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EP1749146B1 - Dispositif de reglage d'arbre a cames - Google Patents

Dispositif de reglage d'arbre a cames Download PDF

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Publication number
EP1749146B1
EP1749146B1 EP05737740A EP05737740A EP1749146B1 EP 1749146 B1 EP1749146 B1 EP 1749146B1 EP 05737740 A EP05737740 A EP 05737740A EP 05737740 A EP05737740 A EP 05737740A EP 1749146 B1 EP1749146 B1 EP 1749146B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
valve piston
hydraulic fluid
piston
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
EP05737740A
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German (de)
English (en)
Other versions
EP1749146A1 (fr
Inventor
Mike Kohrs
Udo Friedsmann
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP1749146A1 publication Critical patent/EP1749146A1/fr
Application granted granted Critical
Publication of EP1749146B1 publication Critical patent/EP1749146B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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

Definitions

  • the invention relates to a camshaft adjuster for the relative angular displacement of a camshaft with respect to a driving crankshaft, with a hydraulically actuated adjusting device with chambers in and out of which for angular adjustment on chamber-specific pressure medium channels alternately a hydraulic fluid is zumarinbar and discharged, and with a control valve via which the Hydraulic fluid supplied via a pump can be fed to the pressure medium ducts or discharged from the pressure medium ducts into a tank, whereby working ports A and B leading to the pressure medium ducts, a pressure port P coupleable to the pump and a drain port T coupleable to the tank are provided on the valve body of the control valve , Which working ports A and B depending on the desired angle adjustment via a controlled via a camshaft adjuster externally arranged decoupled tension or pressure magnet movable valve piston huiwei se with the pressure port P or the drain port T are coupled.
  • camshaft via which the valve movement of the intake and exhaust valves of the internal combustion engine is controlled, is motion-coupled to the crankshaft of the engine via a timing chain or timing belt, that is, the camshaft is moved via the crankshaft driven.
  • camshaft adjusters are integrated via which the relative angle that the camshaft to the crankshaft occupies, can be adjusted. That is, both shafts may be slightly twisted relative to one another, with the result that the actuation timing of the valves actuated via the camshaft changes.
  • camshaft adjusters are designed, for example, as vane-type adjusters and comprise a rotor which is connected in a rotationally fixed manner to the camshaft and a stator which is coupled to the crankshaft via the timing chain or the timing belt.
  • rotor On the rotor radially outwardly projecting wings are provided which engage between radially inwardly projecting stops on the stator, which on the one hand limit the twisting movement and on the other hand form chamber walls.
  • the chambers are bounded by the respective side of a rotor-side wing and by the sides of the stator-side stops.
  • a hydraulic fluid is pressed or withdrawn for rotation of the rotor relative to the stator and thus for angular adjustment, including using a control valve, usually a 4/3-way valve , At this working ports A and B are provided, each leading to a chamber A and a chamber B of each chamber pair.
  • the control valve itself is designed as a central valve in the camshaft adjuster configuration in question, it is centrally, inserted centrally in the camshaft adjuster or in its rotor and connected to the camshaft, that is, the control valve rotates with the adjuster or the rotor.
  • a valve piston is integrated, which is axially movable, wherein its displacement is controlled by a camshaft adjuster externally positioned, arranged for example on a motor or other third object train or pressure magnet.
  • the magnet is at this Embodiment thus not integrated in the stage.
  • one or the other working port A or B is now coupled to the pressure port P, so that hydraulic fluid is conducted into the associated chamber A or B, while the respective other chamber is connected to the valve-side drain port, so that the In the unloaded chamber liquid can be withdrawn through the drain port to the tank down.
  • the rotor can be hydraulically rotated with respect to the stator. To hold a set angle of rotation between the stops of the valve piston can close both working ports A and B and thus the associated chambers and almost.
  • the pressure port P is provided with the valve longitudinal axis aligned end face on the valve body.
  • the supplied under pressure hydraulic fluid presses against an end face of the often hollow cylindrical valve piston, before it passes depending on the piston position in the respective working port A or B.
  • the magnetic force counteracts the spring which acts on the valve piston and moves the valve piston into its basic position (P - B - A - T) when the electromagnet is de - energized.
  • the spring is adapted to the system (magnetic force, hydraulic flow and pressure forces, piston travel, piston friction, etc.).
  • the invention is therefore based on the problem of specifying a camshaft adjuster, which allows a secure placement of the valve piston even with high applied fluid pressure.
  • a camshaft adjuster of the type mentioned that the liquid distribution in the control valve, ie in the valve body or the valve piston or between these two, is designed such that the hydraulic fluid at substantially oppositely directed surfaces of the valve piston engages, so act on the valve piston local and each other substantially oppositely directed forces.
  • the flow path for the hydraulic fluid is designed so that the valve piston is loaded by the fluid at two oppositely directed surfaces, so that out set oppositely directed, directed on the valve piston forces that compensate each other at least partially.
  • the total force exerted on the valve piston by the fluid supply is consequently significantly reduced in comparison to the prior art embodiments, which results in that the external control magnet points to the valve piston or its extended control rod pointing towards the magnet , force to be exerted is significantly reduced.
  • any pressure peaks in the supply of hydraulic fluid can in no case adversely affect the valve control.
  • the pressure port P can be perpendicular to the valve axis and open into a connected between the valve piston and the valve body, position-dependent connectable to the working port A annular channel which leads into the hollow cylindrical, closed at both ends valve piston, the cavity position-dependent with the working port B is connectable, wherein the frontal cavity surfaces are acted upon by the hydraulic fluid with pressure.
  • the two working ports can be connected in a position-dependent manner with the outlet connection situated at an angle, preferably perpendicular to the valve longitudinal axis, via a ring channel formed between the valve piston and the valve body.
  • the outlet connection situated at an angle, preferably perpendicular to the valve longitudinal axis, via a ring channel formed between the valve piston and the valve body.
  • both the pressure port P and the drain port T and the working ports A and B perpendicular to the valve axis extending and arranged in the order B- T- A- P or A- T- B- P, wherein In the latter case, a Switzerlandfederr is used to switch the valve in the de-energized state, ie without acting magnet in the basic position P - B - A - T.
  • An alternative embodiment of a control valve provides that the pressure port P is at an angle, preferably perpendicular to the valve axis and opens in a formed between the valve piston and the valve body position-dependent connectable to the working port A or B annulus, wherein the working ports A, B position-dependent via connecting holes can be connected to the cavity of the hollow cylindrical valve piston, which cavity leads to the drain port T, which in this embodiment is axially aligned with the valve longitudinal axis.
  • the pressure port P and the working ports A and B can run perpendicular to the longitudinal axis of the valve and be arranged in the order A-P-B.
  • a further embodiment provides that the pressure port P is located in the valve longitudinal axis and opens via deflecting channels formed in a position-dependent connected to the working port A or B annular space between the valve piston and the valve body, wherein the working ports A, B position-dependent via connecting holes with the cavity the hollow cylindrical valve piston can be connected, which leads cavity to the drain port T.
  • valve embodiment provides that the pressure port P is aligned with the valve longitudinal axis and opens into the hollow cylindrical valve piston, are provided at the radial openings through which the hydraulic fluid passes into the annular space formed between the valve piston and the valve body, from the front side the valve piston is limited.
  • the hydraulic fluid is guided axially into the hollow cylindrical valve piston.
  • the liquid from the piston enters the rear, formed between the piston and the valve body annulus, where it is virtually deflected and presses on the opposite opposite to the cavity end wall piston outer surface. Also in this embodiment, therefore, are virtually opposite each other directed surfaces acted so that oppositely directed local forces act on the valve piston.
  • Fig. 1 shows a control valve 1 consisting of a valve body 2, on which in the illustrated embodiment, an external thread 3 is provided, via which the valve body is screwed camshaft side after insertion into the rotor of an adjustment.
  • a valve piston 4 is guided axially movable, which can be moved against a restoring force generated by a spring 5.
  • a push rod 6 is arranged on the valve piston 4, which cooperates with an external control magnet, not shown in detail, to move the valve piston against the spring or with spring support in the other direction.
  • the control magnet is as described externally arranged for example on the engine, so it does not move, unlike the control valve 1, which rotates with the rotor.
  • the control valve 1 is enclosed encapsulated in the housing of the camshaft adjuster, via which housing the push rod 6 cooperates with the magnet.
  • valve body 2 On the valve body 2 several different connections are provided.
  • a working port A and a working port B are shown, via which a hydraulic fluid can be conveyed into corresponding chambers of the device designed as a vane-cell adjusting device, depending on the position of the valve piston 4.
  • a pressure port P not one of them pump shown in detail, the hydraulic fluid is supplied.
  • a drain port T is shown, is conveyed via the discharged hydraulic fluid in a tank not shown in detail.
  • various control edges 7a (which are assigned to the working port A) and 7b (which are assigned to the working port B) are provided.
  • the working ports A and B are connected via these control edges either to the pressure port P or to the discharge port T via the channel 41, depending on whether fluid is supplied into the chambers, which are assigned to the working port A, and out of the chambers , which are assigned to the working port B, liquid to be discharged and conveyed into the tank via the drain port T, or vice versa.
  • the position is controlled by the magnet not shown in detail.
  • annular channel. 8 provided in the pressure port P opens.
  • valve-piston-side openings 9 of the annular channel opens 8- depending on the piston position in case of need to be connected to the working port A- in the cavity 10 of the valve piston 4.
  • the hydraulic fluid presses in the cavity 10 on two opposite end faces 12, 13, which limit the cavity seen axially. This results in a force F p1 or F p2 directed in each case on the valve piston, which are obviously directed opposite to one another.
  • the two forces - which are ideally equal in the ideal case - thus compensate each other, so that the valve piston 4 in the ideal case virtually quiescent, as far as forces acting on him on the liquid supply.
  • Fig. 2 shows a camshaft adjuster 14 according to the invention, with a rotor 15 and a stator 16.
  • the rotor 15 is rotatably connected to the control valve 1, this mimic is rotatable with respect to the stator 16 which is connected to the timing chain or the timing belt with the crankshaft.
  • a plurality of vanes 17 are provided on the rotor, which bear tightly against the inner wall 18 of the stator and are bounded by the respective two chambers, which are each acted upon via a working port A or B with fluid or withdrawn from there via the respective working fluid connections can. A closer approach to this is not required after the basic design of such camshaft adjuster is well known.
  • Fig. 3 shows a further embodiment according to the invention a camshaft adjuster 19, the basic structure of the camshaft adjuster 14 from Fig. 2 corresponds, but the integrated control valve 20 is constructed differently. It also has a P-pressure port and the two working ports A and B as well as a drain port T. However, here lies the pressure port P, which is guided from the outside via the valve body 21 inwardly, quasi-centered between the working ports A and B, which via the position of the valve piston 22 in a corresponding manner as described with respect to the control valve 1 with the pressure port P or the drain port T, which runs axially here with the valve longitudinal axis, are connectable.
  • the liquid is supplied in such a way that on the valve piston 22 substantially compensating each other, resulting from the pressed liquid forces act.
  • the pressure port P opens into an annular channel 23 which is bounded by the control flanks 24, 25, via which the connection to the working ports A and B are opened or closed.
  • the liquid thus presses on these oppositely directed flanks, so that inevitably set oppositely directed forces that compensate each other.
  • a liquid distribution space is realized, which allows a compensation of forces.
  • FIG. 4 another control valve 26, which can be integrated equally into a phaser as shown in the preceding figures.
  • This control valve also has a valve body 27 and a valve piston 28.
  • the pressure port P is here axially to the valve longitudinal axis, while the working ports A and B, not shown in detail and the drain port T are vertical to the valve longitudinal axis.
  • valve piston is mounted against a return spring 29 here. It is hollow cylindrical, the liquid supplied enters it. On the opposite side, however, a plurality of openings 30 are provided, so that the liquid can enter the surrounding this piston end annular space 31. There, the liquid presses on the piston outer surface 32, which faces the end face 33 in the interior of the piston. Again, two oppositely directed surfaces are thus again subjected to the fluid, so that mutually oppositely directed forces arise, which act on the valve piston 28.
  • FIG. 5 a further control valve 34 according to the invention, whose pressure port P also extends axially, the working ports A and B are on the valve body 35 perpendicular to the longitudinal axis, while the drain port T from the valve piston 36 is vertical to the longitudinal axis.
  • the hydraulic fluid is first deflected via corresponding guide channels 37 and then placed in an annular space 38, the of two surfaces 39, 40 is limited to the valve piston 36.
  • This embodiment substantially corresponds to the valve design Fig. 3 , There are also here equal, but oppositely directed forces on the valve piston 36 a. However, here is the supply of hydraulic fluid axially, while the valve in Fig. 3 done from the side.

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

Abstract

L'invention concerne un dispositif de réglage d'arbre à cames permettant le déplacement angulaire relatif d'un arbre à cames par rapport à un vilebrequin menant. Ce dispositif comporte un organe de réglage à commande hydraulique, pourvu de chambres dans lesquelles un fluide hydraulique peut être introduit et desquelles ce dernier peut être évacué alternativement par le biais de canaux à fluide sous pression spécifiques aux chambres pour le déplacement angulaire, ainsi qu'une soupape de commande, par l'intermédiaire de laquelle le fluide hydraulique, refoulé par une pompe, peut être amené aux canaux à fluide sous pression et évacués de ceux-ci vers un réservoir. Des raccords de travail A et B menant aux canaux à fluide sous pression, un raccord de pression P pouvant être relié à la pompe et un raccord de sortie T pouvant être relié au réservoir sont prévus sur le corps de la soupape de commande, lesdits raccords de travail A et B pouvant être reliés soit au raccord de pression P soit au raccord de sortie T en fonction du déplacement angulaire souhaité au moyen d'un piston de soupape dont le déplacement est commandé par l'intermédiaire d'un électroaimant de traction ou de poussée séparé, placé à l'extérieur du dispositif de réglage d'arbre à cames. L'invention se caractérise en ce que la chambre de distribution du fluide dans la soupape de commande (1, 20, 26, 34) est conçue, de sorte que le fluide hydraulique est appliqué sur des surfaces sensiblement opposées du piston de soupape (4, 22, 28, 36), de sorte que des forces locales (Fp1, Fp2), sensiblement opposées, agissent sur le piston de soupape (4, 22, 28, 36).

Claims (5)

  1. Dispositif de réglage d'arbre à cames pour le réglage angulaire relatif d'un arbre à cames par rapport à un vilebrequin à entraîner, comprenant un dispositif de réglage à commande hydraulique avec des chambres, dans lesquelles et hors desquelles un liquide hydraulique peut être acheminé et évacué en alternance pour le réglage angulaire par le biais de canaux de fluide sous pression spécifiques aux chambres, ainsi qu'une soupape de commande (1) intégrée centralement dans le dispositif de réglage et tournant avec lui, par le biais de laquelle le liquide hydraulique acheminé par le biais d'une pompe peut être acheminé aux canaux de fluide sous pression ou peut être évacué hors des canaux de fluide sous pression dans un réservoir, un raccord de pression P pouvant être accouplé à la pompe et un raccord d'écoulement T pouvant être accouplé au réservoir étant prévus sur le corps de soupape (2) de la soupape de commande (1) vers les raccords de travail A et B conduisant aux canaux de fluide sous pression, lesquels raccords de travail A et B, en fonction du réglage angulaire souhaité, pouvant être accouplés de manière sélective au raccord de pression P ou au raccord d'écoulement T par le biais d'un piston de soupape (4) déplaçable de manière commandée par le biais d'un aimant de traction ou de pression désaccouplé, disposé à l'extérieur du dispositif de réglage d'arbre à cames, l'espace de distribution de liquide étant réalisé dans la soupape de commande (1) de telle sorte que le liquide hydraulique agisse sur des surfaces du piston de soupape (4) orientées essentiellement de manière opposée l'une à l'autre, de sorte que des forces locales et orientées essentiellement de manière opposée l'une à l'autre (Fp1, Fp2) agissent sur le piston de soupape (4), caractérisé en ce que le raccord de pression P est situé suivant un certain angle, de préférence perpendiculairement à l'axe de la soupape, et débouche dans un canal annulaire (8) formé entre le piston de soupape (4) et le corps de soupape (2), pouvant être connecté en fonction de la position au raccord de travail A, lequel conduit au piston de soupape (4) cylindrique creux, fermé des deux côtés frontaux, dont la cavité (10) peut être connectée en fonction de la position au raccord de travail B, les surfaces frontales (12, 13) de la cavité étant sollicitées en pression par le biais du liquide hydraulique.
  2. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que les deux raccords de travail A, B peuvent être connectés par le biais d'un canal annulaire (41) réalisé entre le piston de soupape (4) et le corps de soupape (2) en fonction de la position au raccord d'écoulement T situé perpendiculairement par rapport à l'axe longitudinal de la soupape.
  3. Dispositif de réglage d'arbre à cames selon la revendication 1 ou 2, caractérisé en ce que le raccord de pression P, le raccord d'écoulement T et les raccords de travail A et B sont disposés de manière à s'étendre perpendiculairement à l'axe longitudinal de la soupape et dans l'ordre B- TA-P ou A-T-B-P.
  4. Dispositif de réglage d'arbre à cames pour le réglage angulaire relatif d'un arbre à cames par rapport à un vilebrequin à entraîner, comprenant un dispositif de réglage à commande hydraulique avec des chambres, dans lesquelles et hors desquelles un liquide hydraulique peut être acheminé et évacué en alternance pour le réglage angulaire par le biais de canaux de fluide sous pression spécifiques aux chambres, ainsi qu'une soupape de commande (26) intégrée centralement dans le dispositif de réglage et tournant avec lui, par le biais de laquelle le liquide hydraulique acheminé par le biais d'une pompe peut être acheminé aux canaux de fluide sous pression ou peut être évacué hors des canaux de fluide sous pression dans un réservoir, un raccord de pression P pouvant être accouplé à la pompe et un raccord d'écoulement T pouvant être accouplé au réservoir étant prévus sur le corps de soupape (27) de la soupape de commande (26) vers les raccords de travail A et B conduisant aux canaux de fluide sous pression, lesquels raccords de travail A et B, en fonction du réglage angulaire souhaité, pouvant être accouplés de manière sélective au raccord de pression P ou au raccord d'écoulement T par le biais d'un piston de soupape déplaçable de manière commandée par le biais d'un aimant de traction ou de pression désaccouplé, disposé à l'extérieur du dispositif de réglage d'arbre à cames, l'espace de distribution de liquide étant réalisé dans la soupape de commande (26) de telle sorte que le liquide hydraulique agisse sur des surfaces du piston de soupape (28) orientées essentiellement de manière opposée l'une à l'autre, de sorte que des forces locales et orientées essentiellement de manière opposée l'une à l'autre (Fp1, Fp2) agissent sur le piston de soupape (28), caractérisé en ce que le raccord de pression P s'étend en affleurement avec l'axe longitudinal de la soupape et débouche dans le piston de soupape cylindrique creux (28), sur lequel sont prévus des alésages radiaux (30), à travers lesquels le liquide hydraulique parvient dans l'espace annulaire (31) formé entre le piston de soupape (28) et le corps de soupape (27), qui est limité par le côté frontal du piston de soupape (28).
  5. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que les forces opposées l'une à l'autre (Fp1, Fp2) ont essentiellement la même amplitude.
EP05737740A 2004-05-22 2005-05-04 Dispositif de reglage d'arbre a cames Expired - Lifetime EP1749146B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004025215A DE102004025215A1 (de) 2004-05-22 2004-05-22 Nockenwellenversteller
PCT/EP2005/004849 WO2005113943A1 (fr) 2004-05-22 2005-05-04 Dispositif de reglage d'arbre a cames

Publications (2)

Publication Number Publication Date
EP1749146A1 EP1749146A1 (fr) 2007-02-07
EP1749146B1 true EP1749146B1 (fr) 2011-04-27

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EP05737740A Expired - Lifetime EP1749146B1 (fr) 2004-05-22 2005-05-04 Dispositif de reglage d'arbre a cames

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Country Link
US (1) US20070169730A1 (fr)
EP (1) EP1749146B1 (fr)
DE (2) DE102004025215A1 (fr)
WO (1) WO2005113943A1 (fr)

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DE102007020525A1 (de) * 2007-05-02 2008-11-06 Schaeffler Kg Nockenwellenversteller für eine Brennkraftmaschine mit integriertem Ventilschieber
DE102007058491A1 (de) * 2007-12-05 2009-06-10 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102009022930A1 (de) 2009-05-27 2010-12-02 Schaeffler Technologies Gmbh & Co. Kg Eingriffseinheit einer Drehwinkelbegrenzungsvorrichtung
DE102010002713B4 (de) * 2010-03-09 2013-12-05 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit Steuerventil für die hydraulische Verstellung der Phasenlage einer Nockenwelle
DE102010023864B4 (de) 2010-06-15 2018-03-08 Hilite Germany Gmbh Zentralventil für einen Schwenkmotornockenwellenversteller
DE102010044637A1 (de) * 2010-09-07 2012-03-08 Hydraulik-Ring Gmbh Zentralventil
US8695548B2 (en) 2010-12-10 2014-04-15 Denso Corporation Valve timing control apparatus
US20150144211A1 (en) * 2012-05-25 2015-05-28 Schaeffler Technologies Gmbh & Co. Kg Control valve of a camshaft adjuster
DE102014200462A1 (de) * 2014-01-14 2015-01-08 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102014207989A1 (de) 2014-04-29 2015-10-29 Schaeffler Technologies AG & Co. KG Hydraulischer Phasensteller einer Nockenwelle
DE102014214251B4 (de) 2014-07-22 2017-09-14 Schaeffler Technologies AG & Co. KG Hydraulischer Phasensteller einer Nockenwelle
DE102014223995A1 (de) 2014-11-25 2016-05-25 Schaeffler Technologies AG & Co. KG Steuerventil für einen Nockenwellenversteller

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DE502005011305D1 (de) 2011-06-09
US20070169730A1 (en) 2007-07-26
EP1749146A1 (fr) 2007-02-07
WO2005113943A1 (fr) 2005-12-01

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