EP2365193A1 - Régulateur de phases d'arbres à cames doté d'une soupape de commande pour le réglage hydraulique de la position de phase d'un arbre à cames - Google Patents

Régulateur de phases d'arbres à cames doté d'une soupape de commande pour le réglage hydraulique de la position de phase d'un arbre à cames Download PDF

Info

Publication number
EP2365193A1
EP2365193A1 EP11156630A EP11156630A EP2365193A1 EP 2365193 A1 EP2365193 A1 EP 2365193A1 EP 11156630 A EP11156630 A EP 11156630A EP 11156630 A EP11156630 A EP 11156630A EP 2365193 A1 EP2365193 A1 EP 2365193A1
Authority
EP
European Patent Office
Prior art keywords
camshaft
valve
piston
housing
valve 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
EP11156630A
Other languages
German (de)
English (en)
Other versions
EP2365193B1 (fr
Inventor
Uwe Dr. Meinig
Jürgen Bohner
Claus Welte
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.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP2365193A1 publication Critical patent/EP2365193A1/fr
Application granted granted Critical
Publication of EP2365193B1 publication Critical patent/EP2365193B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—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
    • F01L2001/34426—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
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location 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
    • F01L2001/34446—Fluid accumulators for the feeding circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a camshaft phaser with a control valve for the hydraulic adjustment of the phase position of a camshaft relative to a crankshaft of an internal combustion engine.
  • the invention relates to the camshaft phaser as such and also an internal combustion engine with the mount camshaft phaser.
  • the internal combustion engine may in particular be a drive motor for or in a motor vehicle.
  • camshaft phasers To increase power and torque, but also to reduce fuel consumption and exhaust gas emissions from internal combustion engines for road vehicles, camshaft phasers have become popular for varying intake or exhaust timing.
  • hydraulic, actuated by engine oil phasing have prevailed on the principle of hydraulic Schwenkmotars.
  • hydraulically actuated camshaft phasers have found distribution in which a control valve for controlling the pressurization of the adjustment of the phase position serving pressure chambers and the actuation of the control valve serving solenoid are arranged centrally on the axis of rotation of the camshaft.
  • the pressure oil to the rotating jointly with the camshaft phaser via a provided in the camshaft channel also centrally arranged control valve is supplied.
  • the pressure oil is supplied to the rotating camshaft from the cylinder head, typically via one of the camshaft bearings, preferably a camshaft thrust bearing.
  • the invention relates to phaser of the kind described in particular.
  • the control valve is conveniently arranged and designed so that the valve characteristic is independent of the pressure of the oil. Otherwise, for example, the adjustment of intermediate positions in the phasing of the camshaft would be made difficult or even prevented. It is therefore desirable that the Pressure oil despite exerting pressure during operation of the engine no or only negligible low axial forces can exert on the valve piston of the control valve in order not to interfere with the balance of forces acting on the valve piston electromagnet and this usually counteracting valve spring.
  • camshaft phaser To circumvent the problem described camshaft phaser are known, for example from the DE 198 48 706 A1 and the DE 103 22 394 A1 whose central control valve is arranged non-rotatably relative to a machine housing of the internal combustion engine, so that the camshaft rotates relative to the control valve.
  • the various oil inlets and outlets to and from the control valve are separated by means of shaft seals, but this causes increased design complexity and significant additional costs. This results in increased demands on the tolerances for the components, which determine the radial position of the control valve relative to the camshaft.
  • a known from the cited prior art further problem causes the preferred arrangement of the coil of the electromagnet rotatably relative to the engine housing of the internal combustion engine, while the armature of the electromagnet is rotatably connected to the valve piston of the control valve.
  • the rotating armature has practically unavoidable radial offset to the coil, which causes radial forces acting on the armature and thus on the valve piston, which must be absorbed by the sliding pair of valve housing and valve piston. This in turn complicates the fulfillment of the requirement for the lowest possible hysteresis of the valve characteristic and increases the wear on the sliding surfaces of the sliding mating.
  • the invention accordingly relates to a camshaft phaser with a preferably central control valve for the controlled supply and discharge of a hydraulic fluid into and out of a pressure chamber, which serves to adjust the rotational angular position of a camshaft relative to a crankshaft of an internal combustion engine.
  • the pressure chamber may be either a Voreilungshunt, which adjusts the camshaft relative to the crankshaft when pressurized on advance, or to a retardation chamber, which adjusts the camshaft when pressurized to lag.
  • a pressure relief is accompanied by a return in the reverse direction of rotation.
  • the camshaft phaser comprises one or more advance advance pressure chambers and one or more additional retard pressure chambers.
  • the phase angle of the camshaft is adjusted by the pressurized fluid by means of the control valve in either the pressure chamber (s) for advance or in the pressure chamber (s) for lag initiated and the other type of pressure chamber (s) with a Low pressure side of the fluid is connected, preferably with a reservoir for the fluid such as an oil sump.
  • the fluid may, in particular, be a lubricating oil used for lubricating the internal combustion engine, in motor vehicles typically the engine oil.
  • the control valve comprises a valve housing with at least one working port and at least one reservoir port for the fluid.
  • the working port serves to supply this pressure fluid to the at least one pressure chamber of the phaser, and the reservoir port of the discharge to a present on the low pressure side of the fluid reservoir.
  • the working connection preferably also serves for the discharge from the pressure chamber via the reservoir connection.
  • the control valve further comprises a valve piston which is axially displaceable in the valve housing between a first and a second piston position.
  • the valve piston is hollow, thus has an axial cavity, in which via a valve piston inlet fluid from a high pressure side, a pressurized fluid, can be introduced. The introduced pressurized fluid is passed out of the cavity via a piston outlet.
  • the piston outlet In the first piston position of the piston outlet is connected to the working port of the valve housing, so that the pressure fluid can be supplied through the valve piston via the working port of the pressure chamber.
  • the piston outlet In the second piston position, the piston outlet is disconnected from the working port of the valve housing.
  • the valve piston outlet is connected in the second piston position with the reservoir port of the valve housing.
  • the valve housing has a housing inlet, through which the fluid of the high-pressure side can be introduced into the valve housing and through the piston inlet connected to the housing inlet into the cavity of the valve piston.
  • Part of the camshaft phaser is also a coupled with the valve piston actuator for axial adjustment of the valve piston.
  • the actuator is preferably an electromagnetic actuator and may, in particular, be an axial-stroke electromagnet.
  • the coupling is such that the actuator acts on the valve piston only with an axial compressive force, but the application of an axial tensile force would alternatively or possibly also additionally conceivable.
  • the valve piston for the coupling with the actuator on a coupling member which projects through a valve housing closing Stirnverschulsswand.
  • the coupling member is accordingly axially movable back and forth relative to the end closure wall of the valve housing, nevertheless seals the end closure wall in close fit with the coupling member, the valve housing with the required tightness.
  • the coupling member preferably acts as an axial plunger.
  • the valve piston In order to prevent the fluid from exerting a practically relevant axial pressure force, a resulting axial thrust, in spite of the flow through the hollow valve piston, the valve piston has a radial widening, ie a radially widened piston portion which is widened by a correspondingly expanded one Housing portion of the valve housing is surrounded in a tight fit and can be acted upon in a direction away from the end closure wall axial direction with the fluid of the high pressure side.
  • the expansion is dimensioned in cross-section so that the fluid acts on the valve piston in spite of the end closure wall projecting coupling member in both axial directions at least substantially equal in compressive force.
  • the axial cavity of the valve piston is preferably a central, cylindrical cavity, which expediently simply runs straight at the inlet end and thereby forms the piston inlet with a cross-sectional area corresponding to the cavity cross-section.
  • the fluid thus flows with little resistance into the valve piston and through the piston outlet to the pressure chamber when the valve piston assumes the corresponding axial piston position.
  • the piston outlet is preferably a radial outlet at the periphery of the valve piston.
  • the axial inflow and radial outflow is conducive to a simple course of the inlets and outlets and, accordingly, an extensive geometric design freedom of the channel cross sections of the supply to the valve piston and the discharge to the pressure chamber and the reservoir.
  • the housing inlet is formed on an axial end side of the valve housing, so that the fluid flowing in the control valve already flows axially into the control valve.
  • the housing inlet can also be a radial inlet on the circumference of the valve housing.
  • a housing inlet leading obliquely into the control valve should not be excluded.
  • the Arbeüsan gleich preferably extends radially through the circumference of the valve housing. If, as preferred, a further working connection is present, this also preferably extends just straight radially through the valve housing. A radial course is also for the reservoir port, and if another reservoir port is present, also for this advantage.
  • the reservoir connection, the optional further reservoir connection, the working connection or the optionally further working connection can also run obliquely through the circumference of the valve housing.
  • the control valve is preferably arranged to rotate with the camshaft. Preferably, it is inserted at an axial end of the camshaft in a central, open to the front end of the camshaft receiving space from the front end.
  • a co-rotating control valve in particular a central control valve with respect to the phaser, can in principle, however, also only be attached to the front end of the camshaft.
  • a central control valve rotating with the camshaft allows a space-saving design for the camshaft phaser and a geometrically simple supply of pressurized fluid through the camshaft.
  • the actuator is preferably arranged on the low pressure side of the fluid and may in particular be at atmospheric pressure, so that no special measures for a seal must be made.
  • the actuator is preferably arranged non-rotatably relative to the engine housing of the internal combustion engine, so that when advantageously with the camshaft rotatably arranged control valve, the coupling member of the valve piston relative to the actuator, the Actuator as a whole, is rotatable.
  • the actuator may, as already mentioned in particular be an electromagnetic actuator, with an electromagnetic coil and a relative to the coil axially movable armature, which is arranged non-rotatably relative to the coil or at least not rotatable, since the relative rotation in the coupling of coupling member and Actuator takes place.
  • the actuator and the coupling member are directly in a coupling engagement with each other.
  • the coupling is preferably only an axial pressure contact, in the case of direct engagement, a pressure contact of an actuating element of the actuator and the coupling member in which the actuating element, for example, said armature, axially presses against a front end of the coupling member.
  • valve piston in relation to the rotor of the phaser, with the camshaft rotatably connectable or connected control valve in combination with a valve piston which is rotatably arranged relative to the axially movable active element of the actuator, already alone advantageous without the compensation of any axial thrust. If such a combination of hydraulic part of the control valve and the actuator is realized, it is further preferred if the valve piston has the described axial cavity and thus can be flowed through by the fluid of the high pressure side.
  • the coupling may be carried out as disclosed in the present invention.
  • the coupling can also be designed such that, when the actuator is designed as an axial stroke actuator, its active element, for example the armature of a magnet, projects through the end closure wall of the valve housing and acts within the valve housing on the end face of the valve piston facing it.
  • its active element for example the armature of a magnet
  • such an active element can also form the coupling element of the invention claimed here.
  • valve piston may have an axial cavity, the piston feed would be in such embodiments, the said piston inlet. If the fluid to be controlled by means of the valve piston is not introduced into the valve piston, but guided to the outer circumference of the valve piston as described in the prior art, said piston feed is a depression formed on the circumference of the valve piston which connects the housing inlet in the corresponding piston position with the piston Connect working port and preferably circulates.
  • the coupling and the actuator are arranged so that the actuator can exert both axial tensile and compressive forces, the actuator so presses the valve piston in one of the piston positions and pulls in the other
  • the control valve comprises a spring member, preferably a mechanical spring such as a helical compression spring, which acts with its spring force: the actuating force of the actuator against the valve piston.
  • the spring member may advantageously be arranged so that it is supported directly with one spring end on the valve housing and with another spring end directly on the valve piston and thereby biases the valve piston in the corresponding axial direction.
  • the widening in the cross section is preferably dimensioned such that at least approximately, preferably exactly, the cross-sectional area with which the coupling member projects through the end closure wall is compensated.
  • the valve piston is preferably circular-cylindrical in the widened piston section on the outer circumference, so that the widening results in an annular area which is at least approximately, preferably precisely compensating for the cross-sectional area of the coupling element.
  • the control piston is at the end of the expansion, the end closure wall of the valve housing facing, acted upon by the fluid of the high pressure side.
  • this pressure fluid used for the compensation is supplied, for example, from outside the valve piston or even from outside the control valve, it corresponds to more preferred embodiments, when the fluid is guided through the axial cavity of the valve piston to the compensating surface formed by the expansion.
  • the cavity may have in its jacket or preferably in a Kolbenstimwand a single passage or a plurality of distributed around the central longitudinal axis of the valve piston arranged passages through which or the pressure fluid to the end closure wall of the valve housing facing end face of the valve piston, in particular also to the compensation surface Expansion, can flow.
  • the widening preferably forms the front end wall of the valve piston facing the end closure wall, from which preferably the coupling element protrudes in the direction of the actuator.
  • the compensation surface formed by the expansion is in such embodiments, one of the end closure wall axially immediately opposite end surface of the valve piston.
  • the shaping of the expansion at the end of the closure wall facing the end of the valve piston allows in a particularly simple manner a supply through the axial cavity at the end remote from the piston inlet end of the valve piston. As a result, the fiction, contemporary compensation can be decoupled from the control function of the control valve in a simple manner.
  • the flared housing portion extends axially beyond the flared piston portion to permit the axial displacements of the valve piston.
  • the valve piston On the side facing away from the end closure wall, the valve piston is preferably acted upon in the region of the expansion only with the fluid pressure of the low-pressure side.
  • the reservoir connection or a further reservoir connection is arranged in the widened housing section on the side of the widening remote from the end closure wall, so that at least substantially the fluid pressure of the reservoir prevails on this side.
  • the valve piston at a side facing away from the end closure wall, axially adjacent to the expansion then has a radial recess, preferably a circumferential recess.
  • the working port and the reservoir port of the valve housing are arranged and the recess axially so long that the working port is connected in the second piston position of the valve piston via the recess with the reservoir port.
  • the control edge is preferably arranged axially on the valve piston and the actuator is preferably controllable such that the valve piston can also be positioned in intermediate positions between the first and the second position, so that the control piston can only partly cover and partially release the reservoir connection. It is also advantageous if the axial speed with which the valve piston is moved from the first position in the direction of the second position or from the second position in the direction of the first position changed, so the valve piston can also be moved at different speeds ,
  • the camshaft phaser comprises a further pressure chamber for the fluid.
  • a further pressure chamber for the fluid.
  • either the one or the other is acted upon by the fluid of the high pressure side. Accordingly, pressurization of the one pressure chamber causes the camshaft to be retarded relative to the crankshaft in the direction of advance and on pressurization of the other in the counter-rotation direction.
  • the control valve is configured in such embodiments to selectively direct the pressurized fluid into either one pressure chamber or the other pressure chamber.
  • the valve housing has a further working port, through which the fluid can flow to the further pressure chamber.
  • the further working port is formed in the valve housing so that the piston outlet is connected in the second piston position with the other working port and is separated in the first piston position of the other working port.
  • the further working port is preferably connected to the reservoir so that the pressure fluid can flow out of the further pressure chamber via the further working port into the reservoir.
  • the valve piston may have a further radial recess, preferably also a circumferential recess which connects the further working port of the valve housing in the first piston position with the reservoir, preferably a further reservoir port of the valve housing connected to the reservoir.
  • these ports are preferably arranged so that axially between the two reservoir ports, the two working ports are arranged, so seen in the axial direction of one of the reservoir connections of this associated Work connection, on this the other work connection and on this the other working port associated reservoir port follows.
  • the adjustment paths covered by the valve piston to selectively connect either one working port with one type of pressure chamber (s) or the other working port with the other type of pressure chamber (s) can be kept short.
  • the inlets and outlets are arranged axially preferably in the following order: Close to or preferably at an axial end of the valve housing, the housing inlet is formed on this follows axially in the direction of the other end face of the valve housing, the other reservoir connection the further working port, then the first-mentioned working port and finally axially furthest away from the housing inlet, the first-mentioned reservoir port.
  • the camshaft phaser is designed in developments such that the supplied fluid, preferably any fluid flowing through the control valve, at a required for the adjustment of the phase position pressure relief of the pressure chamber by one or more rotating with the camshaft component (s) of the phaser into the machine housing flows back and not first in a mounted on the machine housing outside attachment housing, such as a chain case, flows out and must be led from there back to the reservoir.
  • the internal combustion engine for example, the engine housing, must not be set up in such embodiments for a return of the fluid flowing out of the phaser. The assembly of the phaser is facilitated.
  • the return extends in advantageous embodiments by the rotatably connected in the assembled state with the camshaft rotor of the phaser, which is for this purpose with a corresponding return, preferably provided by the rotor axially straight passage.
  • a single passage may form the return, it is preferred that the return includes a plurality of passages distributed about the axis of rotation of the rotor.
  • a further feedback in the stator may extend, wherein the further feedback formed for example by one or more bore (s) in the stator or by one or more groove-shaped or fully inner expansion (s) or radially outward from the stator and radially inside of the camshaft can be limited together. If the control valve has the said further reservoir connection, the fluid required for adjusting the phasing of the camshaft becomes fluid preferably fed back through both reservoir ports through the rotating with the camshaft phaser into the engine housing.
  • the feedback within the rotatable with the camshaft and rotating during operation of the internal combustion engine phaser is also on its own advantage, for example, without the compensation by widening of the valve piston, ie without the characteristics of the main claim.
  • the feedback within the Nockezawellen phaser namely within one or more component (s) of the phaser, which is arranged to rotate during operation of the internal combustion engine with the camshaft or is also generally advantageous and not only in conjunction with a hollow valve piston, which can be flowed through by the fluid.
  • a return within the phase adjuster can also be advantageous for those phase adjusters which have a central control valve with a valve piston to which the fluid is supplied only at the outer circumference, ie which is not flowed through.
  • a hollow valve piston is favorable in terms of the simplest possible channel course.
  • a central control valve with either a hollow and therefore flowed through or a non-flow-through valve piston also have an actuator which does not preferably have a relative to the coil non-rotating armature, but for example a rotatably connected to the valve piston armature.
  • valve piston may have an axial cavity, the piston feed would be in such embodiments, the said piston inlet. If the fluid to be controlled by means of the valve piston is not introduced into the valve piston, but guided to the outer circumference of the valve piston as described in the prior art, said piston feed is a depression formed on the circumference of the valve piston which connects the housing inlet in the corresponding piston position with the piston Connect working port and preferably circulates.
  • the valve housing may in particular be screwed to the camshaft, wherein the valve housing preferably has an external thread and the camshaft in a receiving space corresponding to an internal thread for the screw connection. If the valve housing and the camshaft are connected to one another by means of a screw connection, a screw head of the valve housing can also immediately close the said return for the fluid, if such is provided within the phaser.
  • the valve housing can serve in particular as a clamping screw for the assembly of the rotor and the stator of the camshaft phase adjuster, so that the phase adjuster is also mounted the same when the screw connection is made.
  • a valve housing formed as a central clamping screw can take over the function of a centering element for the rotor of the camshaft phaser by centering the rotor relative to the camshaft.
  • the valve housing may be formed in alternative embodiments as a housing cartridge, which is inserted axially into the camshaft and then secured axially with a securing device, such as a circlip.
  • a housing cartridge, but also a screw-valve housing can be secured axially additionally or exclusively cohesively, for example by a welded connection.
  • the valve housing can also be formed directly from the camshaft itself or be joined to an axial end of the camshaft by means of material connection. However, a positive or frictional mountable valve housing is given preference.
  • the front closure wall projected through by the coupling element can expediently be formed by a closure disk fastened firmly to a jacket of the valve housing.
  • the closure disk can be joined, for example, by pressing in, rolling or by means of screwed or welded connection with the valve housing jacket, which also includes combinations of the joining methods exemplified.
  • FIG. 1 shows a camshaft phaser in a longitudinal section.
  • the camshaft phaser is arranged at an end face of a camshaft 1 and serves to adjust the phase position, ie the rotational angular position of the camshaft 1 relative to a crankshaft of an internal combustion engine, for example a drive motor of a motor vehicle.
  • the camshaft 1 is rotatably mounted about an axis of rotation R in a machine housing 2 of the internal combustion engine, usually in a cylinder head housing.
  • the camshaft phaser comprises a stator 3, which can be rotated by the crankshaft, and a rotor 7, which is non-rotatably connected to the camshaft 1.
  • the stator 3 is composed of a drive wheel 4, for example a sprocket, a cover 6 and an impeller 5 arranged axially between the drive wheel 4 and the cover 6.
  • the drive wheel 4, the Impeller 5 and the lid 6 are rotatably connected to each other.
  • the stator 3 and the rotor 7 form a hydraulic swing motor.
  • FIG. 2 shows the stator-rotor assembly 3, 7 in a frontal plan view.
  • the cover 6 of the stator 3 is removed, so that the impeller 5 of the stator 3 and the rotor formed as a counter rotor 7 can be seen.
  • the impeller 5 forms the outer component and the rotor 7, the inner component of the swing motor.
  • the rotor 7 has radially outwardly projecting wings which form first pressure chambers 8 and second pressure chambers 9 with the vanes of the impeller 5 of the stator 3.
  • the pressure chambers 8 are respectively arranged in the circumferential direction to the left and the pressure chambers 9 to the right side of the wings of the rotor 7.
  • the rotor 7 rotates relative to the stator 3 in FIG FIG. 2 clockwise to maximum in the FIG. 2 assumed end position. If the pressure chambers 9 are pressurized and the pressure chambers 8 relieved in pressure, the rotor 7 rotates counterclockwise. The rotational movement relative to the stator 3 in one direction of rotation corresponds to an overfeed and the relative rotational movement in the other direction to a lag of the camshaft 1 relative to the crankshaft.
  • the camshaft phaser has a centrally arranged with respect to the stator-rotor assembly 3, 7 control valve with a valve housing 10 and in the valve housing 10 axially reciprocally movable and thus axially adjustable valve piston 20 arranged.
  • the valve piston 20 is hollow with an axially extending cavity 21, a piston inlet 22 at one axial end and a piston outlet 23, which leads radially through a jacket of the valve piston 20 surrounding the cavity 21.
  • the valve piston 20 has at its side facing away from the piston inlet 22 the other axial end of a coupling member 25 for a coupling with an actuator 15, which causes the axial displacement of the valve piston 20.
  • the coupling member 25 acts as an actuating tappet of the valve piston 20.
  • the coupling member 25 may be integrally formed with the piston skirt surrounding the cavity 21 in one piece or optionally be axially fixed with this. It protrudes at the front end of the valve piston 20, which faces the actuator 15 axially.
  • the coupling member 25 extends through an end closure wall 11 of the valve housing 10. The end closure wall 11 surrounds the coupling member 25 in close fitting and thus ensures in spite of the reciprocating coupling member 25 for the fluid-tight closure of the valve housing 10th
  • the actuator 15 is an electromagnetic actuator, in the embodiment, a Axialhub electromagnet, with a current-carrying coil 16 and an armature 17, which surrounds the coil 16.
  • the Coil 16 is rotatably connected to the engine housing 2 of the internal combustion engine.
  • the coil 16 is rotatably connected to a lid 2b, which in turn is fixedly connected to a mounted on the machine housing 2 phaser housing 2a.
  • the armature 17 is axially movable relative to the coil 16. It is with the coupling member 25 directly in a coupling engagement, which is formed as an axial pressure contact.
  • the armature 17 When energizing the coil 16 acts on the armature 17 an axially directed towards the coupling member 25 actuating force acting on the coupling member 25 and thus on the valve piston 20 in the coupling engagement, a pure axial pressure contact.
  • rotating valve piston 20 and the non-rotating actuator 15 preferably prevails only point contact.
  • the armature 17 preferably has a spherical surface at its end contacting the coupling member 25.
  • the coupling member 25 could have a spherical surface at its front end.
  • the contact end of the armature 17 is formed as a ball sliding bearing by a ball in a pan of the armature 17 is freely rotatably mounted there.
  • the control valve comprises a spring member 14 whose spring force counteracts the actuating force of the actuator 15.
  • the spring member 14 is supported directly on the valve housing 10 and in the direction of the actuator 15 on the valve piston 20.
  • the actuator 15 is driven by a control of the internal combustion engine, namely energized.
  • the control is preferably carried out via a stored in a memory of the engine control map, for example, depending on the speed of the crankshaft, the load or other or other relevant for the operation of the internal combustion engine parameters.
  • the valve piston 20 is arranged in a central axial cavity of the valve housing 10 in the manner explained back and forth movable. At its end remote from the end closure wall 11, it has an axial housing inlet P a which leads centrally into the housing cavity and can be fed with pressurized fluid via the camshaft 1, namely a pressure inlet P of the camshaft 1.
  • the fluid may in particular be a lubricating oil serving for lubricating the internal combustion engine, which also serves for lubricating, for example, the track bearing of the camshaft 1.
  • the pressurized fluid is supplied to the control valve by way of example as preferred by the thrust bearing of the camshaft 1, that is, the pressure port P is connected to the lubricating oil supply for the thrust bearing.
  • This pressurized fluid flows into the camshaft 1 at P, through the axial housing inlet P a into the valve housing 10 and into the cavity 21 through the piston inlet 22 in axial alignment with the housing inlet P a.
  • the cavity 21 branches laterally, by way of example, preferably in the radial direction , a piston outlet 23 from, through the the pressurized fluid depending on the axial position of the valve piston 20, either the Druckkammeni 8 or pressure chambers 9 is supplied to adjust the phase position of the rotor 7 relative to the stator 3 and thus the phase angle of the camshaft 1 relative to the crankshaft.
  • the piston outlet 23 is formed by radial passages distributed over the circumference of the valve piston 20 through the jacket of the valve piston 20.
  • the piston outlet 23 is arranged in an axially central portion of the valve piston 20.
  • the valve housing 10 has through its jacket leading connections for the supply and discharge of the fluid to and from the pressure chambers 8 and 9. These are a working port A and a working port B, a reservoir port T a assigned to the working port A , and a reservoir port T B assigned to the working port B.
  • the connections A to T B are in each case straight passages through the jacket of the valve housing 10.
  • the connections A, B and T A extend radially over the shortest path through the jacket.
  • the reservoir port T B extends obliquely outward into the phaser housing 2 a.
  • FIG. 3 is only the control valve with the valve housing 10 and the valve piston 20 in cross-section AA of FIG. 1 shown.
  • the sectional view shows in particular the piston outlet 23 of the valve piston 20 and the working port B of the valve housing 10, which is also arranged distributed over the circumference of the valve housing 10, radially extending and therefore short passages through the shell of the valve housing 10 is formed.
  • the terminals A, T A and T B are also each formed by a plurality of distributed around the central axis R arranged passageways.
  • FIG. 4 shows from FIG. 1 only the central area of the cam phaser.
  • the FIGS. 1 . 3 and 4 show the valve piston 20 in a first axial piston position in which it holds the spring member 14. In the first piston position, the piston outlet 23 is connected to the working port B.
  • the pressure fluid supplied via the pressure port P of the camshaft 1 flows in the axial direction through the axial housing inlet P a and the piston inlet 22 into the cavity 21 of the valve piston 20 and from there through the branching piston outlet 23 to that shown in FIG FIG.
  • the pressure chambers associated with the working port A 8 are connected via the working port A and a formed on the outer periphery of the valve piston 20 recess 26 with the reservoir port T A and on this and a with the camshaft 1 rotating feedback 4 ' connected to the reservoir and thus relieved in pressure.
  • the recess 26 extends over the entire outer circumference of the valve piston 20. From the recess 26 seen in the axial direction behind the piston outlet 23 is on the outside Circumference of the valve piston 20 is formed a further axially extending recess, which also extends over the entire outer circumference of the valve piston 20.
  • the recess 27 is connected to the reservoir port T B in the first piston position.
  • the reservoir port T B is assigned to the working port B. However, in the first piston position it is fluidically separated from the working port B by means of a sealing web of the valve piston 20 formed between the piston outlet 23 and the recess 27.
  • the actuator 15 pushes the valve piston 20 from the illustrated first piston position axially in the direction of the housing inlet P A and with correspondingly large actuating force to an axial second piston position, in which no longer the working port B, but the other working port A is connected to the piston outlet 23.
  • a sealing web of the valve piston 20 formed between the piston outlet 23 and the recess 26 separates the working port A from the associated reservoir port T A , so that the pressure chambers 9 are acted upon by the pressure fluid in the second piston position.
  • the recess 27 connects the working port B to the reservoir port T B , so that the fluid can flow out of the pressure chambers 8 and these are relieved of pressure.
  • the rotor 7 moves accordingly in the illustration of FIG. 2 counterclockwise relative to the impeller 5 and thus to the stator 3.
  • the rotatably connected to the rotor 7 camshaft 1 is adjusted in its phase position relative to the crankshaft by the same rotational angle.
  • the high-pressure side fluid flowing into the control valve through the housing inlet P a urges the valve piston 20 with a first axial force acting in the direction of the actuator 15.
  • a first axial force of the valve piston 20 in the direction of the actuator 15 can be flowed through, so that at its the actuator 15 facing rear between this back and the end closure wall 11, a fluid pressure builds up on the back of the valve piston 20, a counterforce, a second Exerts axial force. Since the projected by the pressurized fluid projection surface is reduced by the cross-sectional area with which the coupling member 25 protrudes through the end closure wall 11, the axial counterforce, the second axial force corresponding to the cross-sectional area of the coupling member 25 would be less than the first axial force.
  • the valve piston 20 has a radially expanded piston portion 28, in the following widening 28, and the valve housing 10 has a suitably widened housing portion 18, which surrounds the widening 28 in a tight fit.
  • the valve piston 20 at its outer periphery with the exception of the expansion 28, for example everywhere the same cylindrical cross-section.
  • the valve piston 20 seen from the housing inlet 22 has axially behind the piston outlet 23 a feed 24 which is formed by a plurality of passage channels distributed around the central axis R in a valve piston bottom.
  • the widening 28 and corresponding to the housing section 18 are dimensioned such that the enlargement of the projection surface F 28 facing the actuator 15 due to the widening 28 compensates for at least a predominant part of the cross-sectional area F 25 of the coupling element 25 "lost" for the compensation.
  • the compensation surface is an outer ring surface of the projection surface F 28 .
  • the projection surfaces which each generate an axial force when the valve piston 20 flows through are of the same size in both axial directions.
  • the expansion 28 is preferably formed on the actuator 15 facing the front end of the valve piston 20.
  • the widened housing portion 18 has a sufficient axial extent to allow the adjustment movements of the valve piston 20.
  • the widening 28 forms the end of the recess 27 facing the actuator 15.
  • the widened housing section 18 tapers at 13 onto the narrower cross section, which is constant in the further axial course.
  • the taper 13 is formed within the recess 27, axially by way of example in the region of the reservoir port T B.
  • a locking element 30 locks the rotor 7 relative to the stator 3 in a certain rotational angular position.
  • the locking element 30 is biased in the locking position by means of a spring member. In the other direction, the fluid pressure acts, so that it is moved with increasing pressure of the fluid from the locking position.
  • FIG. 5 also shows a camshaft phaser of a second embodiment in a longitudinal section containing the axis of rotation R of the camshaft 1.
  • the valve housing 10 is not designed as a clamping screw for the phaser and not connected to the camshaft 1 by means of screw.
  • the valve housing 10 is designed as a housing cartridge which is inserted through the open end face of the camshaft 1 in its central receiving space 1a to a stop and sits in the inserted state in radially close fit in the hollow camshaft 1.
  • the valve housing 10 is axially secured by means of a securing element 31, for example a securing ring, relative to the camshaft 1.
  • the receiving space la extends in contrast to the first embodiment within the camshaft 1 axially continuing.
  • the receiving space 1a is separated from the continuing cavity by means of a partition element 1b inserted into the camshaft 1, in particular fluidically, to guide it through the pressure port P of the camshaft 1 into the receiving space 1a and from there through the likewise axial housing inlet P a into the valve piston 20 ,
  • a reservoir port T B as the other working ports A, B and T A is formed as a short radial passage in the shell of the valve housing 10.
  • the valve piston 20 as such is modified relative to the valve piston 20 of the first embodiment only with respect to the compensation of the axial force supply 24, which is not substantially axially as in the first embodiment extends in the direction of the end closure wall 11, but from the piston cavity 21 runs obliquely outwards.
  • phaser of the second embodiment corresponds to the phaser of the first embodiment.
  • FIG. 6 is a camshaft phaser of a third embodiment shown again in a longitudinal axis of rotation R of the camshaft 1 containing.
  • FIG. 7 shows from this phaser in the cross section AA only the central control valve with the valve housing 10 and the valve piston 20.
  • the valve piston 20 corresponds with one exception to the valve piston 20 of the first embodiment.
  • the piston outlet 23 is not formed by simple holes, but by circumferentially slit-like passages.
  • the terminals A to T B are short radial as in the second embodiment Passages, for example, again distributed over the circumference arranged through holes in the valve housing 20th
  • the fluid is not discharged through the actuator 15 close reservoir port T B in the phaser housing 2a and then back into the machine housing 2 or otherwise in a reservoir for the fluid, but via a feedback, which is located within the phaser extends to the low pressure side in the engine housing.
  • the return comprises a return 7a, which is extended by the rotor 7 and has a plurality of return ducts distributed around the central axis R, in each case a return duct 7a for one of the passages which together form the reservoir connection T B.
  • the return channels are exemplified as preferred in each case as an axially straight passage in the rotor 7 is formed.
  • the return 7a leads to a subsequent return 4a, which is radially inwardly of the camshaft 1 and the outside of the stator 3, here the drive wheel 4, limited.
  • the near the housing inlet P a further reservoir port T A leads back to the low pressure side in the machine housing 2 as in the first embodiment on a short path.
  • valve housing 20 The sealing of the return 7a at the front end by the valve housing 20.
  • the valve housing 20 is connected as in the first embodiment by means of screw with the camshaft 1 is advantageous in terms of the simplest possible design of the phaser.
  • the screw head 19 serves in the third embodiment, in an additional function as a seal for the return 7a, whereby their course can be simplified, for example, a simply straight passage through the rotor 7.
  • Simple is also the connection from the reservoir port T B with the return 7a , namely in the form of radial grooves at the front end of the rotor. 7
  • FIG. 8 also shows a camshaft phaser of a fourth embodiment in a longitudinal section containing the axis of rotation R of the camshaft 1. Unlike the other embodiments, the fluid of the high pressure side does not simply flow axially into the control valve but via a radial pressure port P r .
  • the valve housing 10 is closed at its axially inner end face.
  • the terminals A to T B are formed as in the second embodiment.
  • the comments on the first embodiment also apply to the fourth embodiment.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP11156630.3A 2010-03-09 2011-03-02 Régulateur de phases d'arbres à cames doté d'une soupape de commande pour le réglage hydraulique de la position de phase d'un arbre à cames Not-in-force EP2365193B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010002713A DE102010002713B4 (de) 2010-03-09 2010-03-09 Nockenwellen-Phasensteller mit Steuerventil für die hydraulische Verstellung der Phasenlage einer Nockenwelle

Publications (2)

Publication Number Publication Date
EP2365193A1 true EP2365193A1 (fr) 2011-09-14
EP2365193B1 EP2365193B1 (fr) 2013-05-22

Family

ID=44012468

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11156630.3A Not-in-force EP2365193B1 (fr) 2010-03-09 2011-03-02 Régulateur de phases d'arbres à cames doté d'une soupape de commande pour le réglage hydraulique de la position de phase d'un arbre à cames

Country Status (4)

Country Link
US (3) US9021997B2 (fr)
EP (1) EP2365193B1 (fr)
CN (1) CN102191963B (fr)
DE (1) DE102010002713B4 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2550437B1 (fr) * 2010-03-24 2016-04-20 Schaeffler Technologies AG & Co. KG Soupape de commande d'un système permettant l'ajustement du déphasage d'un arbre a cames par rapport au vilebrequin d'un moteur a combustion interne
US10975699B2 (en) 2016-12-12 2021-04-13 Schwäbische Hüttenwerke Automotive GmbH Hydraulic device comprising a sealing element

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010064504B3 (de) 2010-03-18 2022-10-20 Volkswagen Ag Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102010053685B4 (de) * 2010-12-08 2014-10-30 Schwäbische Hüttenwerke Automotive GmbH Vorrichtung zur Verstellung der Drehwinkelposition einer Nockenwelle
DE102011076652B4 (de) 2011-05-27 2017-06-01 Schwäbische Hüttenwerke Automotive GmbH Vorrichtung zur Verstellung der relativen Drehwinkelposition geschachtelter Nockenwellen
DE102011084059B4 (de) 2011-10-05 2016-12-08 Schwäbische Hüttenwerke Automotive GmbH Steuerventil mit integriertem Filter und Nockenwellen-Phasensteller mit dem Steuerventil
DE102011085693A1 (de) * 2011-11-03 2013-05-08 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012208809B4 (de) * 2012-05-25 2020-11-26 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012213002A1 (de) 2012-07-24 2014-01-30 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit Dichtungshülse
CN102926831A (zh) * 2012-10-30 2013-02-13 芜湖杰锋汽车动力系统有限公司 一种配气调节装置
DE102012111033A1 (de) * 2012-11-16 2014-05-22 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einem elektromagnetisch betätigten Hydraulikventil
DE102013104575B4 (de) * 2013-05-03 2018-03-08 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
DE102013209930B4 (de) * 2013-05-28 2016-01-28 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleinrichtung
DE102013212942C5 (de) * 2013-07-03 2021-04-22 Schaeffler Technologies AG & Co. KG Fluidversorgung, etwa eine Ölversorgung, für ein Zentralventilsystem für einen trockenen Riementrieb
CN103953408B (zh) * 2014-04-30 2016-08-17 桂林电子科技大学 无极可变配气定时机构
DE102014115903B4 (de) * 2014-10-31 2020-07-30 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
WO2018019633A1 (fr) 2016-07-27 2018-02-01 ECO Holding 1 GmbH Piston pour unité hydraulique d'un dispositif de réglage à pivotement et dispositif de réglage à pivotement pour un arbre à cames
DE102016214914A1 (de) 2016-08-10 2018-02-15 Schwäbische Hüttenwerke Automotive GmbH Partikelabscheidesystem
EP3665367A1 (fr) * 2017-08-07 2020-06-17 HELLA GmbH & Co. KGaA Appareil de réglage de synchronisation d'arbre à cames avec pompe intégrée
DE102017122425A1 (de) * 2017-09-27 2019-03-28 ECO Holding 1 GmbH Bausatz mit einem Nockenwellenversteller
US10598089B1 (en) * 2018-11-07 2020-03-24 Hts Llc Opposed piston engine with parallel combustion chambers
US20230008355A1 (en) * 2021-07-09 2023-01-12 Borgwarner Inc. Variable cam timing phaser and system including the same

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19654926C2 (de) 1996-03-22 1999-10-14 Daimler Chrysler Ag Vorrichtung zur relativen Winkelverstellung einer Nockenwelle
DE19848706A1 (de) 1998-10-22 2000-04-27 Schaeffler Waelzlager Ohg Vorrichtung zur Relativverdrehung einer Nockenwelle gegenüber einer diese Nockenwelle antreibenden Kurbelwelle einer Brennkraftmaschine
DE19955507C2 (de) 1999-11-18 2003-04-24 Daimler Chrysler Ag Nockenwellensteller für Brennkraftmaschinen
DE10322394A1 (de) 2003-05-12 2004-12-02 Hydraulik-Ring Gmbh Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen
DE10346443A1 (de) 2003-10-07 2005-05-04 Daimler Chrysler Ag Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine
WO2005113943A1 (fr) * 2004-05-22 2005-12-01 Schaeffler Kg Dispositif de reglage d'arbre a cames
DE102006031517A1 (de) * 2006-07-07 2008-01-10 Schaeffler Kg Schalteinrichtung für eine druckölbetätigte Nockenwellenstellvorrichtung, sowie Montageverfahren zum Einbau derselben in eine Brennkraftmaschine
WO2009010332A1 (fr) * 2007-07-18 2009-01-22 Schaeffler Kg Élément d'une soupape de commande hydraulique

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2958151B2 (ja) * 1991-04-30 1999-10-06 株式会社ユニシアジェックス 内燃機関のバルブタイミング制御装置
US7556000B2 (en) * 2002-05-21 2009-07-07 Delphi Technologies, Inc. Camshaft phaser having designated contact vane
JP2005016377A (ja) 2003-06-25 2005-01-20 Honda Motor Co Ltd 船外機
EP1596040B1 (fr) * 2004-05-14 2010-10-13 Schaeffler KG Déphaseur d'arbre à cames
JP2007032689A (ja) 2005-07-26 2007-02-08 Denso Corp スプール弁装置
DE102005052481A1 (de) * 2005-11-03 2007-05-24 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102006022402A1 (de) * 2006-05-13 2007-12-06 Schaeffler Kg Steuerventil für einen Nockenwellenversteller
DE112007002915B4 (de) * 2006-12-04 2020-10-29 Daimler Ag Verstelleinrichtung zur Phaseneinstellung einer Nockenwelle
DE102008023583A1 (de) * 2008-05-14 2009-11-19 Daimler Ag Steuerventileinheit

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19654926C2 (de) 1996-03-22 1999-10-14 Daimler Chrysler Ag Vorrichtung zur relativen Winkelverstellung einer Nockenwelle
DE19848706A1 (de) 1998-10-22 2000-04-27 Schaeffler Waelzlager Ohg Vorrichtung zur Relativverdrehung einer Nockenwelle gegenüber einer diese Nockenwelle antreibenden Kurbelwelle einer Brennkraftmaschine
DE19955507C2 (de) 1999-11-18 2003-04-24 Daimler Chrysler Ag Nockenwellensteller für Brennkraftmaschinen
DE10322394A1 (de) 2003-05-12 2004-12-02 Hydraulik-Ring Gmbh Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen
DE10346443A1 (de) 2003-10-07 2005-05-04 Daimler Chrysler Ag Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine
WO2005113943A1 (fr) * 2004-05-22 2005-12-01 Schaeffler Kg Dispositif de reglage d'arbre a cames
DE102006031517A1 (de) * 2006-07-07 2008-01-10 Schaeffler Kg Schalteinrichtung für eine druckölbetätigte Nockenwellenstellvorrichtung, sowie Montageverfahren zum Einbau derselben in eine Brennkraftmaschine
WO2009010332A1 (fr) * 2007-07-18 2009-01-22 Schaeffler Kg Élément d'une soupape de commande hydraulique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2550437B1 (fr) * 2010-03-24 2016-04-20 Schaeffler Technologies AG & Co. KG Soupape de commande d'un système permettant l'ajustement du déphasage d'un arbre a cames par rapport au vilebrequin d'un moteur a combustion interne
US10975699B2 (en) 2016-12-12 2021-04-13 Schwäbische Hüttenwerke Automotive GmbH Hydraulic device comprising a sealing element

Also Published As

Publication number Publication date
EP2365193B1 (fr) 2013-05-22
CN102191963A (zh) 2011-09-21
CN102191963B (zh) 2014-06-11
US20110220046A1 (en) 2011-09-15
US9021997B2 (en) 2015-05-05
DE102010002713B4 (de) 2013-12-05
US20150233269A1 (en) 2015-08-20
DE102010002713A1 (de) 2011-09-15
US20160194985A1 (en) 2016-07-07
US9970333B2 (en) 2018-05-15
US10072538B2 (en) 2018-09-11

Similar Documents

Publication Publication Date Title
EP2365193B1 (fr) Régulateur de phases d'arbres à cames doté d'une soupape de commande pour le réglage hydraulique de la position de phase d'un arbre à cames
DE102010053685B4 (de) Vorrichtung zur Verstellung der Drehwinkelposition einer Nockenwelle
DE112011103133B4 (de) Nockendrehmomentbetätigter-torsionsunterstützter Versteller
EP2690261B1 (fr) Régulateur de phase d'arbre à cames avec douille d'étanchéité
EP2527607B1 (fr) Dispositif de réglage de la position relative de l'angle de rotation d'un arbre à came imbriqué
DE102010019004B4 (de) Schwenkmotorversteller mit einem Hydraulikventil
DE102005052481A1 (de) Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
EP2267282B1 (fr) Régulateur de phase d'arbres à came doté d'un couvercle de boîtier multifonctionnel
EP2492459B1 (fr) Régulateur de phase d'arbres doté d'un dispositif de verrouillage amélioré
DE102008029692B4 (de) Gebaute Nockenwelle mit einem Flügelzellenversteller und Herstellungsverfahren
DE102004036096A1 (de) Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE10346448A1 (de) Nockenwellenversteller für eine Brennkraftmaschine
DE102011077587A1 (de) Nockenwellenversteller
DE19860025A1 (de) Ventilsteuerzeitenregelvorrichtung
DE102012210178B4 (de) Steuerventil eines Nockenwellenverstellers
DE102006033425A1 (de) Gruppe mehrerer Nockenwellen mit Nockenwellenverstellern
EP2118455B1 (fr) Dispositif combiné de verrouillage et de limitation d'angle de rotation d'un variateur d'arbre à cames
DE112020001476T5 (de) Ventil-Timing-Einstellvorrichtung
DE102012213176A1 (de) Hydraulischer Nockenwellenversteller
DE102012201573A1 (de) Nockenwellenversteller
DE102009016186A1 (de) Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102010032133A1 (de) Zentralventil
DE102009056021A1 (de) Vorrichtung zur varibalen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102010005603A1 (de) Nockenwellenverstellanordnung
DE102009022868B4 (de) Flügelzellennockenwellenversteller

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20111117

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 613357

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130615

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011000756

Country of ref document: DE

Effective date: 20130718

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130823

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130923

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130902

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130822

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130822

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20140225

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011000756

Country of ref document: DE

Effective date: 20140225

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E019571

Country of ref document: HU

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140302

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140331

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140331

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140302

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 613357

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160302

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160302

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130522

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20210323

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20210324

Year of fee payment: 11

Ref country code: DE

Payment date: 20210319

Year of fee payment: 11

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: HU

Payment date: 20210420

Year of fee payment: 11

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011000756

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20220302

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220303

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220302

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220331

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221001