EP1924759B1 - Soupape de distribution destinee a un dispositif pour modifier les temps de distribution d'un moteur a combustion - Google Patents

Soupape de distribution destinee a un dispositif pour modifier les temps de distribution d'un moteur a combustion Download PDF

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Publication number
EP1924759B1
EP1924759B1 EP20060762977 EP06762977A EP1924759B1 EP 1924759 B1 EP1924759 B1 EP 1924759B1 EP 20060762977 EP20060762977 EP 20060762977 EP 06762977 A EP06762977 A EP 06762977A EP 1924759 B1 EP1924759 B1 EP 1924759B1
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EP
European Patent Office
Prior art keywords
pressure medium
control valve
control piston
valve
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
EP20060762977
Other languages
German (de)
English (en)
Other versions
EP1924759A1 (fr
Inventor
Gerhard Scheidig
Ali Bayrakdar
Jens Hoppe
Rainer Ottersbach
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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Filing date
Publication date
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Publication of EP1924759A1 publication Critical patent/EP1924759A1/fr
Application granted granted Critical
Publication of EP1924759B1 publication Critical patent/EP1924759B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34483—Phaser return springs
    • 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

Definitions

  • the invention relates to a control valve for a device for changing the timing of an internal combustion engine according to the preamble of claims 1 or 2 and a device for changing the timing of an internal combustion engine according to the preamble of claim 18th
  • 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 particularly desirable for the opening and closing times of the intake or to be able to exert an influence separately on exhaust valves, for example, to set a defined valve overlap in a targeted manner.
  • the specific fuel consumption can be reduced, the exhaust behavior positively influenced, the engine efficiency, the maximum torque and the maximum power increases become.
  • the described variability of the gas exchange valve timing is achieved by a relative change in the phase angle of the camshaft to the crankshaft.
  • the camshaft is usually via a chain, belt, gear drive or equivalent drive concepts in drive connection with the crankshaft.
  • a device for changing 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.
  • 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. It consists of a driven by the crankshaft, a fixed phase relation to this holding drive wheel, one in drive connection standing with the camshaft driven part and a torque transmitting from the drive wheel to the driven part adjusting mechanism.
  • 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 adjustment 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 part via helical gears in combination.
  • the piston separates a cavity formed by the driven part and the drive wheel into two pressure chambers arranged axially relative to one another. 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 part and thus the camshaft to the crankshaft.
  • a second embodiment of hydraulic phaser are the so-called Rotationskolbenverstelter.
  • 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.
  • each cavity in two pressure chambers Splits.
  • 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 connections. 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 leaving the pressure chambers is guided becomes. 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 by means of an electromagnetic, pneumatic or hydraulic actuator, against the spring force of a spring member axially in any position between two defined end positions.
  • the control piston is further provided with control edges, whereby the working ports with the supply ports and thus the individual pressure chambers or groups of pressure chambers can be selectively connected to the pressure medium pump or the tank.
  • a position of the control piston may be provided, in which the Druckstoffkammem are separated from both the pressure medium pump and the pressure medium tank.
  • Such a control valve is out of US 6,363,896 B1 known.
  • This consists of a substantially hollow cylindrical valve housing and an axially displaceably arranged therein control piston.
  • On the valve housing two working ports, an inlet port and a drain 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.
  • an axial outlet connection is provided, via which pressure medium can be removed from the control valve.
  • 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 either be directly connected to the one working connection or be connected by means of a pressure medium channel formed within the control piston with the other working port.
  • a supply line is provided, via which the inlet connection communicates with a pressure medium pump which continuously supplies the control valve with pressure medium.
  • the position of the inlet connection between the working connections requires an elaborate supply of material within the output element.
  • On the one hand are located within an axial portion of the output element both radially extending pressure medium lines, starting from one of the working ports, as well as axially extending supply lines, starting from the radial supply port.
  • This accumulation of lines in an axial section reduces their maximum flow cross-sections.
  • a further disadvantage arises from the fact that a connection between the axial supply lines and the radial pressure medium lines must be prevented.
  • the supply lines are formed by a plurality of thin bores communicating with each other, via which pressure medium is supplied from a camshaft bearing to the inlet port.
  • the formation of these holes is very expensive and error-prone.
  • the process reliability suffers because the thin drills tend to break during the formation of the holes.
  • the EP 1447602 A1 shows an oil control valve for a phaser. There is provided a check valve by which a backflow of oil is prevented in the engine oil system.
  • the check valve is integrated in the housing of the oil control valve. As a result, the control piston of the oil control valve is not affected by a sudden change in oil pressure.
  • the invention is therefore based on the object to avoid these disadvantages and thus to provide a hydraulic control valve, wherein the Pressure medium supply to the inlet port and the pressure fluid discharge from the tank connection by simple, inexpensive to produce constructive features can be accomplished.
  • Another object is to realize a simple and inexpensive to produce connection between the working ports and the pressure chambers of the camshaft adjuster.
  • a control valve for a device for variably setting the timing of gas exchange valves of an internal combustion engine having a substantially hollow cylindrical valve housing, and a control piston axially displaceably arranged therein, wherein exactly two working ports, exactly one first and exactly one second supply port on the valve housing are formed, via one of the supply ports to the control valve pressure medium supplied from a pressure medium pump and the other supply port pressure medium from the control valve can be discharged into a tank, both working ports and the first supply port are formed by at least one radial opening in an outer circumferential surface of the valve housing wherein the working ports and the first supply port are spaced apart in the axial direction, and wherein the first supply port communicates with a supply line, the object is achieved in that the working ports are arranged directly adjacent in the axial direction and the first supply port is connected in the axial direction on the side of the supply line to the working ports.
  • the control valve consists of a substantially hollow cylindrical valve housing and a control piston arranged axially displaceable therein.
  • the valve housing is arranged within a valve receptacle of a surrounding structure, for example a camshaft, a cylinder head or an output element of a camshaft adjuster, wherein the outer diameter of the valve housing is adapted to the inner diameter of the valve receptacle.
  • On the outer lateral surface of the valve housing at least three axially spaced connections in the form of radial openings of the valve housing are formed.
  • the one radial connection serves as a supply connection.
  • the remaining radial ports serve as working ports, via which pressure medium can be passed to the pressure chambers of the device or discharged from them.
  • the supply connection as an inlet connection, via which the control valve pressure medium is supplied, or as a drain connection, via the pressure medium the control valve is discharged serve.
  • the supply connection is arranged in the axial direction such that no working connection is arranged between it and an axial end of the control valve. Due to this arrangement of the supply connection, a strict separation in the axial direction is established between the pressure medium lines communicating with the working connections and the supply line which communicates with the supply connection.
  • the axially extending supply line no longer penetrates into the region of the radial pressure medium lines which communicate with the working ports.
  • Another advantage is that the axial pressure medium channels can be formed with larger cross-sectional areas. Overall, this leads to a considerable simplification of the pressure medium system and thus to a reduction in the manufacturing cost of the device.
  • the supply line is at least partially formed as an annular space between the valve housing and the surrounding structure.
  • the supply line can be formed, at least in sections, as at least one groove, which opens out onto the outer jacket surface of the control piston and opens into the first supply connection.
  • a further simplification of the pressure medium system results from the fact that the supply line is realized by a gap between the valve housing and the valve receptacle of the surrounding construction.
  • a valve housing comprehensive annular channel or one or more circumferentially spaced longitudinal grooves may be provided, which open into the radial supply port.
  • the inner diameter of the valve receptacle is larger than the outer diameter of the valve housing.
  • the longitudinal grooves these may be on an inner lateral surface of the valve seat or an outer lateral surface of the Valve housing are formed. In both cases, this can be done inexpensively or cost-neutral during the molding process.
  • each of the pressure fluid channels communicates with each of the control piston in any position of the supply ports, each of the pressure fluid channels by appropriate positioning of the control piston relative to the valve housing with at least one the working connections can be connected and wherein at least one of the pressure medium channels is not formed rotationally symmetrical with respect to the longitudinal axis of the control valve.
  • a control valve for a device for variably setting the timing of gas exchange valves of an internal combustion engine having a substantially hollow cylindrical valve housing, and a axially displaceably arranged therein control piston, wherein on the valve housing two working ports and two supply ports are formed, each working port through at least one radial opening in an outer circumferential surface of the valve housing is formed, wherein the working ports are spaced apart in the axial direction, wherein at least two axially extending, mutually delimited pressure fluid channels are formed on the control piston, each of the pressure fluid channels in each position of the control piston with one of the supply ports communicates with each of the pressure medium channels by suitably positioning the control piston relative to the valve housing with at least one of the Ar Beitsan say can be connected, the object is achieved in that at least one of the pressure medium channels is not formed rotationally symmetrical with respect to the longitudinal axis of the control valve.
  • the control piston can be used for different valve housing configurations.
  • an insert may be provided in a control valve on whose valve housing the working connections are arranged directly adjacent.
  • an insert in a control valve between the radial working ports a supply connection is provided.
  • the working connections are arranged directly adjacent in the axial direction. It can be formed on the valve housing exactly two working connections and / or exactly two supply connections. Furthermore, it can be provided that one of the supply connections is designed as a feed connection, via which the control valve pressure medium is supplied and / or that one of the supply connections is designed as a drain port can be discharged via the pressure medium from the control valve to a tank.
  • the non-rotationally symmetrical design according to the invention of at least one pressure medium channel with respect to the longitudinal axis of the control valve offers the advantage of establishing the communication between the working connection farther from the radial supply connection and the supply connection without establishing a connection to the working connection therebetween. This can be done without further design features, such as adapters, while still being able to dispense with the formation of further supply connections to the valve housing.
  • At least one pressure medium channel is formed on an outer circumferential surface of the control piston.
  • this embodiment of the invention is one of the pressure medium channels in the interior formed of the control piston and provided as a second pressure medium channel extending in the axial direction of a groove on the outer circumferential surface of the control piston. From the axially extending groove one or two axially spaced, extending in the circumferential direction of grooves, which establish the connection between the second pressure medium channel and the circumferentially to the pressure medium channel spaced radial openings in the valve housing, which form the working connections. In the case of a circumferentially extending groove, two radial openings are provided on the control piston through which the exterior of the control piston can communicate with its interior.
  • the circumferentially extending groove is located on the outer circumferential surface of the control piston in the axial direction between the openings and between the working ports, while the openings comprise the working ports in the axial direction.
  • the circumferentially extending groove may communicate with either the first or the second working port.
  • one of the two openings of the control piston communicates with the other working connection.
  • a radial opening is provided on the control piston. This lies in the axial direction between the two circumferentially extending channels and between the working ports, the circumferentially extending grooves comprising the working ports.
  • one of the two circumferentially extending grooves can communicate with the corresponding working port, while the connection of the other groove is interrupted with the other working port.
  • the opening of the control piston communicates with the other work connection.
  • the controls may be arranged on the control piston such that a middle position exists in which either both working ports only communicate with the inlet port or with none of the supply ports. In this position of the control piston, the phase position of the device is maintained.
  • control piston all pressure medium channels are formed within the control piston.
  • a pressure medium channels separating wall can be integrally formed with the control piston.
  • control piston it is also conceivable to form the control piston as a substantially hollow cylindrical component, in the interior of which a separately manufactured insert component is provided, wherein the insert component forms the pressure medium channels in cooperation with an inner circumferential surface of the control piston.
  • At least two separate pressure medium channels are formed within the control piston, which communicate via radial openings with the exterior of the control piston and thus can be connected to the working ports.
  • each of the pressure medium passages can be connected to each of the working ports by suitably positioning the control piston relative to the valve body. This measure ensures that exactly two supply connections, namely an inlet connection and a discharge connection, are required in order to operate the device.
  • control piston is made of a plastic and is produced by means of an injection molding process. Molds are produced for the injection molding process which already have all the typical geometric features of the finished component.
  • the component is produced by filling the plasticized plastic into the mold and then curing the mass.
  • undercuts or cavities by means of slide and / or Kemzugtechnologie, wherein the non-material to be filled spaces are filled with one or more moldings during the injection molding process.
  • These moldings are elements of the injection mold and can be removed again from the workpiece after completion of the injection molding operation. Basically, the use of lost cores is conceivable.
  • control piston consists of a metal and is produced by means of a metallurgical injection molding process, also known as metal injection molding (MIM).
  • MIM metal injection molding
  • This process is analogous to the plastic injection molding process described above, in which case the material to be introduced into the mold consists of a mixture of fine metal powder and organic binders. The volume fraction of the metal powder is usually more than 50%.
  • the organic binder and any lost cores are removed in a subsequent debinding process. This can be done either by thermal decomposition and subsequent evaporation or by solvent extraction.
  • the remaining porous moldings are compacted by sintering under various shielding gases or under vacuum to give the components having the final geometric properties.
  • the advantage of this manufacturing method is that even structures that are not rotationally symmetrical to the longitudinal axis of the control piston, can be produced inexpensively and reliably.
  • the device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine comprises at least two mutually acting pressure chambers, by means of which the phase position between a camshaft and a crankshaft can be adjusted or held either.
  • the pressure chambers pressure medium is supplied or derived from these.
  • a control valve is provided on which at least two working ports and at least two supply ports, in the form of an inlet and a drain port are formed. At least one of the supply ports is formed as at least one radial opening on an outer circumferential surface of the valve housing, wherein this connects in the axial direction of the control valve to the radially formed working ports.
  • This supply connection communicates with a supply line which is designed at least in sections as formed on the valve receptacle of the surrounding construction, axially extending groove.
  • the surrounding construction may be a rotor of a camshaft adjuster, a camshaft, a cylinder head cover or a cylinder head.
  • the groove can be formed cost-neutral during the manufacture of the surrounding structure. For example, this can be realized cost-neutral by simple modifications of the forming tool in the manufacture of a rotor made of sintered steel.
  • the working ports can also be designed as axially spaced radial openings in the valve housing, wherein these in the axial direction on the side facing away from the groove side of the supply terminal to connect to this.
  • an axial supply connection can be provided, wherein at least two pressure medium channels are formed on the control piston, wherein each of the pressure medium channels is connected to one of the supply connections.
  • at least one of the pressure medium channels is not rotationally symmetrical with respect to the longitudinal axis of the control valve. It can be provided that all pressure medium channels are formed within the control piston.
  • the pressure medium channels from each other separating wall can be integrally formed with the control piston.
  • the control piston may be formed as a substantially hollow cylindrical component, in the interior of which a separately manufactured insertion component is provided, wherein the insertion component forms the pressure medium channels in cooperation with an inner circumferential surface of the control piston.
  • 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, only one of the camshafts 106, 107 can be provided with a device 1, or only one camshaft 106, 107 provided with a device 1 is provided.
  • FIGS. 2a . 2 B 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 1a essentially consists of a drive wheel 5, a stator 2 and a rotor arranged concentrically therewith, referred to below as output element 3.
  • the output element 3 consists of a wheel hub 4, on whose outer circumference five wings 6 are formed, which extend radially outward.
  • 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 closed 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 driven element 3 are arranged within a cup-shaped housing 11, which kapseit these components by interacting with the drive wheel 5 fluid-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 by means of a sealing joining process or be realized by the use of a sealant, not shown.
  • 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 central screw 17 passes through the opening 16 and the central bore 4b, wherein a threaded portion of the central screw 17 engages in a provided with an internal thread receptacle 18 of the camshaft 3a.
  • the central screw 17 is further provided with a collar 19 which is supported in the assembled state of the central screw 17 either directly or indirectly on the output element 3 and thus rotatably connected to the camshaft 3a.
  • 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.
  • the central screw 17 is provided with a blind hole-like receptacle 21, which extends to the camshaft facing away from the axial end of the central screw 17.
  • the resulting cylindrical outer 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 valve housing 22 is provided with three groups of axially spaced-apart openings 23 a, b, c, via which the exterior of the valve housing 22 can communicate with the receptacle 21.
  • Each group of openings 23a, b, c forms a pressure medium connection of the control valve 20, the camshaft-side group of openings 23a forming a supply connection 24 and the two other groups of openings 23b, c serving as working connections A, B.
  • two axially spaced annular channels 25a, 25b are formed in the form of radially inwardly open annular grooves, which are bounded by the valve housing 22 radially inwardly.
  • Each of the ring channels 25a, 25b communicates with one of Working connections A, B.
  • two groups of pressure medium lines 26 are formed, each of the pressure medium lines 26 on the one hand communicates with one of the pressure chambers 14, 15 and on the other hand with one of the annular channels 25a, 25b.
  • the supply port 24 of the valve housing 22 is formed in the illustrated embodiment as a feed port P, via the control valve 20 pressure medium is supplied from a pressure medium pump. This is in fluid communication with a formed between the central screw 17 and the camshaft 3a supply line 27.
  • the supply line 27 communicates via formed in the region of a camshaft bearing 28 tap holes 29 and a rotary feedthrough, not shown, with a likewise not shown pressure medium pump.
  • a substantially hollow cylindrical trained control piston 30 is received axially displaceable.
  • its outer diameter is adapted to the inner diameter of the receptacle 21 of the valve housing 22.
  • the control piston 30 can be arbitrarily positioned by means of an actuating unit 31 via a push rod 32 against the force of a spring element 33 in the axial direction within the valve housing 22.
  • the respective annular grooves 39a, 39b, 39c communicate with the interior of the control piston 30 via the radial openings 34a, 34b, 34c. Furthermore, fourth radial openings 35 are formed on the end of the control piston 30 remote from the camshaft.
  • a drain port T from, via the pressure medium from the control valve 20 can be removed.
  • the inflow port P pressure medium can be supplied, which, depending on the position of the control piston 30 relative to the valve housing 22, to one of the two working ports A, B can be passed.
  • the pressure medium passes via the working port A, B the corresponding annular channel 25a, 25b and the corresponding pressure medium line 26 to the respective pressure chamber 14, 15.
  • At least one axially extending groove 38b is provided, which connects the annular space 38a to the inlet port P.
  • the groove 38b may be formed either on an inner wall of the surrounding structure, in the illustrated case the camshaft 3a and the output element 3, or the outer circumferential surface of the valve housing 22. In any case, these can be formed during the manufacturing process of the respective component cost neutral or with little additional effort. This is compared to the wells described in the prior art a considerable simplification, while at the same time increasing process safety and thereby reducing the scrap rate. Overall, this leads to a significant cost reduction in the production of the device. 1
  • control valve 20 is not limited to the illustrated embodiment. It is also conceivable, the output element 3 not rotatably with a central screw 17, but other friction, material, non-positive or positive means to connect with the camshaft 3a, wherein within a central bore 4b of the output element 3, a control valve 20 is arranged. Likewise, the control valve 20 according to the invention may also be designed as a so-called. Plug-in or cartridge valve, which is arranged in a formed on a cylinder head or a cylinder head cover valve receptacle 4a. In the case of central valve applications, the control valve 20, depending on the design of the device 1, for example, be arranged within the driven element 3, the camshaft 3a or an extension of the camshaft 3a. The inlet P and the outlet connection T may be arranged on the cam shaft facing or -abgewandten end or at different ends of the control valve 20. In this case, the radial supply connection 24 can serve both as supply P and as discharge connection T.
  • a first embodiment of a control valve 20 according to the invention is in the Figures 2c . 3, 3a-c shown.
  • the outer diameter of the outer circumferential surface of the substantially hollow cylindrical control piston 30 is adapted to the inner diameter of the valve housing 22.
  • three annular grooves 39a, b, c are formed on the outer lateral surface of the control piston 30, wherein these are arranged spaced apart in the axial direction.
  • a first, central pressure medium channel 40 is formed, to which two second pressure medium channels 41 adjoin in the radial direction, which extend in the cross section of the control piston 30 only within an angular segment of less than 360 °.
  • the pressure medium channels 40, 41 are separated from each other within the control piston 30 by walls 42, wherein the two second pressure medium channels 41 are arranged opposite to the longitudinal axis 36 of the control piston 30 opposite.
  • the second pressure medium channels 41 communicate with the first and third annular grooves 39a, 39c via the first and third radial openings 34a, 34c, respectively.
  • the first pressure medium channel 40 communicates via the second radial openings 34b with the second annular groove 39b.
  • the second radial openings 34b offset from the first and the third radial openings 34a, 34c in the circumferential direction by 90 °, whereby it is achieved that the first pressure medium channel 40 exclusively with the second annular groove 39b and the second pressure medium channels 41 exclusively with the first and third annular groove 39a, 39c communicate.
  • the first annular groove 39a is designed such that it communicates with the inlet port P relative to the valve housing 22 in each position of the control piston 30. Pressure medium entering the control valve 20 via the inlet port P passes into the first annular groove 39a and via the second pressure medium channels 41 to the third annular groove 39c.
  • the pressure medium passes either via the first annular groove 39a to the working port B or via the third annular groove 39c to the working port A and from there to the respective pressure chamber 14, 15.
  • the pressure medium enters the central Pressure medium channel 40, from where it is directed in the axial direction to the drain port T and thus discharged from the control valve 20.
  • the walls 42 prevent the pressure medium to be discharged from entering the first or third annular groove 39a, 39c.
  • the pressure medium channels 40, 41 are formed in this embodiment by an insert 43, which is made separately to the control piston 30 and is then arranged by means of a force, form, frictional or cohesive connection in the interior thereof.
  • FIGS. 4, 4a-d show a further embodiment of a control piston 30 of a control valve 20 according to the invention.
  • This is identical in many parts to that in FIG. 3
  • the separation between the pressure medium channels 40, 41 realized by means of one piece with the control piston 30 running walls 42.
  • a first central pressure medium channel 40 is formed, followed by two opposing second pressure medium channels 41 in the radial direction.
  • the second pressure medium channels 41 are again not rotationally symmetrical with respect to the longitudinal axis 36 of the control piston 30.
  • the first pressure medium channel 40 communicates on the one hand with the drain port T and on the other hand with the second annular groove 39b.
  • the second pressure medium channels 41 communicate with both the first and the third annular groove 39a, 39c.
  • FIGS 5, 5a-5d show a third embodiment of a control piston 30 of a control valve 20 according to the invention, which is identical to the first two embodiments in large parts.
  • two first and two second pressure medium channels 41 are arranged within the control piston 30, two first and two second pressure medium channels 41 are arranged.
  • the first and second pressure medium channels 40, 41 in turn extend in the axial direction, but are arranged alternately in the circumferential direction in this embodiment.
  • the pressure medium channels 40, 41 separating walls 42 are not; as in the first two Embodiments, designed as circular chords, but extend along two mutually perpendicular inner diameter of the control piston 30th
  • the second pressure medium channels 41 facing one another in the vertical direction in the illustrations 5a-5d in turn connect the first to the third annular groove 39a, 39c, while the horizontally opposed first pressure medium channels 40 connect the drain port T to the second annular groove 39b.
  • control valve 20 In addition to the one-piece design of the control valve 20 with a central screw 17 through which the device 1 is attached to the camshaft 3a, embodiments are also conceivable in which the device 1 is fixed by means of non-positive, positive or cohesive connections to a camshaft 3a and the Control valve 20 is designed as a separate component. Also conceivable is the use of a control valve 20 according to the invention as a so-called plug-in or cartridge valve, which is mounted in a valve seat 4a in the cylinder head or cylinder head cover, wherein the working ports A, B of the control valve 20 are passed by suitable pressure medium lines and rotary unions to the adjuster.
  • control piston 30 of the control valve 20 according to the invention or the insert 43 is produced by means of an injection molding process. It is conceivable here to produce the components from a suitable plastic by means of a plastic injection molding method or from metal by means of a powder metallurgical injection molding method, also known as a metel-injection molding method. In both processes, moldings are produced which already have all the typical geometric features of the component in the negative. In these moldings, the plasticized plastic is introduced under pressure in the case of a plastic injection molding. Subsequently, the plastic is cured and can be removed from the reusable molding after this step.
  • the shaped body is filled with a mixture of fine metal powder and organic binders during the injection molding process. Subsequently, the organic binders are removed, for example, by evaporation or solvent extraction, and the remaining blank is compacted by sintering under appropriate protective gases or vacuum to the finished control piston 30.
  • injection molding methods have the advantage that the shaping of the components can be carried out without costly machining such as milling or drilling.
  • the non-rotationally symmetrical design of the pressure medium channels 40, 41 shown in the embodiments has the advantage that on the cylindrical surface of the valve housing 22 no additional openings must be formed, and thus less structural features must be realized. This leads to a considerable cost reduction in the production of the control valve 20.
  • valve housing 22 In addition to the illustrated embodiments or analogous modifications, it is also possible to form one of the pressure medium channels 40, 41 within the control piston 30 and the other of the pressure medium channels 40, 41 on the outer circumferential surface of the control piston 30.
  • the working ports A, B must be arranged at excellent positions of the valve housing 22 in the circumferential direction.
  • an anti-rotation device between valve housing 22 and control piston 30 must be provided.

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

Abstract

L'invention concerne une soupape de distribution (20) destinée à un dispositif (1) servant à régler de façon variable les temps de distribution de soupapes de changement des gaz (110, 111) d'un moteur à combustion (100). Deux raccords de travail (A, B) et un raccord d'alimentation (24) sont formés au niveau d'une surface latérale extérieure d'un corps (22) de la soupape de distribution (20), les raccords de travail (A, B) étant disposés directement l'un à côté de l'autre et le raccord d'alimentation (24) étant adjacent à ceux-ci. Par ailleurs, deux canaux à fluide de pression (40, 41) sont formés au niveau du piston de distribution (30), au moins un de ces canaux à fluide de pression (40, 41) étant caractérisé par une absence de symétrie de révolution par rapport à l'axe longitudinal (36) du piston de distribution (30).

Claims (14)

  1. Soupape pilote (20) pour un dispositif (1) d'ajustement variable des instants d'actionnement de soupapes (110, 111) de renouvellement de gaz d'un moteur à combustion interne (100), qui présente
    un boîtier de soupape (22) configuré essentiellement en cylindre creux,
    un piston pilote (30) qui y est disposé à coulissement axial,
    deux raccordements de travail (A, B), à savoir un premier raccordement d'alimentation (P) et un deuxième raccordement d'alimentation (T) étant formés sur le boîtier de soupape (22),
    du fluide sous pression étant apporté par une pompe à fluide sous pression à la soupape pilote (20) par le premier raccordement d'alimentation (P) et du fluide sous pression pouvant être évacué de la soupape pilote (20) jusque dans un réservoir par l'autre raccordement d'alimentation (T),
    les deux raccordements de travail (A, B) et le premier raccordement d'alimentation (P) étant formés par au moins une ouverture radiale (23a, 23b, 23c) formée dans la surface d'enveloppe extérieure du boîtier de soupape (22),
    les raccordements de travail (A, B) et le premier raccordement d'alimentation (P) étant disposés à distance mutuelle dans la direction axiale, le premier raccordement d'alimentation (P) communiquant avec un conduit d'alimentation (27),
    les raccordements de travail (A, B) étant directement voisins dans la direction axiale et le premier raccordement d'alimentation (P) se raccordant dans la direction axiale aux raccordements de travail (A, B) sur le côté du conduit d'alimentation (27),
    au moins deux canaux (40, 41) de fluide sous pression s'étendant axialement et délimités l'un par rapport à l'autre étant formés sur le piston pilote (30),
    chacun des canaux (40, 41) de fluide sous pression communiquant avec l'un des raccordements d'alimentation (P, T) dans une position respective du piston pilote (30),
    chacun des canaux (40, 41) de fluide sous pression pouvant être relié à au moins l'un des raccordements de travail (A, B) par un positionnement approprié du piston pilote (30) par rapport au boîtier de soupape (22),
    au moins l'un des canaux (40, 41) de fluide sous pression n'étant pas symétrique en rotation par rapport à l'axe longitudinal (36) de la soupape pilote (20), caractérisée en ce que
    chacun des canaux (40, 41) de fluide sous pression peut être relié à chacun des raccordements de travail (A, B) par un positionnement approprié du piston pilote (30) par rapport au boîtier de soupape (22).
  2. Soupape pilote (20) selon la revendication 1, caractérisée en ce que les raccordements de travail (A, B) sont directement voisins l'un de l'autre dans la direction axiale.
  3. Soupape pilote (20) selon la revendication 1, caractérisée en ce qu'exactement deux raccordements de travail (A, B) sont formés sur le boîtier de soupape (22).
  4. Soupape pilote (20) selon la revendication 1, caractérisée en ce qu'exactement deux raccordements d'alimentation (24) sont formés sur le boîtier de soupape (22).
  5. Soupape pilote (20) selon la revendication 1, caractérisée en ce que l'un des raccordements d'alimentation (24) est configuré comme raccordement d'amenée (P) par lequel du fluide sous pression est apporté à la soupape pilote (20).
  6. Soupape pilote (20) selon la revendication 1, caractérisée en ce que l'un des raccordements d'alimentation (24) est configuré comme raccordement d'évacuation (T) par lequel du fluide sous pression provenant de la soupape pilote (20) peut être évacué dans un réservoir.
  7. Soupape pilote (20) selon la revendication 1, caractérisée en ce que tous les canaux (40, 41) de fluide sous pression sont formés à l'intérieur du piston pilote (30).
  8. Soupape pilote (20) selon la revendication 7, caractérisée en ce qu'une paroi (42) qui sépare l'un de l'autre les canaux (40, 41) de fluide sous pression est configurée d'un seul tenant avec le piston pilote (30).
  9. Soupape pilote (20) selon la revendication 7, caractérisée en en ce que le piston pilote (30) est configuré comme composant essentiellement en cylindre creux à l'intérieur duquel est prévu un composant d'insertion (44) fabriqué séparément, le composant d'insertion (44) formant en coopération avec une surface d'enveloppe intérieure du piston pilote (30) les canaux (40, 41) de fluide sous pression.
  10. Soupape pilote (20) selon la revendication 1, caractérisée en ce qu'au moins un canal (40, 41) de fluide sous pression est formé sur une surface d'enveloppe extérieure du piston pilote (30).
  11. Soupape pilote (20) selon la revendication 1, caractérisée en ce que le piston pilote (30) est constitué d'un métal et est fabriqué par un procédé métallurgique de moulage par injection.
  12. Soupape pilote (20) selon la revendication 1, caractérisée en ce que le piston pilote (30) est constitué d'une matière synthétique et est fabriquée par un procédé de moulage par injection.
  13. Soupape pilote (20) selon la revendication 1, caractérisée en ce qu'au moins une partie du conduit d'alimentation (27) est configurée comme espace annulaire (38a) entre le boîtier de soupape (22) et la structure environnante (3).
  14. Soupape pilote (20) selon la revendication 1, caractérisée en ce qu'au moins une partie du conduit d'alimentation (27) est configurée comme rainure (38b) débouchant dans le premier raccordement d'alimentation (24) et prévue sur la surface d'enveloppe extérieure du piston pilote (30).
EP20060762977 2005-09-01 2006-08-04 Soupape de distribution destinee a un dispositif pour modifier les temps de distribution d'un moteur a combustion Expired - Fee Related EP1924759B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510041393 DE102005041393A1 (de) 2005-09-01 2005-09-01 Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
PCT/EP2006/007710 WO2007025630A1 (fr) 2005-09-01 2006-08-04 Soupape de distribution destinee a un dispositif pour modifier les temps de distribution d'un moteur a combustion

Publications (2)

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EP1924759A1 EP1924759A1 (fr) 2008-05-28
EP1924759B1 true EP1924759B1 (fr) 2011-02-23

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US (1) US7849825B2 (fr)
EP (1) EP1924759B1 (fr)
KR (1) KR101292391B1 (fr)
CN (1) CN101253312B (fr)
DE (2) DE102005041393A1 (fr)
WO (1) WO2007025630A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014209179A1 (de) * 2014-03-20 2015-09-24 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller, Verwendung sowie Verfahren zur Montage eines zumindest zweiteiligen Rotors eines hydraulischen Nockenwellenverstellers

Families Citing this family (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006031595A1 (de) * 2006-07-08 2008-02-21 Schaeffler Kg Hydraulisches Spannsystem
WO2009010332A1 (fr) * 2007-07-18 2009-01-22 Schaeffler Kg Élément d'une soupape de commande hydraulique
DE102008004591A1 (de) * 2008-01-16 2009-07-23 Schaeffler Kg Hydraulisches Steuerventil mit integriertem Rückschlagventil
ATE512285T1 (de) 2008-06-19 2011-06-15 Hydraulik Ring Gmbh Ventil zum verschwenken einer nockenwelle
DE102009031934A1 (de) * 2009-07-07 2011-01-13 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102009043777A1 (de) * 2009-09-30 2011-03-31 Schaeffler Technologies Gmbh & Co. Kg Zentralventil eines Nockenwellenverstellers einer Brennkraftmaschine
DE102009051310A1 (de) * 2009-10-29 2011-05-05 Schaeffler Technologies Gmbh & Co. Kg Befestigungsanordnung eines Nockenwellenverstellers
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
DE102010009401A1 (de) * 2010-02-26 2011-09-01 Schaeffler Technologies Gmbh & Co. Kg Proportionalventil, insbesondere für einen Nockenwellenversteller
DE102010013777A1 (de) 2010-04-03 2011-10-06 Hydraulik-Ring Gmbh Zentralventil
DE202010006605U1 (de) 2010-04-03 2010-11-18 Hydraulik-Ring Gmbh Zentralventil
DE102010019005B4 (de) * 2010-05-03 2017-03-23 Hilite Germany Gmbh Schwenkmotorversteller
DE102010019004B4 (de) 2010-05-03 2014-09-18 Hilite Germany Gmbh Schwenkmotorversteller mit einem Hydraulikventil
DE102010023864B4 (de) 2010-06-15 2018-03-08 Hilite Germany Gmbh Zentralventil für einen Schwenkmotornockenwellenversteller
DE102010044637A1 (de) 2010-09-07 2012-03-08 Hydraulik-Ring Gmbh Zentralventil
DE102010049551A1 (de) * 2010-10-25 2012-04-26 Schaeffler Technologies Gmbh & Co. Kg Steuerventil für einen Nockenwellenversteller
DE102011003053A1 (de) * 2011-01-24 2012-07-26 Schaeffler Technologies Gmbh & 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
DE102013203951A1 (de) * 2012-05-25 2013-11-28 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012210178B4 (de) * 2012-06-18 2016-05-19 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012106096B3 (de) 2012-07-06 2014-05-15 Hilite Germany Gmbh Schwenkmotorversteller mit einem Hydraulikventil
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
DE102012223582A1 (de) 2012-12-18 2014-06-18 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenverstellersystem
DE102014212993A1 (de) * 2014-07-04 2016-01-07 Schaeffler Technologies AG & Co. KG Steuerventilkolben aus Kunststoff
DE102014219990B4 (de) * 2014-09-12 2017-10-05 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102014115687A1 (de) * 2014-10-29 2016-05-04 Robert Bosch Automotive Steering Gmbh Steuerventil
US9976450B2 (en) * 2015-11-10 2018-05-22 Delphi Technologies Ip Limited Camshaft phaser
US10082054B2 (en) * 2015-11-10 2018-09-25 Delphi Technologies Ip Limited Camshaft phaser
KR101689654B1 (ko) 2016-02-05 2016-12-26 현대자동차주식회사 내연기관의 밸브타이밍 조정장치용 제어밸브
DE102017110553A1 (de) * 2017-05-15 2018-11-15 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit einem verbesserten Zentralventil
DE202020104168U1 (de) * 2019-07-25 2020-09-10 ECO Holding 1 GmbH Nockenwellenversteller
CN111535894B (zh) * 2020-04-28 2021-02-19 一汽解放汽车有限公司 一种电控液压式气门系统及发动机
US11753970B2 (en) 2021-09-03 2023-09-12 Borgwarner Inc. Hydraulically-actuated VCT system including a spool valve

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59206920D1 (de) * 1992-05-19 1996-09-19 New Sulzer Diesel Ag Vorrichtung zum Steuern des Durchflusses eines hydraulischen Druckmittels, insbesondere für die Brennstoffeinspritzung einer Hubkolbenbrennkraftmaschine
DE19756016A1 (de) * 1997-12-17 1999-06-24 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
DE19809175A1 (de) * 1998-03-04 1999-09-09 Schaeffler Waelzlager Ohg Brennkraftmaschine mit Magnetventileinrichtung
SK16982000A3 (sk) * 1998-05-12 2001-04-09 Trochocentric International Ag Prestavovacie zariadenie na prestavenie fázovej polohy hriadeľa
DE19905646A1 (de) * 1999-02-11 2000-08-17 Schaeffler Waelzlager Ohg Nockenwellenstellvorrichtung und Steuerventil mit Leckageausgleich
DE19944535C1 (de) 1999-09-17 2001-01-04 Daimler Chrysler Ag Nockenwellenversteller für Brennkraftmaschinen
DE10215939C1 (de) * 2002-04-11 2003-08-21 Ina Schaeffler Kg Elektromagnetisches Hydtaulikventil, insbesondere Proportionalventil zur Steuerung einer Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine, sowie Verfahren zu dessen Herstellung
GB0303571D0 (en) 2003-02-17 2003-03-19 Delphi Tech Inc Oil flow control valve for a cam phaser
US6871621B2 (en) * 2003-05-12 2005-03-29 Hydraulik-Ring Gmbh Camshaft adjuster for internal combustion engines of motor vehicles
DE102004035035B4 (de) 2003-07-24 2022-04-14 Daimler Ag Nockenwellenversteller für Brennkraftmaschinen
DE10346443A1 (de) * 2003-10-07 2005-05-04 Daimler Chrysler Ag Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine
DE102004038252A1 (de) 2004-05-14 2005-12-15 Ina-Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014209179A1 (de) * 2014-03-20 2015-09-24 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller, Verwendung sowie Verfahren zur Montage eines zumindest zweiteiligen Rotors eines hydraulischen Nockenwellenverstellers

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CN101253312A (zh) 2008-08-27
US7849825B2 (en) 2010-12-14
WO2007025630A1 (fr) 2007-03-08
CN101253312B (zh) 2012-05-09
US20080236529A1 (en) 2008-10-02
EP1924759A1 (fr) 2008-05-28

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