EP1749146A1 - Dispositif de reglage d'arbre a cames - Google Patents

Dispositif de reglage d'arbre a cames

Info

Publication number
EP1749146A1
EP1749146A1 EP05737740A EP05737740A EP1749146A1 EP 1749146 A1 EP1749146 A1 EP 1749146A1 EP 05737740 A EP05737740 A EP 05737740A EP 05737740 A EP05737740 A EP 05737740A EP 1749146 A1 EP1749146 A1 EP 1749146A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve piston
pressure
camshaft adjuster
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.)
Granted
Application number
EP05737740A
Other languages
German (de)
English (en)
Other versions
EP1749146B1 (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 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 KG filed Critical Schaeffler KG
Publication of EP1749146A1 publication Critical patent/EP1749146A1/fr
Application granted granted Critical
Publication of EP1749146B1 publication Critical patent/EP1749146B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 adjustment of a camshaft with respect to a driving crankshaft, with a hydraulically actuated adjusting device with chambers into and from which hydraulic fluid can be alternately supplied and removed for adjusting the angle via chamber-specific pressure medium channels, and with a control valve via that the hydraulic fluid supplied via a pump can be supplied to the pressure medium channels or can be removed from the pressure medium channels into a tank, working connections A and B leading to the pressure medium channels on the valve body of the control valve, a pressure connection P which can be coupled to the pump and a pressure port P which can be coupled to the tank Drain connection T is provided, which working connections A and B, depending on the desired angle adjustment, can be moved via a valve piston controlled by a decoupled pull or pressure magnet arranged externally to the camshaft adjuster can be coupled to the pressure port P or the drain port T in some cases.
  • the camshaft via which the valve movement of the intake and exhaust valves of the internal combustion engine is controlled, is motionally coupled to the crankshaft of the engine via a timing chain or a timing belt, that is, the camshaft is Belwelle driven.
  • camshaft adjusters are integrated, via which the relative angle that the camshaft has to the crankshaft occupies, can be adjusted. This means that both shafts can be rotated somewhat relative to each other, which means that the actuation time of the valves actuated via the camshaft changes.
  • camshaft adjusters are designed, for example, as vane-cell adjusters and comprise a rotor which is connected to the camshaft in a rotationally fixed manner and a stator which is coupled to the crankshaft via the timing chain or the timing belt.
  • Radially outwardly projecting vanes are provided on the rotor, which engage between stops projecting radially inward on the stator, which limit the twisting movement on the one hand and form chamber walls on the other.
  • the chambers are delimited by the respective side of a rotor-side wing and by the sides of the stator-side stops.
  • a hydraulic fluid is now pressed or withdrawn to rotate the rotor with respect to the stator and thus to adjust the angle, for which purpose a control valve, usually a 4/3-way valve, is used , Working connections A and B are provided on this, each leading to a chamber A and a chamber B of a respective pair of chambers.
  • the control valve itself is designed as a central valve, it is inserted centrally, centrally in the camshaft adjuster or in its rotor and connected to the camshaft, that is to say the control valve thus rotates with the adjuster or the rotor.
  • a valve piston which is axially movable, is integrated in the control valve itself, its displacement being controlled by means of a tension or compression magnet positioned externally to the camshaft adjuster, for example arranged on an engine or other third-party object.
  • the magnet is So embodiment not integrated in the adjuster.
  • one or the other working port A or B is now coupled to the pressure port P, so that hydraulic fluid is led into the assigned chamber A or B, while the other chamber is connected to the valve-side drain port, so that the liquid in the unloaded chamber can be drawn off to the tank via the drain connection.
  • the rotor can be rotated hydraulically with respect to the stator.
  • the valve piston can almost close both working ports A and B and thus the associated chambers.
  • the pressure connection P is provided on the end face of the valve body in alignment with the longitudinal axis of the valve.
  • the hydraulic fluid supplied under pressure presses against an end face of the often hollow cylindrical valve piston before it passes into the respective working port A or B depending on the piston position.
  • the result of this is that, as a result of the liquid supply, a considerable force is exerted on the piston, which the external control magnet has to overcome in order to move the valve piston in an opposite direction.
  • the magnetic force is counteracted by the spring acting on the valve piston, which moves the valve piston into its basic position (P - B - A - T) when the electromagnet is de-energized.
  • the spring is matched to the system (magnetic force, hydraulic flow and pressure forces, piston travel, piston friction, etc.). If, in addition, the fluid-related force acting in the opposite direction now has to be overcome, this can, in extreme cases with high fluid pressure, result in the magnetic force acting not being strong enough to displace the valve piston or that of the electrical force applied to the magnet Power-assigned movement path of the valve piston is not completely covered. Summary of the invention
  • the invention is therefore based on the problem of specifying a camshaft adjuster which allows the valve piston to be set securely even when the fluid pressure is high.
  • the fluid distribution space in the control valve that is to say in the valve body or the valve piston or between the two, is designed in such a way that the hydraulic fluid on surfaces which are essentially oppositely directed of the valve piston, so that local and essentially opposite forces act on the valve piston.
  • the flow path for the hydraulic fluid is designed such that the valve piston is loaded by the liquid on two opposite surfaces, so that this directed load set opposite forces acting on the valve piston, which at least partially compensate each other.
  • the total force resulting from the liquid supply and acting on the valve piston is significantly reduced in comparison with the designs of the prior art, which leads to the fact that the control rod extending from the external control magnet to the valve piston or its extended control rod, which points towards the magnet force to be exerted is significantly reduced. In this way, any pressure peaks in the supply of the hydraulic fluid can in no case have an adverse effect on the valve control.
  • the pressure port P can be perpendicular to the valve axis and open into an annular channel formed between the valve piston and the valve body and which, depending on the position, can be connected to the working port A and which leads into the hollow cylindrical valve piston, the cavity of which is position-dependent and closed can be connected to the working connection B, the end cavity surfaces being pressurized by the hydraulic fluid.
  • the surfaces over which the oppositely directed forces are introduced into the valve piston are, in this embodiment, the end surfaces delimiting the end face of the cavity. Since it is a hollow cylindrical piston part with a constant cavity diameter, the surfaces are consequently essentially the same size, so that forces of essentially the same size and in opposite directions are also established.
  • the working connection B can also be connected to the ring channel or instead of the working connection B, the working connection A can be connected to the cavity, that is, the respective work connections can also be interchanged. This applies to all the embodiments described below.
  • the two working connections can be connected via a ring channel formed between the valve piston and the valve body, depending on the position, to the drain connection lying at an angle, preferably perpendicular to the longitudinal axis of the valve.
  • all connections that is to say both the pressure connection P and the drain connection T and the working connections A and B, are expediently arranged perpendicular to the valve axis and arranged in the order B - T - A - P or A - T - B - P
  • a tension spring is used to switch the valve to the basic position P - B - A - T when de-energized, ie without a magnet.
  • An alternative embodiment of a control valve provides that the pressure connection P lies at an angle, preferably perpendicular to the valve axis, and opens into an annular space formed between the valve piston and the valve body and can be connected to the working connection A or B depending on the position, the working connections A, B depending on the position Can be connected via connecting bores to the cavity of the hollow cylindrical valve piston, which cavity leads to the outlet connection T, which in this embodiment runs axially in alignment with the longitudinal valve axis.
  • the pressure connection P and the working connections A and B can expediently run perpendicular to the longitudinal axis of the valve and be arranged in the order A-P-B.
  • a further embodiment variant provides that the pressure connection P lies in the longitudinal axis of the valve and opens via deflection channels into an annular space formed between the valve piston and the valve body and which can be connected to the working connection A or B depending on the position, the working connections A, B depending on the position via connecting bores with the cavity of the hollow cylindrical valve piston can be connected, which cavity leads to the drain port T.
  • a further valve embodiment provides that the pressure connection P runs in alignment with the longitudinal valve axis and opens into the hollow cylindrical valve piston, at which radial openings are provided, through which the hydraulic fluid reaches the annular space formed between the valve piston and the valve body, which is from the front side of the valve piston is limited.
  • the hydraulic fluid is guided axially into the hollow cylindrical valve piston.
  • the piston openings provided according to the invention the liquid from the piston enters the rear annular space formed between the piston and the valve body, where it is virtually deflected and presses on the piston outer surface lying opposite the cavity end wall. In this embodiment, too, quasi are opposed to one another directed surfaces acted on, so that oppositely directed local forces act on the valve piston.
  • FIG. 1 shows a sectional view of a control valve of a first embodiment
  • FIG. 2 shows a camshaft adjuster according to the invention with the integrated control valve from FIG. 1,
  • FIG. 3 shows a camshaft adjuster according to the invention of a second embodiment with an integrated control valve of a second embodiment
  • Fig. 4 shows a control valve of a third embodiment
  • valve 1 shows a control valve 1 consisting of a valve body 2, on which, in the exemplary embodiment shown, an external thread 3 is provided, by means of which the valve body is screwed on the camshaft side after insertion into the rotor of an adjusting device.
  • a valve piston 4 is axially movably guided in the valve body 2 and can be moved against a restoring force generated by a spring 5.
  • a push rod 6 is arranged on the valve piston 4 and cooperates with an external control magnet, not shown in more detail, in order to move the valve piston in the other direction against the spring or with spring support.
  • the control magnet is arranged externally on the motor, for example, so it does not move, unlike the control valve 1, which rotates with the rotor.
  • the control valve 1 is encapsulated in the housing of the camshaft adjuster, via which housing the push rod 6 interacts with the magnet.
  • valve body 2 Several different connections are provided on the valve body 2.
  • 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 through which one does not Pump shown in detail, the hydraulic fluid is supplied.
  • a drain connection T is shown, via which hydraulic fluid to be discharged is conveyed into a tank (not shown in more detail).
  • valve piston 4 Various control edges 7a (which are assigned to working port A) and 7b (which are assigned to working port B) are provided on valve piston 4. Depending on the position of the valve piston, the working connections A and B are connected via these control edges to either the pressure connection P or the drain connection T via the channel 41, depending on whether liquid is supplied to and from the chambers in the chambers which are assigned to the working connection A , which are assigned to the working connection B, liquid is to be discharged and conveyed into the tank via the drain connection T, or vice versa. The position is controlled by the magnet, not shown in detail.
  • Ring channel 8 is provided, into which the pressure port P opens.
  • the annular channel 8 which, depending on the piston position, can be connected to the working port A if necessary - opens into the cavity 10 of the valve piston 4.
  • the cavity 10 can be connected to the working port B via corresponding openings 11, if the latter the hydraulic fluid is to be supplied.
  • the hydraulic fluid presses in the cavity 10 on two mutually opposite end faces 12, 13, which axially limit the cavity.
  • FIG. 2 shows a camshaft adjuster 14 according to the invention, with a rotor 15 and a stator 16.
  • the rotor 15 is connected in a rotationally fixed manner to the control valve 1, this facial expression is related to the stator 16, which is connected to the timing chain or the timing belt to the crankshaft, rotatably.
  • a plurality of vanes 17 are provided on the rotor, which bear tightly against the inner wall 18 of the stator and are delimited by the two chambers, each of which is supplied with fluid via a working connection A or B or from there via the respective working connections fluid can be deducted. It is not necessary to go into this in greater detail after the basic structure of such camshaft adjusters is sufficiently known.
  • FIG. 3 shows a further embodiment of a camshaft adjuster 19 according to the invention, which corresponds in principle to the camshaft adjuster 14 from FIG. 2, but the integrated control valve 20 is constructed differently. It also has a P pressure connection and the two working connections A and B as well as a drain connection T. However, here the pressure connection P, which is guided inwards from the outside via the valve body 21, is located quasi-centrally between the working connections 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 connection P or the outlet connection T, which here runs axially with the valve along the longitudinal axis, can be connected.
  • valve piston 22 is also controlled by a control magnet, not shown, against one, not shown Return spring is movable
  • the liquid supply takes place in such a way that largely compensating forces resulting from the pressed-in liquid act on the valve piston 22.
  • the pressure port P opens into an annular channel 23 which is delimited by the control flanks 24, 25, via which the connection to the working ports A and B are opened or closed.
  • the liquid therefore presses on these oppositely directed flanks, so that inevitably opposite forces are created which compensate for one another.
  • a liquid distribution space is realized that allows force compensation.
  • FIG. 4 shows a further control valve 26 which can likewise be integrated into a camshaft adjuster as shown in the previous figures.
  • This control valve also has a valve body 27 and a valve piston 28.
  • the pressure port P is located axially to the longitudinal axis of the valve, while the working ports A and B, not shown, and the drain port T are vertical to the longitudinal valve axis.
  • valve piston is also supported here against a return spring 29. It is hollow cylindrical, the liquid supplied enters it. However, a plurality of openings 30 are provided on the opposite side, so that the liquid can enter the annular space 31 surrounding this piston end. There, the liquid presses on the piston outer surface 32, which lies opposite the end surface 33 in the interior of the piston. Here, too, two oppositely directed surfaces are again exposed to the fluid, so that oppositely directed forces result which act on the valve piston 28.
  • FIG. 5 shows a further control valve 34 according to the invention, the pressure connection P of which also runs axially, the working connections A and B go off on the valve body 35 perpendicular to the longitudinal axis, while the outlet connection T goes out of the valve piston 36 vertically to the longitudinal axis.
  • the hydraulic fluid is first deflected via corresponding guide channels 37 and then placed in an annular space 38 which is closed by two surfaces 39, 40 on the valve piston 36 is limited.
  • This embodiment corresponds essentially to the valve design from FIG. 3; here, too, forces of the same size, but oppositely directed, occur on the valve piston 36.
  • the supply of the hydraulic fluid is axial here, while it takes place from the side in the valve in FIG. 3.
  • Valve body 32 piston outer surface
  • Valve piston 34 control valve

Landscapes

  • 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).
EP05737740A 2004-05-22 2005-05-04 Dispositif de reglage d'arbre a cames Active 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 true EP1749146A1 (fr) 2007-02-07
EP1749146B1 EP1749146B1 (fr) 2011-04-27

Family

ID=34966090

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05737740A Active EP1749146B1 (fr) 2004-05-22 2005-05-04 Dispositif de reglage d'arbre a cames

Country Status (4)

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

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DE102005034275B4 (de) 2005-07-22 2018-02-15 Daimler Ag Nockenwellenstellventilvorrichtung
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
DE102013203951A1 (de) * 2012-05-25 2013-11-28 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
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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Also Published As

Publication number Publication date
DE102004025215A1 (de) 2005-12-08
DE502005011305D1 (de) 2011-06-09
EP1749146B1 (fr) 2011-04-27
US20070169730A1 (en) 2007-07-26
WO2005113943A1 (fr) 2005-12-01

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