1 publication Critical patent/EP1477636B1/fr
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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.
  • valve is at least partially housed within the camshaft adjuster. As a result, no additional installation space is needed for the valve in the internal combustion engine.
  • the camshaft adjuster according to Fig. 1 to 4 serves to the opening time of intake and exhaust valves of an internal combustion engine of a motor vehicle to the power requirement to adapt to 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 webs 9, which abut with their faces 10 flat against an inner cylindrical surface 11 of the shell 4 of the stator 3 sealing.
  • 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 is provided, in which in the operation of the camshaft adjuster dirt is collected, which is located in the pressure medium and which is displaced radially outwardly into the dirt collecting grooves 19 due to the centrifugal forces. 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.
  • a central opening 34 in the flange 33 projects a central screw 35, which is screwed into an axial and centrally arranged 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 bush 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 medium passes through radial openings 65 from the hollow piston 41 in the working port B. From here, the hydraulic medium 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 which 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.

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

Claims (24)

  1. Dispositif de déphasage d'arbre à cames pour moteur à combustion interne de véhicule automobile, avec un stator (3) et un rotor (1) pouvant tourner par rapport à lui, entre lesquels des chambres de pression (13, 14) sont prévues, lesdites chambres étant reliées à au moins une soupape (38) via des conduites, l'agent de mise sous pression pouvant être amené aux chambres de pression (13, 14) respectives via ladite soupape, caractérisé en ce que la soupape (38) est disposée de telle sorte au niveau du côté du dispositif de déphasage d'arbre à cames opposé au raccord d'arbre à cames que le rotor (1) repose de façon pivotante sur un boîtier (27) de la soupape (38).
  2. Dispositif de déphasage d'arbre à cames, notamment selon la revendication 1, caractérisé en ce que la soupape (38) est logée au moins en partie dans le dispositif de déphasage d'arbre à cames.
  3. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 2, caractérisé en ce que le rotor (1) comprend un logement central (32) pour la soupape (38).
  4. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la soupape (38) se situe dans le même axe que le raccord d'arbre à cames.
  5. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que la soupape (38) ressort du logement (32) du rotor
    (1) et est maintenue fixement en place de façon avantageuse avec sa partie (28) saillant du logement (32) du rotor (1).
  6. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le boîtier de soupape (27) comprend une collerette (28) orientée vers l'extérieur dans le plan radial.
  7. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la soupape (38) est recouverte par un cache (44) fixé de façon avantageuse sur la collerette (28) du boîtier de soupape (27).
  8. Dispositif de déphasage d'arbre à cames selon la revendication 6 ou 7, caractérisé en ce que la collerette (28) du boîtier de soupape (27) est fixée au niveau d'une calotte de recouvrement (25) qui emboîte au moins en partie le dispositif de déphasage d'arbre à cames.
  9. Dispositif de déphasage d'arbre à cames, notamment selon l'une quelconque des revendications précédentes, caractérisé en ce que la soupape (38) prend la forme d'un palier du dispositif de déphasage d'arbre à cames.
  10. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un filtre (58) est raccordé en amont de la soupape (38).
  11. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une soupape anti-retour (59) fermée contre le raccord de pression (P) est raccordée en amont de la soupape (38).
  12. Dispositif de déphasage d'arbre à cames selon la revendication 11, caractérisé en ce que la soupape anti-retour (59) est raccordée en amont du filtre (58).
  13. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 10 à 12, caractérisé en ce que le filtre (58) et la soupape anti-retour (59) forment une unité fonctionnelle comportant de façon avantageuse un boîtier (48) de préférence vissé dans le boîtier de soupape (27).
  14. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 11 à 13, caractérisé en ce que l'unité fonctionnelle ressort dans une vis (35) comportant de façon avantageuse un alésage axial (51) pour l'amenée de l'agent de mise sous pression, le rotor (1) étant fixé à l'arbre à cames (2) au moyen de ladite vis.
  15. Dispositif de déphasage d'arbre à cames selon la revendication 14, caractérisé en ce que la vis (35) est vissée dans l'arbre à cames (2).
  16. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que l'agent de mise sous pression peut être amené via l'arbre à cames (2).
  17. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 14, caractérisé en ce que l'agent de mise sous pression peut être amené radialement à la soupape (38) en passant à l'extérieur de l'arbre à cames (2).
  18. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que la soupape (38) comporte une bague de soupape (60) insérée dans le boîtier de soupape (27) et comportant de façon avantageuse une collerette (61) orientée vers l'extérieur dans le plan radial, avec laquelle la bague de soupape (60) repose dans un renfoncement (62) côté avant du boîtier de soupape (27).
  19. Dispositif de déphasage d'arbre à cames selon la revendication 18, caractérisé en ce que la collerette (61) de la bague de soupape (60) est bloquée par le cache (44) fixé au niveau du boîtier de soupape (27).
  20. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 19, caractérisé en ce que le boîtier de soupape (27) comporte au moins un alésage axial (66, 73) pouvant être relié au raccord de travail (A, B) de la soupape (38).
  21. Dispositif de déphasage d'arbre à cames selon l'une quelconque des revendications 1 à 20, caractérisé en ce que le boîtier de soupape (27) comporte au moins un alésage de réservoir (77) axial pouvant être relié au raccord de réservoir (T) de la soupape (38).
  22. Dispositif de déphasage d'arbre à cames selon la revendication 21, caractérisé en ce que l'alésage de réservoir (77) est relié à l'espace intérieur d'un piston creux (41) de la soupape (38) et que de façon avantageuse, au moins une soupape anti-retour (83) se fermant contre l'alésage de réservoir (77) est disposée entre l'alésage de réservoir (77) et l'espace intérieur du piston creux (41).
  23. Dispositif de déphasage d'arbre à cames selon la revendication 22, caractérisé en ce que la soupape anti-retour (83) est disposée à l'intérieur de la bague de soupape (60) comportant de façon avantageuse un bandeau annulaire reposant sous précontrainte élastique contre la paroi intérieure de la bague de soupape (60) dans la zone d'au moins une ouverture de passage (80) radiale.
  24. Dispositif d'ajustement d'arbre à cames selon la revendication 22 ou 23, caractérisé en ce que l'espace intérieur du piston creux (41) est relié au raccord de pression (P).
EP04010748.4A 2003-05-12 2004-05-06 Dispositif de déphasage d'arbre à cames pour moteur à combustion interne Expired - Lifetime EP1477636B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10322394 2003-05-12
DE10322394A DE10322394A1 (de) 2003-05-12 2003-05-12 Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen

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EP1477636A2 EP1477636A2 (fr) 2004-11-17
EP1477636A3 EP1477636A3 (fr) 2005-08-24
EP1477636B1 true EP1477636B1 (fr) 2010-02-17
EP1477636B2 EP1477636B2 (fr) 2015-05-27

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JP (1) JP2004340142A (fr)
AT (1) ATE458128T1 (fr)
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US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster

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DE502005010369D1 (de) * 2004-05-14 2010-11-25 Schaeffler Kg Nockenwellenversteller
DE102004036096B4 (de) * 2004-07-24 2017-09-14 Schaeffler Technologies AG & Co. KG Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005013085B3 (de) * 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
WO2006127347A1 (fr) * 2005-05-23 2006-11-30 Borgwarner Inc Clapet anti-retour integre
DE102005052481A1 (de) * 2005-11-03 2007-05-24 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
WO2009005999A1 (fr) * 2007-07-02 2009-01-08 Borgwarner Inc. Came concentrique avec clapets anti-retour dans la bobine pour un déphaseur
JP5105187B2 (ja) * 2008-07-31 2012-12-19 アイシン精機株式会社 弁開閉時期制御装置
US8322317B2 (en) 2009-01-28 2012-12-04 Aisin Seiki Kabushiki Kaisha Valve timing control apparatus
DE102010002713B4 (de) 2010-03-09 2013-12-05 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit Steuerventil für die hydraulische Verstellung der Phasenlage einer Nockenwelle
DE102010013777A1 (de) 2010-04-03 2011-10-06 Hydraulik-Ring Gmbh Zentralventil
DE202010006605U1 (de) 2010-04-03 2010-11-18 Hydraulik-Ring Gmbh Zentralventil
DE102010023864B4 (de) 2010-06-15 2018-03-08 Hilite Germany Gmbh Zentralventil für einen Schwenkmotornockenwellenversteller
DE102010026853B4 (de) 2010-07-12 2024-05-02 Schaeffler Technologies AG & Co. KG Steuerventil zur Steuerung von Druckmittelströmen eines Nockenwellenverstellers
DE102010044637A1 (de) * 2010-09-07 2012-03-08 Hydraulik-Ring Gmbh Zentralventil
DE102010061521A1 (de) 2010-12-23 2012-06-28 Hydraulik-Ring Gmbh Schwenkmotorversteller mit einem Zentralventil
DE102011000522A1 (de) 2011-02-04 2012-08-09 Hydraulik-Ring Gmbh Schwenkmotorversteller mit einem Hydraulikventil
DE102011000591B4 (de) 2011-02-09 2018-03-08 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
DE102011000822B4 (de) 2011-02-11 2012-11-08 Hydraulik-Ring Gmbh Gehäuse mit einem Schwenkmotorversteller
US8534246B2 (en) * 2011-04-08 2013-09-17 Delphi Technologies, Inc. Camshaft phaser with independent phasing and lock pin control
JP5692289B2 (ja) * 2012-09-28 2015-04-01 株式会社デンソー バルブタイミング調整装置
DE102012221876B4 (de) * 2012-11-29 2021-01-07 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung
DE102013017540A1 (de) * 2013-10-22 2015-04-23 Daimler Ag Nockenwellenversteller für eine Brennkraftmaschine
DE102014102617A1 (de) * 2014-02-27 2015-08-27 Hilite Germany Gmbh Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle
DE102016118710A1 (de) * 2016-08-04 2018-02-08 Hilite Germany Gmbh Nockenwellenverstellsystem für eine Verbrennungskraftmaschine
US11261765B1 (en) 2020-08-25 2022-03-01 Borgwamer Inc. Control valve assembly of a variable cam timing phaser

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DE19817319C2 (de) * 1998-04-18 2001-12-06 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
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DE10029261A1 (de) * 2000-06-14 2001-12-20 Deutz Ag Nockenwellenverschwenkeinrichtung

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Publication number Priority date Publication date Assignee Title
US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8794201B2 (en) 2009-10-27 2014-08-05 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and method for mounting a friction disc on a rotor
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster

Also Published As

Publication number Publication date
EP1477636B2 (fr) 2015-05-27
DE10322394A1 (de) 2004-12-02
EP1477636A2 (fr) 2004-11-17
DE502004010755D1 (de) 2010-04-01
ATE458128T1 (de) 2010-03-15
EP1477636A3 (fr) 2005-08-24
JP2004340142A (ja) 2004-12-02

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