EP1945917B1 - Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne - Google Patents

Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne Download PDF

Info

Publication number
EP1945917B1
EP1945917B1 EP20060807333 EP06807333A EP1945917B1 EP 1945917 B1 EP1945917 B1 EP 1945917B1 EP 20060807333 EP20060807333 EP 20060807333 EP 06807333 A EP06807333 A EP 06807333A EP 1945917 B1 EP1945917 B1 EP 1945917B1
Authority
EP
European Patent Office
Prior art keywords
pressure medium
guide insert
control valve
valve
medium guide
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.)
Active
Application number
EP20060807333
Other languages
German (de)
English (en)
Other versions
EP1945917A1 (fr
Inventor
Jens Hoppe
Ali Bayrakdar
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=37744633&utm_source=***_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1945917(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of EP1945917A1 publication Critical patent/EP1945917A1/fr
Application granted granted Critical
Publication of EP1945917B1 publication Critical patent/EP1945917B1/fr
Active 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
    • 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
    • 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
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/04—Special measures taken in connection with the properties of the fluid
    • F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
    • 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
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/3444—Oil filters
    • 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
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86759—Reciprocating
    • Y10T137/86767—Spool

Definitions

  • the invention relates to a control valve for a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine with a hollow valve housing having at least one inlet port, at least one drain port and at least two working ports, and with a control piston (see eg EP-A-1477636 ).
  • camshafts are used to actuate the gas exchange valves.
  • Camshafts are mounted in the internal combustion engine such that cams attached to them abut cam followers, for example cup tappets, drag levers or rocker arms. If a camshaft is rotated, the cams roll on the cam followers, which in turn actuate the gas exchange valves. Due to the position and the shape of the cams thus both the opening duration and the opening amplitude but also the opening and closing times of the gas exchange valves are set.
  • valve lift and valve opening duration should be variable, up to the complete shutdown of individual cylinders.
  • concepts such as switchable cam followers or electrohydraulic or electric valve actuations are provided.
  • it has been found to be advantageous to be able to influence the opening and closing times of the gas exchange valves during operation of the internal combustion engine. It is in particular it is desirable to be able to influence the opening and closing points of the intake or exhaust valves separately in order to set a defined valve overlap, for example.
  • the specific fuel consumption can be reduced, the exhaust behavior positively influenced, increases the motor efficiency, the maximum torque and the maximum power become.
  • the described variability of the gas exchange valve control times is achieved by changing the relative phase position of the camshaft to the crankshaft.
  • the camshaft is connected via a chain, belt, gear drive or equivalent drive concepts in drive connection with the crankshaft.
  • a device for the variable adjustment of the timing of an internal combustion engine hereinafter also called camshaft adjuster, mounted, which transmits the torque from the crankshaft to the camshaft.
  • this device is designed such that during operation of the internal combustion engine, the phase angle between the crankshaft and camshaft securely held and, if desired, the camshaft can be rotated in a certain angular range relative to the crankshaft.
  • each with a camshaft for the intake and the exhaust valves these can each be equipped with a camshaft adjuster.
  • the opening and closing times of the inlet and outlet gas exchange valves can be shifted relative to one another and the valve overlaps can be adjusted in a targeted manner.
  • the seat of modern camshaft adjuster is usually located at the drive end of the camshaft.
  • the camshaft adjuster can also be arranged on an intermediate shaft, a non-rotating component or the crankshaft. This consists of a driven by the crankshaft, a fixed phase relationship to this holding drive wheel, a drive element in driving connection with the camshaft output element and a torque transmitting from the drive wheel to the output element actuating device.
  • the drive wheel may be designed as a chain, belt or gear in the case of a not arranged on the crankshaft camshaft adjuster and is driven by means of a chain, a belt or a gear drive from the crankshaft.
  • the actuating mechanism can be operated electrically, hydraulically or pneumatically.
  • hydraulically adjustable camshaft adjusters Two preferred embodiments of hydraulically adjustable camshaft adjusters are the so-called Axialkolbenversteller and Rotationskolbenversteller.
  • the drive wheel is connected to a piston and this with the output element via helical gears in combination.
  • the piston separates a cavity formed by the output element and the drive wheel in two axially arranged pressure chambers. If one pressure chamber is acted upon by pressure medium while the other pressure chamber is connected to a tank, then the piston shifts in the axial direction. The axial displacement of the piston is translated by the helical gears in a relative rotation of the drive wheel to the output element and thus the camshaft to the crankshaft.
  • a second embodiment of hydraulic phaser are the so-called Rotationskolbenversteller.
  • the drive wheel is rotatably connected to a stator.
  • the stator and a rotor or driven element are arranged concentrically to one another, wherein the rotor is non-positively, positively or materially connected, for example by means of a press fit, a screw or welded connection with a camshaft, an extension of the camshaft or an intermediate shaft.
  • a plurality of circumferentially spaced cavities are formed which extend radially outward from the rotor.
  • the cavities are limited pressure-tight in the axial direction by side cover. In each of these cavities extends Wing connected to the rotor, which divides the respective cavity into two pressure chambers.
  • camshaft adjuster sensors detect the characteristics of the engine such as the load condition and the speed. These data are supplied to an electronic control unit, which controls the supply and the outflow of pressure medium to the various pressure chambers after comparing the data with a characteristic field of the internal combustion engine.
  • one of the two counteracting pressure chambers of one cavity is connected in hydraulic camshaft adjusters with a pressure medium pump and the other with the tank.
  • the inlet of pressure medium to a chamber in conjunction with the flow of pressure medium from the other chamber moves the pressure chambers separating piston in the axial direction, whereby in Axialkolbenverstellern on the helical gears, the camshaft is rotated relative to the crankshaft.
  • Rotationskolbenverstellern is caused by the pressurization of a chamber and the pressure relief of the other chamber, a displacement of the wing and thus directly a rotation of the camshaft to the crankshaft.
  • both pressure chambers are either connected to the pressure medium pump or separated from both the pressure medium pump and the tank.
  • control valves usually by means of a 4/3-way proportional valve.
  • This has a valve housing, which is each provided with a connection for the pressure chambers (working port) and at least two supply ports. At least one of the supply connections serves as an inflow connection, via which the control valve is supplied with pressure medium from a pressure medium pump. Furthermore, a further supply connection serves as a discharge connection, via which the pressure medium emerging from the pressure chambers is dissipated. It can be provided, for example, that the drain port communicates with a tank.
  • an axially displaceable control piston is arranged within the substantially hollow cylindrical valve housing.
  • the control piston can be brought axially into any position between two defined end positions by means of an electromagnetic, pneumatic or hydraulic actuator, against the spring force of a spring element.
  • the control piston is further provided with control portions having control edges, and annular grooves, whereby the terminals can be interconnected or locked against each other.
  • Such a control valve is out of DE 199 44 535 C1 known.
  • This consists of a substantially hollow cylindrical valve housing and an axially displaceably arranged therein control piston.
  • On the valve housing two radial working ports, a radial inlet port and an axial outlet port are formed.
  • the two working ports and the inlet port are formed as axially spaced openings in the cylindrical surface of the valve housing.
  • the inlet connection lies in the axial direction between the two working connections.
  • a control piston is provided, which can be moved by means of an electromagnetic actuator in the axial direction relative to the valve housing.
  • an annular groove is formed, via which, depending on the position of the control piston to the valve housing, selectively either the first or the second working port can be connected to the inlet port.
  • the drain connection can, depending on the relative position of the control piston within the valve housing via further annular grooves and an axial Hole within the control piston to be connected to either the first or the second working port.
  • the control valve is designed as a central valve, ie, the control valve is arranged radially within the output element of the camshaft adjuster.
  • valve housing is integrally formed with a central screw, by means of which the output element of the camshaft adjuster is rotationally connected to a camshaft.
  • the position of the inlet connection between the working connections requires a complex design of a supply line for the supply of pressure medium to the inlet connection of the control valve.
  • This is realized by means of a plurality formed in the valve housing, in each other opening holes, which communicate with a bore in the screw shaft of the central screw, which in turn opens into the hollow camshaft.
  • the interior of the camshaft is acted upon by a pressure medium pump via a camshaft bearing with pressure medium.
  • the formation of these holes in the wall of the valve housing is very expensive and error-prone.
  • the US-A-6799544 shows a camshaft adjuster, with which an oscillating torque is used by an opening and closing the engine valve to adjust the camshaft displacement.
  • Valve means communicate with one in a feed channel and a discharge channel and are actuated via a solenoid.
  • the phaser is designed as a self-contained unit that is independent of engine oil pressure.
  • the EP-A-1452786 discloses a valve, preferably a proportional solenoid valve, having a solenoid member to which a piston of a valve member is operable having a housing having ports for a pressure medium, at least one of the port bores being in a groove extending along the valve.
  • the US-A-5377720 shows a hydraulic valve with a valve body having an inlet, a control channel and a drain.
  • a valve piston is arranged displaceably.
  • a sleeve-shaped insert is provided, via which the control piston can slide.
  • the sleeve-shaped insert and the control piston define a flashback space with which the force on the control piston, as applied by a solenoid, is balanced.
  • the DE-A-1 0346446 discloses a cam phaser.
  • the invention is therefore based on the object to avoid these disadvantages and thus to provide a hydraulic control valve, can be realized in the significant different overhead pressure fluid logics between the different ports without significant additional effort.
  • a maximum of freedom in the design of the pressure fluid logics of the control valve should be achieved without increasing the space requirements, dien manufacturing costs or production costs appreciably.
  • this object is achieved in that disposed within the valve housing a hollow Druckschleitrise and at least one substantially extending in the axial direction pressure medium channel is formed, wherein the pressure medium channel is at least partially surrounded by the Druckstoffleitrise, wherein the pressure medium channel with at least one of the terminals and over a radial opening communicates with the interior of the pressure medium insert and wherein the control piston is arranged within the Druckstoffleitconses.
  • the outer dimensions of the Druckstoffleit tenuouslyes are adapted to the inner dimensions of the valve housing and that the pressure medium channel is formed at the interface between the valve housing and the Druckstoffleitinate.
  • the device is fastened by means of a central screw to a camshaft and the valve housing is formed integrally with the central screw.
  • the at least one pressure medium channel is formed as a recess on an inner circumferential surface of the valve housing, wherein an outer circumferential surface of the Druckmitmititmonyes the pressure medium channel bounded radially inwardly and the interior of the Druckstoffleitmilaes communicates via a formed at this radial opening with the pressure medium channel.
  • the at least one pressure medium channel is formed as a recess on an outer circumferential surface of the Druckstoffleit tenues, wherein an inner circumferential surface of the valve housing the pressure medium channel radially outwardly limited and the pressure medium channel over a radial opening formed on the pressure fluid insert communicates with its interior.
  • the Druckmitffenleitrise comprises at least an inner and an outer sleeve-shaped member and that the at least one pressure medium channel is formed as a slot in a wall of the outer sleeve-shaped component of Druckstoffleitmbies, wherein an inner lateral surface of the valve housing the pressure medium channel radially outward and the inner sleeve-shaped component of Druckstoffleit conses the pressure medium channel bounded radially inwardly and the pressure medium channel communicates via a formed on the inner sleeve-shaped member radial opening with the interior of the Druckstoffleitmilaes.
  • the outer sleeve-shaped component as an injection molded part and to form the inner sleeve-shaped component as an insert component, which is encapsulated by the latter during the injection molding process of the outer sleeve-shaped component.
  • the pressure medium channel connects the inlet connection with the interior of the Druckstoffleitrum.
  • a check valve and / or a filter element can be arranged upstream of the pressure medium channel within the control valve.
  • the filter element and / or parts of the check valve are integrally connected to the Druckstoffleitrum.
  • the check valve has a closing element acted upon by a spring element with a force, the spring element being supported on a spring bearing formed integrally with the pressure medium guide insert.
  • the non-return valve has a closure element acted upon by a spring element with a force, a spring bearing and a valve seat, wherein at least the spring bearing or the valve seat is designed as a component separate from the pressure medium insert.
  • a piston pressure spring element can be provided, which acts on the control piston in an axial direction with a force, which is supported on a piston spring bearing formed integrally with the Druckmitmitelleitmony or on a separately formed for Druckstoffstoffleitbib piston spring bearing.
  • the control valve according to the invention is characterized in that the control piston is not applied directly to an inner circumferential surface of the valve housing, but that a Druckstoffleitrus is disposed between these components.
  • the valve housing continues to serve in this embodiment as a connection element of the control valve to the surrounding structures. It establishes the connection to the, for example, in an output element of a camshaft adjuster trained pressure medium lines that lead to the hydraulic consumers (pressure chambers).
  • the connection to at least one supply line, such as a supply or a drain line, manufactured, which may be formed for example in a camshaft or a connection component.
  • the pressure medium line insert exercises the function of connecting its interior to at least one of the connections via at least one essentially axially extending pressure medium channel. Furthermore, the pressure medium insert together with the control piston fulfills the control function of the pressure medium flows within the valve.
  • the control piston is arranged axially displaceable within the Druckstoffleitinate, wherein on the control piston control sections are formed whose outer dimensions are adapted to the inner dimensions of the Druckstoffleitinate.
  • the pressure medium supply line can be considerably simplified by the control valve according to the invention.
  • the pressure medium guide insert assumes the task of supplying the pressure medium supplied to the inlet connection at one point to the effective region of the control collar, which lies axially between the two working connections.
  • the line of the pressure medium can be made via easy-to-manufacture structures of Druckstoffleitvones. These pressure medium channels can be formed, for example, at the interface between the Druckstoffleitnou and the valve housing.
  • depressions or axial grooves on the Druckstoffleitrus or the valve housing are provided which communicate on the one hand with one of the terminals and on the other hand via suitable radial openings with the interior of the Druckstoffleitinate.
  • the depressions formed on the pressure medium insert can be introduced into these at no cost during the production process of the Druckstoffleitinate. This can be achieved, for example, in a plastic version of the pressure fluid insert that the pressure fluid channels are already taken into account in the injection mold.
  • pressure medium conductor inserts consisting of steel or another metal, for example aluminum. Conceivable in this context would be a machining or a production in a suitable metal injection molding process.
  • the formation of the pressure medium insert from a steel sheet by means of a non-cutting forming process, such as a deep drawing process, in which case the pressure medium channels can in turn be formed cost neutral during the forming process.
  • inlet connection communicates via the pressure medium channels with the interior of the Druckstoffleitmbies
  • other oil logics can be realized, such as a connection of the interior of the Druckstoffleit conses with the drain port or one or more of the working ports. It is important in this context only that it is ensured that the pressure medium channels communicate exclusively with the provided terminals, wherein the pressure medium at the other terminals, which lie in the axial region of the pressure medium channels, is passed without being a direct connection to these.
  • an inner and an outer component could be provided, wherein the inner component is disposed within the outer member.
  • the pressure medium channels are formed in the outer component, while the inner component delimits them from the interior of the Druckstoffleit tenues and carries the radial opening for introducing the pressure medium into the interior of Druckstoffleitmbies.
  • the inner component can be made, for example, a non-cutting steel sleeve and the outer component made of plastic by means of an injection molding process.
  • the steel sleeve acts as an insert, which is overmolded during the manufacturing process of the outer component with this.
  • other material combinations and positive, positive or cohesive connections or adhesive bonds are also conceivable are other material combinations and positive, positive or cohesive connections or adhesive bonds.
  • control valve filter elements or check valves may be arranged. These may be formed separately from the components of the control valve and materially connected to one or more components, or designed as an insert. Likewise conceivable are embodiments in which at least parts of the check valve or the filter element are formed integrally with components of the control valve. For example, it may be provided in the case of a Druckstoffleitiqueses or an inner component made of sheet steel to perform a spring bearing of the check valve integral with the respective component, whereby a further cost reduction can be achieved.
  • FIG. 1 an internal combustion engine 100 is outlined, wherein a seated on a crankshaft 101 piston 102 is indicated in a cylinder 103.
  • the crankshaft 101 is in the illustrated embodiment via a respective traction drive 104 and 105 with an intake camshaft 106 and exhaust camshaft 107 in conjunction, with a first and a second device 1 for relative rotation between the crankshaft 101 and cam shafts 106, 107 can provide.
  • Cams 108, 109 of the camshafts 106, 107 actuate an inlet gas exchange valve 110 and an outlet gas exchange valve 111. Equally, it may be provided to equip only one of the camshafts 106, 107 with a device 1, or to provide only one camshaft 106, 107, which is provided with a device 1 is provided.
  • FIGS. 2a, 2b show a first embodiment of a device 1 for the variable adjustment of the timing of gas exchange valves 110, 111 of an internal combustion engine 100th
  • An adjusting device 1 a consists essentially of a drive wheel 5, a stator 2 and a driven element arranged concentrically therewith.
  • the driven element 3 consists of a wheel hub 4, on whose outer circumference five wings 6 are formed, which extend radially outwards.
  • the actuator 1 a is provided with a central bore 4b, in the assembled state of the device 1, a camshaft 3a, in the illustration of FIG. 2a , from the left, intervenes.
  • the device 1 In the assembled state of the device 1, this can, for example by means of a force, friction, form, or cohesive connection or by means of fastening means, rotatably connected to the camshaft 3a.
  • the device 1 is rotatably connected by means of a central screw 17 with the camshaft 3a.
  • the stator 2 is formed as a thin-walled sheet metal part, which consists of inner peripheral walls 7 and outer peripheral walls 8, which are connected to one another via side walls 9.
  • the inner and outer peripheral walls 7, 8 extend substantially in the circumferential direction.
  • the stator 2 is rotatably mounted on the driven element 3.
  • the side walls 9 extend outwardly in a substantially radial direction and merge into the outer circumferential walls 8.
  • a plurality of, in the illustrated embodiment, five, pressure chambers 10 are formed, which are completed in the axial direction of the drive wheel 5 and a sealing washer 12 pressure-tight.
  • the wings 6 are arranged on the outer circumferential surface of the driven element 3 such that exactly one wing 6 extends into each pressure chamber 10.
  • the wings 6 are in the radial direction of the outer peripheral walls 8 of the stator 2 at.
  • the width of the wings 6 is designed such that they rest in the axial direction on the drive wheel 5 and the sealing washer 12. As a result, each wing 6 divides a pressure chamber 10 into two counteracting pressure chambers 14, 15.
  • the stator 2 and the output element 3 are arranged within a cup-shaped housing 11, which encapsulates these components by the interaction with the drive wheel 5 pressure medium tight.
  • the open end of the housing 11 is oil-tightly connected to the drive wheel 5.
  • the connection between the drive wheel 5 and the housing 11 can be realized by means of a sealing joining method or by the use of a sealant.
  • a circumferential circumferential weld joint 16a is provided.
  • a concentric with the central bore 4b arranged opening 16 is provided on a bottom 13 of the housing 11, a concentric with the central bore 4b arranged opening 16 is provided.
  • a central screw 17 passes through the opening 16 and the central bore 4b, wherein a threaded portion of the central screw 17 engages in an internally threaded receptacle 18 of the camshaft 3a.
  • the central screw 17 is further formed on the side facing away from the camshaft of the device 1 with a stepped portion 19 a, via which the central screw 17 in the assembled state via a separately manufactured Anschraubbund 19 either directly or indirectly supported on the output element 3 and thus this rotatably connected to the camshaft 3a.
  • the advantage of a separately manufactured bolted collar 19 is the lower production costs and the lower production costs.
  • the central screw 17, which is simultaneously formed as a valve housing 22 of a control valve 20, is usually produced by a turning process.
  • the collar must be designed with a certain minimum outer diameter.
  • the region of the central screw 17, which is arranged within the output element 3, is designed as a control valve 20. This region of the central screw 17 extends within the central bore 4b, which acts as a valve seat 4a.
  • FIG. 3 the central screw 17 is shown in an enlarged form. This is provided with a blind hole-like receptacle 21, whose opening is arranged on the camshaft remote axial end of the central screw 17.
  • the resulting cylindrical surface of the control valve 20 fulfills the function of a valve housing 22.
  • the outer diameter of the valve housing 22 is adapted to the inner diameter of the driven element 3.
  • the control valve 20 is provided with four ports A, B, P, T, wherein three of the ports A, B, P are formed as radial openings in the cylindrical lateral surface of the valve housing 22.
  • the inlet port P is formed on the valve housing 22 such that it is arranged in the mounted state of the control valve 20 within the receptacle 18 of the camshaft 3a.
  • the receptacle 18 of the camshaft 3a is formed such that between the central screw 17 and an inner circumferential surface of the receptacle 18, an annular channel 24 is formed, which camshaft end side of the central screw 17 is closed.
  • the annular channel 24 communicates on the one hand with the inlet port P and on the other hand via radial bores 25, which are formed in the region of a camshaft bearing 26 on the camshaft 3a, with a pressure medium pump, not shown.
  • the inlet port P and the working ports A, B are arranged axially offset from one another, wherein the inlet port P on the camshaft side facing the working ports A, B is arranged.
  • a substantially hollow cylindrical executed Druckschleitrus 27 is arranged, wherein the outer diameter of the Druckmitffenleit tenuis 27 is adapted to the inner diameter of the valve housing 22.
  • the pressure medium guide insert 27 rests at one end on a shoulder 28 formed on the valve housing 22 and at the other end is positioned axially inside the valve housing 22 by means of a securing ring 29.
  • the camshaft-side axial opening of the Druckmitffenleitmbies 27 is in direct communication with the inlet port P, wherein as in FIG. 3 illustrated, between the inlet port P and the Druckstoffleitrus 27 a filter element 27a (in this case a ring filter element) and / or a check valve 27b may be arranged.
  • the filter element 27a prevents dirt particles entering the control valve 20 with the entering into the control valve 20 pressure fluid, whereby both the control valve 20 and the device 1 are effectively protected against malfunction.
  • the implementation of the check valve 27b improves at various operating points an internal combustion engine 100, the function of the device 1 considerably. The response and the adjustment speed of the device 1 can be increased and an idling of the device 1 during the operating pauses of the internal combustion engine 100 can be avoided.
  • a spring bearing 30 is arranged, which closes the axial bore of the Druckstoffleit tenues 27 pressure-tight in the axial direction and on which a spring element 31 is supported, which acts on a closing body 32 of the check valve 27b with an axial force.
  • first radial openings 33a are provided in the cylindrical lateral surface of the Druckstoffleit tenues.
  • Each of the first radial openings 33a opens into a pressure medium channel 34, which is designed as formed on the outer circumferential surface of the Druckstoffleit tenues 27, extending in the axial direction depression.
  • Each pressure medium channel 34 opens at the side remote from the camshaft 3a side of the spring bearing 30 via a respective second radial opening 33b in the interior of the Druckstoffleit propositiones 27th Furthermore, third and fourth radial openings 33c, 33d are formed on the pressure medium guide insert 27, which communicate with one of the working ports A, B, respectively. It is provided that the third and fourth radial openings 33c, 33d relative to the first radial openings 33a, the second radial openings 33b and the pressure medium channels 34 are arranged offset in the circumferential direction to each other ( FIG. 3a ).
  • the third and fourth radial openings 33c, 33d can communicate with the working ports A, B either directly, or via further pressure medium channels 34 formed on the pressure medium guide insert 27, essentially axially extending. This makes it possible to arrange the working ports A, B offset to the third and fourth radial openings 33c, 33d, with further degrees of freedom in the design of the valve housing 22 are present.
  • a substantially hollow cylindrical control piston 35 is arranged axially displaceable.
  • the control piston 35 is acted upon by an axial force on the camshaft side by means of a piston pressure spring element 36, the piston pressure spring element 36 being supported on a piston spring bearing 30, which is formed integrally with the spring bearing 30, and the control piston 35.
  • an electrical actuating unit 37 is formed, which can move the control piston 35 against the force of the piston compression spring member 36 in the axial direction via a push rod 38.
  • the control piston 35 is designed as a substantially hollow cylindrical component, wherein on the outer circumferential surface of which two control sections 39 of larger outer diameter are formed, which are separated from one another by an annular groove 40. It is provided that the second radial openings 33b open in the region of the annular groove 40 in the interior of the Druckmitffenleit complicates 27.
  • the outer diameter of the control sections 39 is adapted to the inner diameter of the Druckstoffleitunes 27, whereby via the second radial openings 33b in the annular groove 40 pressure fluid, depending on the relative position of the control piston 35 to the Druckstoffleitrus 27, to the third or fourth radial openings 33c, 33d and thus can get to the working ports A, B can.
  • the interior of the control piston 35 communicates camshaft side via an axial opening 41 with the interior of the Druckstoffleit tenues 27 and on the other hand via radial openings 41 with the exterior of the central screw 17th
  • the pressure medium now passes through the third or fourth radial openings 33c, 33d either to the first or the second working port A, B and from there to the respective pressure chambers 14, 15 of the device 1. From the pressure chambers 14,15 Backflowing pressure medium enters via the respective working port A, B and the corresponding radial opening 33c, 33d in the interior of the Druckstoffleitvones 27 a. Via the working port A entering pressure medium is passed through the interior of the control piston 35 and the radial openings 41 to a pressure medium reservoir of the internal combustion engine 100, not shown. Pressure medium entering via the working connection B passes directly on the control section 39, which faces away from the camshaft 3a, to the pressure medium reservoir.
  • the pressure medium guide insert 27 can, as in in FIG. 3 illustrated embodiment in one piece, for example, made of a suitable steel, aluminum or plastic. In this case, it may be provided, for example, to produce the pressure medium guide insert 27 by means of a non-cutting shaping method or by means of an injection molding method.
  • the spring bearing 30 is formed as a separate component, which is subsequently fixed in the bore of the Druckmitmititcons 27. It is conceivable, for example, form the spring bearing 30 as a non-cutting forming part and non-positively or materially connected to the Druckstoffleitrus 27. Alternatively, the spring bearing 30 can be poured into the Druckstoffleitnou 27 during the injection molding process. Also conceivable is a one-piece design of the spring bearing 30 with the pressure medium guide insert 27th Since neither the Druckstoffleitrus 27 nor the valve housing 22 are rotationally symmetrical with respect to a longitudinal axis of the control valve 20, advantageously means for preventing rotation of the two components against each other are provided.
  • the spring-groove connection 43 also serves as an assembly aid, and make sure that the pressure medium guide insert 27 only in one, the correct, orientation can be mounted within the valve housing 22.
  • the check valve 27b or the filter element 27a may be formed separately from the pressure medium guide insert 27 or in one piece therewith. In the case of a separate embodiment, it is proposed to connect the filter element 27a or the check valve 27b to the pressure medium guide insert 27 by means of a cohesive connection, such as ultrasonic welding.
  • FIG. 4 shows a further embodiment according to the invention of a control valve 20, these being identical in many parts to the in FIG. 3 illustrated embodiment.
  • the pressure medium channels 34 are formed as depressions or long grooves on the inner circumferential surface of the valve housing 22 in this embodiment.
  • the radial openings 33a-33d are formed.
  • FIG. 5 a further embodiment according to the invention of a control valve 20 is shown, wherein the Druckstoffleitrus 27 in this case in two parts, in the form of an inner and an outer sleeve-shaped member 44, 45 is formed. Both the inner and the outer sleeve-shaped component 44, 45 have the aligned third radial openings 33c.
  • the fourth radial openings 33d are formed only in the inner sleeve-shaped component 44 and open into the second pressure medium channel 34, which are formed on the outer sleeve-shaped component 45.
  • the first radial openings 33a are exclusively in the outer sleeve-shaped component 45 and the second radial openings 33b are formed exclusively in the inner sleeve-shaped component 44.
  • Both the first and the second radial openings 33b open into the pressure medium channels 34. These are designed in this case as elongated holes 46 which are formed on the lateral surface of the outer sleeve-shaped member 45.
  • the pressure medium channels 34 are bounded radially outwardly by the inner lateral surface of the valve housing 22 and radially inwardly by the inner sleeve-shaped member 44.
  • FIG. 5a shows the pressure medium insert 27 of in FIG. 5 illustrated embodiment of a control valve 20 in an enlarged sectional view, wherein the sectional plane of the in FIG. 5 differs.
  • the spring bearing 30 can in this embodiment both as a separate component, as in FIG. 5 represented, or, as in FIG. 5a may be formed integrally with the inner sleeve-shaped member 44.
  • the one-piece embodiment can be produced for example by means of a chipless forming process from a suitable sheet steel blank.
  • the filter element 27a is formed separately to this, wherein a frame 47 of the filter element 27a is connected by means of a material connection with the Druckmitmitelleitrus 27.
  • the frame 47 of the filter element 27a acts as a valve seat for a closing body 32, not shown.
  • the outer sleeve-shaped component 45 is produced as a plastic injection-molded part, wherein the made of a steel inner sleeve-shaped member 44 during the injection molding process of the outer sleeve-shaped member 45 is encapsulated by this. Also conceivable are various other material combinations, wherein fuel or positive connections between the two sleeve-shaped components 44, 45 come into question.
  • the pressure medium channels 34 connect the drain port T with the interior of the Druckstoffleit Vietnamesees 27, while pressure medium can be passed via an axial inlet port P within the control piston 35 either to the working port A or the working port B.
  • first pressure medium channels 34 may as well as in the FIGS. 3 and 3a represented, the working ports A, B communicate via second pressure medium channels 34 and the third and fourth radial openings 33c, 33d with the interior of the Druckstoffleitmilaes 27.
  • the valve housing 22 can thus be adapted to the surrounding construction and not vice versa.
  • control valve 20 and thus the device 1, which is controlled by the control valve 20 can be increased by the integration of further functionalities in the pressure medium guide insert 27, such as filter elements 27a or check valves 27b.
  • the costs and assembly costs are hardly increased by the integration of additional functions.
  • the pressure medium channels 34 would be formed at an interface between the pressure medium guide insert 27 and the surrounding structure, for example the output element 3, a camshaft 3a, which engages in the output element 3 or a valve receptacle formed on a cylinder head or a cylinder head cover.
  • the control valve 20 communicates with all pressure medium lines 3c of all pressure chambers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Valve Device For Special Equipments (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Claims (19)

  1. Soupape de commande (20) pour un dispositif (1) de réglage variable des temps de commande de soupapes d'échange de gaz (110, 111) d'un moteur à combustion interne (100), comprenant :
    - un boîtier de soupape (22) de configuration creuse,
    - qui présente au moins un raccord d'entrée (P), au moins un raccord de sortie (T) et au moins deux raccords de travail (A, B), et
    - un piston de commande (30),
    - à l'intérieur du boîtier de soupape (22), étant disposé un insert de guidage de fluide sous pression (27) de configuration creuse et étant réalisé au moins un canal de fluide sous pression (34) s'étendant essentiellement dans la direction axiale,
    - le canal de fluide sous pression (34) étant engagé au moins en partie sur sa périphérie par l'insert de guidage de fluide sous pression (27),
    - le canal de fluide sous pression (34) communiquant avec au moins l'un des raccords (A, B, P, T) et par le biais d'une ouverture radiale (33b-d) avec l'intérieur de l'insert de guidage de fluide sous pression (27) et
    - le piston de commande (35) étant disposé à l'intérieur de l'insert de guidage de fluide sous pression (27),
    caractérisée en ce que les dimensions extérieures de l'insert de guidage de fluide sous pression (27), sont adaptées aux dimensions intérieures du boîtier de soupape (22) et en ce que le canal de fluide sous pression (34) est réalisé sur la surface limite entre le boîtier de soupape (22) et l'insert de guidage de fluide sous pression (27), l'insert de guidage de fluide sous pression (27), comprenant au moins un composant interne et externe en forme de douille (44, 45) et en ce que l'au moins un canal de fluide sous pression (34) est réalisé sous forme de trou oblong dans une paroi du composant externe en forme de douille (45) de l'insert de guidage de fluide sous pression (27), une surface d'enveloppe intérieure du boîtier de soupape (22) limitant radialement vers l'extérieur le canal de fluide sous pression (34) et le composant interne en forme de douille (44) de l'insert de guidage de fluide sous pression (27) limitant radialement vers l'intérieur le canal de fluide sous pression (34), et le canal de fluide sous pression (34) communiquant par le biais d'une ouverture radiale (33b-d) réalisée sur le composant interne en forme de douille (44) avec l'intérieur de l'insert de guidage de fluide sous pression (27).
  2. Soupape de commande (20) selon la revendication 1, caractérisée en ce que le dispositif (1) est fixé au moyen d'une vis centrale (17) à un arbre à came (3a) et le boîtier de soupape (22) est réalisé d'une seule pièce avec la vis centrale (17).
  3. Soupape de commande (20) selon la revendication 1, caractérisée en ce que l'au moins un canal de fluide sous pression (34) est réalisé sous forme de renfoncement sur une surface d'enveloppe interne du boîtier de soupape (22), une surface d'enveloppe externe de l'insert de guidage de fluide sous pression (27) limitant radialement vers l'intérieur le canal de fluide sous pression (34) et l'intérieur de l'insert de guidage de fluide sous pression (27) communiquant par le biais d'une ouverture radiale (33b-d) réalisée sur celui-ci avec le canal de fluide sous pression (34).
  4. Soupape de commande (20) selon la revendication 1, caractérisée en ce que l'au moins un canal de fluide sous pression (34) est réalisé sous forme de renfoncement sur une surface d'enveloppe extérieure de l'insert de guidage de fluide sous pression (27), une surface d'enveloppe interne du boîtier de soupape (22) limitant radialement vers l'extérieur le canal de fluide sous pression (34) et le canal de fluide sous pression (34) communiquant par le biais d'une ouverture radiale (3b-d) réalisée sur l'insert de guidage de fluide sous pression (27) avec l'intérieur de celui-ci.
  5. Soupape de commande (20) selon la revendication 1, caractérisée en ce que l'insert de guidage de fluide sous pression (27) est réalisé d'une seule pièce et en acier.
  6. Soupape de commande (20) selon la revendication 1, caractérisée en ce que l'insert de guidage de fluide sous pression (27) est réalisé d'une seule pièce et en plastique.
  7. Soupape de commande (20) selon la revendication 1, caractérisée en ce que le composant interne en forme de douille (44) est fabriqué séparément du composant externe en forme de douille (45) et est connecté à celui-ci au moyen d'une connexion par engagement par force ou par correspondance géométrique ou d'une connexion par collage.
  8. Soupape de commande (20) selon la revendication 1, caractérisée en ce que le composant externe en forme de douille (45) est réalisé sous forme de pièce moulée par injection et le composant interne en forme de douille (44) est réalisé sous forme de composant inséré qui, pendant le processus de moulage par injection du composant externe en forme de douille (45), est surmoulé par ce dernier.
  9. Soupape de commande (20) selon la revendication 1, caractérisée en ce que le canal de fluide sous pression (34) relie le raccord d'entrée (P) à l'intérieur de l'insert de guidage de fluide sous pression (27).
  10. Soupape de commande (20) selon la revendication 9, caractérisée en ce qu'un clapet anti-retour (27b) est disposé à l'intérieur de la soupape de commande (20) en amont du canal de fluide sous pression (34).
  11. Soupape de commande (20) selon la revendication 10, caractérisée en ce qu'un élément de filtre (27a) est disposé à l'intérieur de la soupape de commande (20) en amont du canal de fluide sous pression (34).
  12. Soupape de commande (20) selon la revendication 10, caractérisée en ce que le clapet anti-retour (27b) présente un corps de fermeture (32) sollicité avec une force par un élément de ressort (31), l'élément de ressort (31) s'appuyant sur un palier de ressort (30) réalisé d'une seule pièce avec l'insert de guidage de fluide sous pression (27).
  13. Soupape de commande (20) selon la revendication 11, caractérisée en ce que le clapet anti-retour (27b) présente un corps de fermeture (32) sollicité avec une force par un élément de ressort (31), un palier de ressort (30) et un siège de soupape, au moins le palier de ressort (30) ou le siège de soupape étant réalisé sous forme de composant séparé de l'insert de guidage de fluide sous pression.
  14. Soupape de commande (20) selon la revendication 1, caractérisée en ce qu'il est prévu un élément de ressort de pression à piston (36) qui sollicite avec une force le piston de commande (35) dans une direction axiale, cet élément s'appuyant sur un palier de ressort à piston (30) réalisé d'une seule pièce avec l'insert de guidage de fluide sous pression (27).
  15. Soupape de commande (20) selon la revendication 1, caractérisée en ce qu' qu'il est prévu un élément de ressort de pression à piston (36) qui sollicite avec une force le piston de commande (35) dans une direction axiale, cet élément s'appuyant sur un palier de ressort à piston (30) réalisé séparément de l'insert de guidage de fluide sous pression (27).
  16. Soupape de commande (20) selon la revendication 1, caractérisée en ce qu'il est prévu à la fois un palier de ressort à piston (30) et un palier de ressort (30) réalisé d'une seule pièce avec celui-ci.
  17. Soupape de commande (20) selon l'une quelconque des revendications 10 ou 11, caractérisée en ce que l'élément de filtre (27a) et/ou des parties du clapet anti-retour (27b) sont connectés par engagement par liaison de matière avec l'insert de guidage de fluide sous pression (27).
  18. Soupape de commande (20) selon la revendication 1, caractérisée en ce que l'insert de guidage de fluide sous pression (27) est disposé fixement par rapport au boîtier de soupape (22) à l'intérieur du boîtier de soupape (22).
  19. Soupape de commande selon la revendication 18, caractérisée en ce que l'on prévoit sur l'insert de guidage de fluide sous pression (27) et sur le boîtier de soupape (22) des moyens d'engagement par correspondance géométrique (43) qui servent à la fixation axiale de l'insert de guidage de fluide sous pression (27) par rapport au boitier de soupape (22) et/ou à sa fixation immobilisée dans la direction périphérique.
EP20060807333 2005-11-03 2006-10-17 Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne Active EP1945917B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510052481 DE102005052481A1 (de) 2005-11-03 2005-11-03 Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2006/067482 WO2007051704A1 (fr) 2005-11-03 2006-10-17 Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1945917A1 EP1945917A1 (fr) 2008-07-23
EP1945917B1 true EP1945917B1 (fr) 2009-08-19

Family

ID=37744633

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060807333 Active EP1945917B1 (fr) 2005-11-03 2006-10-17 Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne

Country Status (7)

Country Link
US (1) US7389756B2 (fr)
EP (1) EP1945917B1 (fr)
JP (1) JP2009515090A (fr)
CN (1) CN101300408B (fr)
AT (1) ATE440207T1 (fr)
DE (2) DE102005052481A1 (fr)
WO (1) WO2007051704A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020003430A1 (de) 2020-06-08 2021-12-09 Daimler Ag Rückschlagventil für einen Nockenwellenversteller
DE102021104936A1 (de) 2021-03-02 2022-09-08 Schaeffler Technologies AG & Co. KG Druckmitteleinsatz eines Steuerkolbens mit Druckmittel regulierendem Druckmittelkanal

Families Citing this family (93)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112008001407B4 (de) * 2007-06-19 2018-10-11 Borgwarner Inc. Konzentrischer Nocken mit Versteller
DE102007058491A1 (de) * 2007-12-05 2009-06-10 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102008004591A1 (de) * 2008-01-16 2009-07-23 Schaeffler Kg Hydraulisches Steuerventil mit integriertem Rückschlagventil
DE102008006178A1 (de) * 2008-01-26 2009-07-30 Schaeffler Kg Druckmitteleinsatz für ein Steuerventil in einer hydraulischen Stellvorrichtung
DE102008006179A1 (de) 2008-01-26 2009-07-30 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen in Brennkraftmaschinen
DE102008001078A1 (de) * 2008-04-09 2009-10-15 Robert Bosch Gmbh Vorrichtung zum Verändern der Nockenwellenphasenlage
WO2009134579A2 (fr) 2008-04-28 2009-11-05 Borgwarner Inc. Manchon surmoulé ou embouti pour routage hydraulique de solénoïde
DE102008036183A1 (de) 2008-08-02 2011-07-21 Schaeffler KG, 91074 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102008036182A1 (de) 2008-08-02 2010-02-04 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
CN102245865B (zh) * 2008-12-10 2014-01-29 谢夫勒科技股份两合公司 用于可变地调节内燃机的换气阀的控制时间的装置的控制阀
WO2010066551A1 (fr) * 2008-12-10 2010-06-17 Schaeffler Technologies Gmbh & Co. Kg Valve de commande pour dispositif de réglage variable des temps de commande de vannes d'échange de gaz d'un moteur à combustion interne
DE102009018043A1 (de) 2009-04-18 2010-10-21 Schaeffler Technologies Gmbh & Co. Kg Hydraulikventil
DE102009039385A1 (de) * 2009-08-29 2011-03-03 Schaeffler Technologies Gmbh & Co. Kg Steuerventil
DE102009039384A1 (de) 2009-08-29 2011-03-03 Schaeffler Technologies Gmbh & Co. Kg Steuerventil
DE102009051519A1 (de) 2009-10-31 2011-05-05 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenverstellanordnung
DE102009054049B4 (de) * 2009-11-20 2020-08-27 Schaeffler Technologies AG & Co. KG Nockenwellenverstellanordnung
DE102010005603B4 (de) 2010-01-25 2021-05-20 Schaeffler Technologies AG & Co. KG Nockenwellenverstellanordnung mit einem als Wälzlager ausgebildetem Nockenwellenlager
DE102010008002A1 (de) 2010-02-15 2011-08-18 Schaeffler Technologies GmbH & Co. KG, 91074 Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102010008001B4 (de) 2010-02-15 2022-03-10 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung von Ventilerhebungskurven von Gaswechselventilen einer Brennkraftmaschine
DE102010002713B4 (de) * 2010-03-09 2013-12-05 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit Steuerventil für die hydraulische Verstellung der Phasenlage einer Nockenwelle
DE102010011836A1 (de) 2010-03-18 2011-09-22 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102010064504B3 (de) 2010-03-18 2022-10-20 Volkswagen Ag Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102010012479A1 (de) * 2010-03-24 2011-09-29 Schaeffler Technologies Gmbh & Co. Kg Steuerventil einer Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102010013777A1 (de) 2010-04-03 2011-10-06 Hydraulik-Ring Gmbh Zentralventil
DE202010006605U1 (de) 2010-04-03 2010-11-18 Hydraulik-Ring Gmbh Zentralventil
US8261708B2 (en) * 2010-04-07 2012-09-11 Eaton Corporation Control valve mounting system
DE102010019004B4 (de) 2010-05-03 2014-09-18 Hilite Germany Gmbh Schwenkmotorversteller mit einem Hydraulikventil
JP5182326B2 (ja) * 2010-06-09 2013-04-17 トヨタ自動車株式会社 流量制御弁
DE102010023864B4 (de) 2010-06-15 2018-03-08 Hilite Germany Gmbh Zentralventil für einen Schwenkmotornockenwellenversteller
DE102010026853B4 (de) * 2010-07-12 2024-05-02 Schaeffler Technologies AG & Co. KG Steuerventil zur Steuerung von Druckmittelströmen eines Nockenwellenverstellers
JP5381921B2 (ja) * 2010-07-21 2014-01-08 トヨタ自動車株式会社 センターボルト
DE102010032251A1 (de) * 2010-07-26 2012-01-26 Schaeffler Technologies Gmbh & Co. Kg Rückschlagventil sowie hydraulisches Ventil mit einem eingebauten Rückschlagventil
DE102010044637A1 (de) 2010-09-07 2012-03-08 Hydraulik-Ring Gmbh Zentralventil
DE102010049551A1 (de) * 2010-10-25 2012-04-26 Schaeffler Technologies Gmbh & Co. Kg Steuerventil für einen Nockenwellenversteller
DE102010060181B4 (de) * 2010-10-26 2014-08-21 Hilite Germany Gmbh Zentralventil
DE102011003556B4 (de) 2011-02-03 2022-03-24 Schaeffler Technologies AG & Co. KG Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102011000522A1 (de) 2011-02-04 2012-08-09 Hydraulik-Ring Gmbh Schwenkmotorversteller mit einem Hydraulikventil
DE102011000591B4 (de) 2011-02-09 2018-03-08 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
US8662039B2 (en) 2011-03-16 2014-03-04 Delphi Technologies, Inc. Camshaft phaser with coaxial control valves
US8714859B2 (en) * 2011-07-26 2014-05-06 Raytheon Company Clamping assembly that acts as an interface between two components
JP5360173B2 (ja) * 2011-09-15 2013-12-04 株式会社デンソー バルブタイミング調整装置
DE102011084059B4 (de) 2011-10-05 2016-12-08 Schwäbische Hüttenwerke Automotive GmbH Steuerventil mit integriertem Filter und Nockenwellen-Phasensteller mit dem Steuerventil
DE102012208591B4 (de) 2012-05-23 2018-06-07 Schaeffler Technologies AG & Co. KG Steuerventil für eine hydraulische Steuervorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen an Brennkraftmaschinen
JP5811358B2 (ja) * 2012-05-24 2015-11-11 株式会社デンソー バルブタイミング調整装置
DE102012208812B4 (de) * 2012-05-25 2018-02-01 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012209859A1 (de) 2012-06-13 2013-12-19 Schaeffler Technologies AG & Co. KG Ventileinheit mit axialem Druckmittelzufluss
DE102012210016A1 (de) 2012-06-14 2013-12-19 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleranordnung
DE102012220626A1 (de) * 2012-11-13 2014-05-15 Schaeffler Technologies Gmbh & Co. Kg Steuerventil für eine hydraulische Vorrichtung mit Verriegelung
DE102012220830B4 (de) * 2012-11-15 2018-01-18 Schaeffler Technologies AG & Co. KG Steuerventil für eine hydraulische Vorrichtung mit einer austauschbaren Hydraulikeinheit
JP5682614B2 (ja) 2012-12-04 2015-03-11 株式会社デンソー バルブタイミング調整装置
DE102013207383B4 (de) * 2013-04-24 2022-03-24 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleinrichtung
DE102013104575B4 (de) * 2013-05-03 2018-03-08 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
DE102013209862A1 (de) * 2013-05-28 2014-12-04 Schaeffler Technologies Gmbh & Co. Kg Anordnung eines Elektromagneten zur Ansteuerung eines Zentralventils
JP2015039959A (ja) * 2013-08-22 2015-03-02 ダイハツ工業株式会社 サイドエアバッグ装置
KR101518897B1 (ko) * 2013-09-06 2015-05-11 현대자동차 주식회사 가변 밸브 타이밍 기구를 갖는 엔진
JP6015605B2 (ja) * 2013-09-17 2016-10-26 株式会社デンソー バルブタイミング調整装置
JP6064873B2 (ja) * 2013-11-21 2017-01-25 株式会社デンソー バルブタイミング調整装置
JP5904254B2 (ja) 2013-12-17 2016-04-13 株式会社デンソー 油圧制御弁及びバルブタイミング調整装置
DE102014201562A1 (de) 2014-01-29 2015-07-30 Schaeffler Technologies AG & Co. KG Steuerventil für einen Nockenwellenversteller
CN105934565B (zh) * 2014-03-19 2018-09-11 日立汽车***株式会社 阀正时控制装置的控制阀，以及内燃机的阀正时控制装置
WO2016021328A1 (fr) * 2014-08-04 2016-02-11 日立オートモティブシステムズ株式会社 Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en œuvre une valve oléo-hydraulique
EP3179143A4 (fr) * 2014-08-04 2017-07-19 Hitachi Automotive Systems, Ltd. Valve oléo-hydraulique, et dispositif de commande de réglage de distribution pour moteur à combustion interne mettant en uvre une valve oléo-hydraulique
JP6292083B2 (ja) 2014-08-27 2018-03-14 アイシン精機株式会社 弁開閉時期制御装置
JP6369253B2 (ja) 2014-09-16 2018-08-08 アイシン精機株式会社 弁開閉時期制御装置
JP6442945B2 (ja) 2014-09-16 2018-12-26 アイシン精機株式会社 弁開閉時期制御装置
JP6217587B2 (ja) 2014-10-21 2017-10-25 アイシン精機株式会社 弁開閉時期制御装置
US9587527B2 (en) 2014-11-04 2017-03-07 Delphi Technologies, Inc. Camshaft phaser
DE102014223503A1 (de) 2014-11-18 2015-11-26 Schaeffler Technologies AG & Co. KG Schnell schaltender hydraulischer Nockenwellenversteller mit zwei gleichsinnig durchlässigen Rückschlagventilen
DE102015200543B4 (de) 2015-01-15 2020-11-05 Schaeffler Technologies AG & Co. KG Steuerventil mit Ablaufkanal und Verbrennungsmotor
JP6308163B2 (ja) * 2015-04-08 2018-04-11 株式会社デンソー バルブタイミング調整装置
JP6396851B2 (ja) * 2015-06-02 2018-09-26 日立オートモティブシステムズ株式会社 油圧制御弁及び該油圧制御弁が用いられた内燃機関のバルブタイミング制御装置
DE102015213135B3 (de) 2015-07-14 2017-01-05 Schaeffler Technologies AG & Co. KG Steuerventil für einen Nockenwellenversteller
US20180266286A1 (en) * 2015-09-21 2018-09-20 Schaeffler Technologies AG & Co. KG Control valve for a camshaft adjuster
JP6578896B2 (ja) * 2015-11-09 2019-09-25 アイシン精機株式会社 弁開閉時期制御装置
US10082054B2 (en) 2015-11-10 2018-09-25 Delphi Technologies Ip Limited Camshaft phaser
US9976450B2 (en) 2015-11-10 2018-05-22 Delphi Technologies Ip Limited Camshaft phaser
JP6410742B2 (ja) 2016-01-08 2018-10-24 アイシン精機株式会社 弁開閉時期制御装置
DE102016201513A1 (de) 2016-02-02 2017-08-03 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Trennhülse
US9957853B2 (en) 2016-08-30 2018-05-01 Delphi Technologies Ip Limited Camshaft phaser
JP6769253B2 (ja) * 2016-11-14 2020-10-14 アイシン精機株式会社 弁開閉時期制御装置
JP6834381B2 (ja) 2016-11-14 2021-02-24 アイシン精機株式会社 弁開閉時期制御装置
JP6834382B2 (ja) 2016-11-14 2021-02-24 アイシン精機株式会社 弁開閉時期制御装置
JP6790925B2 (ja) * 2017-03-07 2020-11-25 株式会社デンソー 作動油制御弁、および、これを用いたバルブタイミング調整装置
JP2018138779A (ja) 2017-02-24 2018-09-06 アイシン精機株式会社 弁開閉時期制御装置
CN107869476B (zh) * 2017-12-11 2024-03-08 重庆通用工业(集团)有限责任公司 传动装置及离心通风机***
DE102018102206A1 (de) * 2018-02-01 2019-08-01 ECO Holding 1 GmbH Einstellbare Hydraulikbaugruppe
DE102018115343A1 (de) 2018-06-26 2020-01-02 Schaeffler Technologies AG & Co. KG Steuerventil mit Dichtkontur auf einem hülsenförmigen Hydraulikleitelement; sowie Bausatz mit Steuerventil und Nockenwellenversteller
JP2020007943A (ja) 2018-07-05 2020-01-16 アイシン精機株式会社 弁開閉時期制御装置
DE102019109536B4 (de) * 2019-04-11 2022-03-03 ECO Holding 1 GmbH Nockenwellenversteller vom Flügelzellentyp
DE102020119092A1 (de) * 2019-07-25 2021-01-28 ECO Holding 1 GmbH Verfahren zum Herstellen eines Nockenwellenverstellers und Nockenwellenversteller
US11131221B1 (en) * 2020-08-19 2021-09-28 Schaeffler Technologies AG & Co. KG Central valve for camshaft phaser
DE102020127280A1 (de) 2020-10-16 2022-04-21 Schaeffler Technologies AG & Co. KG Steuerventil
CN112502840B (zh) * 2020-12-18 2022-09-16 中船动力有限公司 柴油机燃油定时液压调节装置

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4439984A (en) * 1981-07-20 1984-04-03 Pall Corporation Coaxial bidirectional spool valve
US5289805A (en) * 1992-03-05 1994-03-01 Borg-Warner Automotive Transmission & Engine Components Corporation Self-calibrating variable camshaft timing system
US5325762A (en) * 1992-10-29 1994-07-05 Nordson Corporation Fluid pressure operated piston engine assembly
US5377720A (en) * 1993-11-18 1995-01-03 Applied Power Inc. Proportional pressure reducing and relieving valve
DE19729935B4 (de) * 1997-07-12 2006-11-16 Hydraulik-Ring Gmbh Hydraulisches Einbauventil, insbesondere für eine hydraulische Nockenwellenverstellung an einem Kraftfahrzeugmotor
JP4070857B2 (ja) * 1997-12-17 2008-04-02 トヨタ自動車株式会社 内燃機関のバルブ特性制御装置
US6382148B1 (en) * 1999-06-10 2002-05-07 Unisia Jecs Corporation Oil pressure control apparatus for an internal combustion engine
DE19944535C1 (de) * 1999-09-17 2001-01-04 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
DE10044486A1 (de) * 1999-10-05 2001-04-12 Schaeffler Waelzlager Ohg Verfahren und Vorrichtung zur Regelung der axialen Lage des Ventilkolbens eines Hydraulikventils
DE10308074A1 (de) * 2003-02-26 2004-09-09 Hydraulik-Ring Gmbh Ventil, vorzugsweise Proportionalmagnetventil
DE10322394A1 (de) * 2003-05-12 2004-12-02 Hydraulik-Ring Gmbh Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen
US6799544B1 (en) * 2003-05-29 2004-10-05 Delphi Technologies, Inc. Method and apparatus for actuating a cam phaser
DE10346443A1 (de) * 2003-10-07 2005-05-04 Daimler Chrysler Ag Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine
DE10346446A1 (de) * 2003-10-07 2005-05-12 Daimler Chrysler Ag Nockenwellenversteller für eine Brennkraftmaschine mit Hydraulikmittelführungen
DE10359364B4 (de) * 2003-12-18 2012-10-11 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetisches Hydraulikventil, insbesondere 3/2-Wegeschaltventil zur Steuerung eines varialblen Ventiltriebes einer Brennkraftmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020003430A1 (de) 2020-06-08 2021-12-09 Daimler Ag Rückschlagventil für einen Nockenwellenversteller
DE102021104936A1 (de) 2021-03-02 2022-09-08 Schaeffler Technologies AG & Co. KG Druckmitteleinsatz eines Steuerkolbens mit Druckmittel regulierendem Druckmittelkanal

Also Published As

Publication number Publication date
WO2007051704A1 (fr) 2007-05-10
DE102005052481A1 (de) 2007-05-24
CN101300408A (zh) 2008-11-05
JP2009515090A (ja) 2009-04-09
EP1945917A1 (fr) 2008-07-23
US20070095315A1 (en) 2007-05-03
ATE440207T1 (de) 2009-09-15
DE502006004615D1 (de) 2009-10-01
US7389756B2 (en) 2008-06-24
CN101300408B (zh) 2011-09-28

Similar Documents

Publication Publication Date Title
EP1945917B1 (fr) Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne
EP1924759B1 (fr) Soupape de distribution destinee a un dispositif pour modifier les temps de distribution d'un moteur a combustion
EP1596040B1 (fr) Déphaseur d'arbre à cames
EP2470756B1 (fr) Vanne de commande
EP2452052B1 (fr) Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne
DE102004036096B4 (de) Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
EP1896699B1 (fr) Soupape de commande pour un dispositif de reglage variable des temps de commande de soupapes d'echange des gaz d'un moteur a combustion interne
DE112009004393B4 (de) Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE202005008264U1 (de) Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
EP1596041A2 (fr) Valve de commande pour déphaseur d'arbre à cames de moteur à combustion interne
EP2220345B1 (fr) Dispositif de réglage variable de la distribution de soupapes de renouvellement des gaz d'un moteur à combustion interne
DE102006022402A1 (de) Steuerventil für einen Nockenwellenversteller
WO2010015541A1 (fr) Dispositif de réglage variable des temps de commande de soupapes d’échange des gaz d’un moteur à combustion interne
EP2470757B1 (fr) Vanne de commande
WO2010139522A1 (fr) Soupape de commande pour commander des flux d'agent de pression avec clapet anti-retour intégré
DE102010008001B4 (de) Vorrichtung zur variablen Einstellung von Ventilerhebungskurven von Gaswechselventilen einer Brennkraftmaschine
EP2220346B1 (fr) Dispositif de réglage variable de la distribution des soupapes de renouvellement des gaz d'un moteur à combustion interne
EP2536926A1 (fr) Roue à aubes d'un dispositif pour l'ajustement variable des temps de commande de soupapes d'échange gazeux d'un moteur à combustion interne
DE102012201573A1 (de) Nockenwellenversteller
DE102004038160B4 (de) Nockenwellenversteller
DE102005024241B4 (de) Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
WO2013174533A1 (fr) Soupape de commande d'un déphaseur d'arbre à cames
DE102012202823B4 (de) Nockenwellenversteller
EP2536925B1 (fr) Dispositif de réglage variable des temps de commande des vannes d'échange de gaz d'un moteur à combustion interne
DE102021104936A1 (de) Druckmitteleinsatz eines Steuerkolbens mit Druckmittel regulierendem Druckmittelkanal

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

17P Request for examination filed

Effective date: 20080603

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20080908

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
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): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK 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: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502006004615

Country of ref document: DE

Date of ref document: 20091001

Kind code of ref document: P

REG Reference to a national code

Ref country code: RO

Ref legal event code: EPE

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20090819

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

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: 20090819

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: 20090819

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: 20091130

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: 20091219

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: 20090819

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

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: 20090819

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: 20090819

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: 20090819

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: 20090819

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E006827

Country of ref document: HU

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: 20090819

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: 20091119

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: 20091221

BERE Be: lapsed

Owner name: SCHAEFFLER K.G.

Effective date: 20091031

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

Ref country code: IE

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: 20090819

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: 20090819

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: 20090819

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: 20090819

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG

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 NON-PAYMENT OF DUE FEES

Effective date: 20091031

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: 20090819

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: 20100520

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: 20091120

Ref country code: BE

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

Effective date: 20091031

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: 20091017

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

Ref country code: RO

Payment date: 20101008

Year of fee payment: 5

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

Ref country code: GB

Payment date: 20101029

Year of fee payment: 5

Ref country code: IT

Payment date: 20101025

Year of fee payment: 5

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 NON-PAYMENT OF DUE FEES

Effective date: 20091017

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20110407 AND 20110413

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: LI

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

Effective date: 20101031

Ref country code: CH

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

Effective date: 20101031

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

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: 20090819

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

Ref country code: FR

Payment date: 20111115

Year of fee payment: 6

Ref country code: HU

Payment date: 20111014

Year of fee payment: 6

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502006004615

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

Ref country code: DE

Ref legal event code: R081

Ref document number: 502006004615

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

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

Effective date: 20121017

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130628

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

Ref country code: GB

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

Effective date: 20121017

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 NON-PAYMENT OF DUE FEES

Effective date: 20121017

Ref country code: FR

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

Effective date: 20121031

Ref country code: HU

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

Effective date: 20121018

Ref country code: IT

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

Effective date: 20121017

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502006004615

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140217

Ref country code: DE

Ref legal event code: R081

Ref document number: 502006004615

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140217

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502006004615

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150223

REG Reference to a national code

Ref country code: DE

Ref legal event code: R008

Ref document number: 502006004615

Country of ref document: DE

Ref country code: DE

Ref legal event code: R039

Ref document number: 502006004615

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R040

Ref document number: 502006004615

Country of ref document: DE

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230522

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

Ref country code: DE

Payment date: 20231214

Year of fee payment: 18