EP2452052A1 - Zentralventil eines nockenwellenverstellers einer brennkraftmaschine - Google Patents
Zentralventil eines nockenwellenverstellers einer brennkraftmaschineInfo
- Publication number
- EP2452052A1 EP2452052A1 EP10724489A EP10724489A EP2452052A1 EP 2452052 A1 EP2452052 A1 EP 2452052A1 EP 10724489 A EP10724489 A EP 10724489A EP 10724489 A EP10724489 A EP 10724489A EP 2452052 A1 EP2452052 A1 EP 2452052A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve housing
- valve
- mounting flange
- receptacle
- camshaft adjuster
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
-
- 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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0475—Hollow camshafts
-
- 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
- F01L2001/34433—Location oil control valves
-
- 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
- Y10T137/86574—Supply and exhaust
- Y10T137/8667—Reciprocating valve
- Y10T137/86694—Piston valve
- Y10T137/86702—With internal flow passage
Definitions
- the invention relates to a central valve of a camshaft adjuster of an internal combustion engine with a valve housing, a control piston and a mounting flange, wherein the valve housing is at least partially disposed within a receptacle within the camshaft adjuster and at least one inlet port, a drain port and a working port has, wherein the control piston within the pressure medium flows to and from the camshaft adjuster can be controlled by suitable positioning of the control piston within the valve housing, wherein the mounting flange is fixedly connected to a wall of the receptacle and the axial position of the valve housing relative to the camshaft adjuster sets.
- camshaft adjusters are used in order to make the phase relation between crankshaft and camshaft variable within a defined angular range, between a maximum early and a maximum late position.
- the camshaft adjuster is integrated into a drive train via which torque is transmitted from the crankshaft to the camshaft.
- This drive rod can be realized for example as a belt, chain or gear drive.
- Such camshaft adjusters are generally designed as hydraulic swivel motors, for example in vane-type construction, with at least two counteracting pressure chambers. In doing so, the pressure medium supply to or the pressure medium discharge from the pressure chambers by means of a hydraulic directional control valve, for example a proportional valve controlled.
- a hydraulic directional control valve for example a proportional valve controlled.
- embodiments are known in which the hydraulic directional control valve is arranged in a central passage opening of the camshaft adjuster and rotates therewith. Such directional valves are commonly referred to as the central valve.
- Such a central valve is known for example from DE 10 2004 038 160 A1.
- a central passage opening of the camshaft adjuster is penetrated by a hollow camshaft.
- the central valve is arranged in the region of the camshaft adjuster.
- the central valve consists of a valve body, a control piston, a spring element and a snap ring.
- the substantially hollow cylindrical valve housing has an inlet connection, an outlet connection and two working connections on its outer jacket surface. Furthermore, an axial working connection is provided.
- the inlet port communicates with a pressure medium pump of the internal combustion engine
- the drain ports communicate with a pressure medium reservoir
- the working ports each communicate with a group of pressure chambers of the camshaft phaser.
- control piston Within the valve housing, the control piston is arranged axially displaceable.
- control piston by means of an electromagnetic actuator against the force of the spring element, which is supported on the control piston and the valve housing, moved to any position between two end stops and held there.
- the first end stop is realized by the snap ring, which is arranged at the open end of the valve housing.
- the second end stop is realized by the spring receiver.
- the pressure medium volume flow conveyed from the pressure medium pump to the inlet connection is conducted to the first or second working port and thus to the first or the second pressure chambers.
- the pressure medium from the other pressure chambers is Final and expelled one of the drain ports in the pressure medium reservoir.
- the valve housing has, in addition to the hydraulic connections, a fastening section, in the illustrated embodiment a threaded section, by means of which the central valve is fixed within the camshaft.
- a radially extending collar is formed, which projects beyond the camshaft in the radial direction and rests in the axial direction on a cylinder head of the internal combustion engine.
- the collar forms part of the axial bearing of the camshaft relative to the cylinder head.
- valve body is made by means of cutting manufacturing process of a metal blank. This production process is very time-consuming and results in a high use of materials.
- the invention has for its object to provide a central valve of a camshaft lenverstellers an internal combustion engine, the production cost is to be reduced.
- the object is achieved according to the invention in that the fastening flange and the valve housing are designed as two separate components.
- the central valve has at least one valve housing, a control piston and a mounting flange.
- the valve housing is at least partially disposed within a receptacle within the camshaft adjuster, for example, a central passage opening of the camshaft adjuster.
- the valve housing which may be formed, for example, substantially hollow cylindrical, has at least one inlet port, a drain port and a a drain port and a working port, wherein the valve housing cooperates with the wall of the receptacle such that the ports outside the valve housing are hydraulically separated from each other.
- the receptacle is located in the region which is engaged by the camshaft adjuster and can be formed directly on the camshaft adjuster or an intermediate component which is arranged between the camshaft adjuster and the valve housing.
- the camshaft adjuster can be penetrated by a camshaft which has a receptacle in the region of the camshaft adjuster in which the valve housing is arranged.
- the control piston is received axially displaceable. This can be positioned for example by means of an electromagnetic actuator between two end stops.
- the pressure medium supplied to the central valve is directed either to the first or the second pressure chambers of the camshaft adjuster, wherein pressure medium from the other pressure chambers is simultaneously directed to a pressure medium reservoir.
- the mounting flange which is non-rotatably and immovably connected in the axial direction with a wall of the receptacle, the axial position of the valve housing is set within the receptacle.
- the fastening flange can be connected to the wall of the receptacle in a positive, material or non-positive manner, for example by means of a welding, soldering, adhesive or screw connection, by means of an interference fit or caulking. Due to the separate design of the mounting flange of the loaded during operation of the internal combustion engine region of the central valve of the otherwise unloaded valve housing, which serves only to control the pressure medium flows to and from the camshaft adjuster is separated. Thus, only the loaded mounting flange must be solid, while the valve body by means of inexpensive and faster method can be produced.
- Conceivable for example, valve housing, which are formed as a sheet metal component and, for example, by means of a chipless forming process, for example a deep-drawing process, are made.
- the separation of the mounting flange from the valve housing reduces the complexity of the solid mounting flange, so that it can be manufactured by means of simpler manufacturing processes than the valve housing known from the prior art.
- Conceivable for example, extrusion molding or the like.
- the production of the central valve, in particular of the valve housing and the fastening component is simplified considerably and their production costs are reduced.
- the use of materials decreases.
- valve housing is positively, materially or non-positively connected to the mounting flange.
- the valve housing may, for example, be connected to the mounting flange by means of a welding, soldering, adhesive or screw connection, by means of an interference fit or caulking.
- an assembly can be prefabricated, which can be installed as a whole.
- valve housing on the one hand abut against a stop of the receptacle and on the other hand on the mounting flange.
- first the valve housing is inserted into the receptacle and then the mounting flange firmly connected to the wall of the receptacle.
- the valve housing is pressed by means of the mounting flange against the receptacle, whereby its axial position is fixed within the receptacle.
- the mounting flange has a collar which is arranged outside of the camshaft adjuster and abuts in at least one axial direction on a cylinder head fixed component of the internal combustion engine.
- the cylinder-head-resistant component can be, for example, the cylinder head, the cylinder head cover or a component fixedly connected to the cylinder head.
- the thrust bearing function is the Camshaft or the camshaft adjuster integrated into the central valve according to the invention.
- the valve housing may be formed as a substantially tubular sheet-metal component.
- the sheet metal component may come to rest directly on the wall of the receptacle, so that the hydraulic connections of the valve housing outside the valve housing are hydraulically separated from each other.
- the tubular sheet-metal component may be surrounded by an adapter sleeve, for example a plastic sleeve, whose outer circumferential surface bears against a wall of the receptacle.
- the valve housing is formed by the tubular member and the adapter sleeve.
- the adapter sleeve may be fixedly connected to the mounting flange or the tubular sheet metal component or both. This can be realized for example by means of an adhesive connection, a clip or flare connection.
- the tubular sheet metal component serves as a bearing and sliding surface for the control piston.
- the wall thickness of the tubular component can be made small and the distance to the wall of the receptacle can be bridged by means of a lightweight plastic sleeve. This reduces the weight of the valve housing rotating with the camshaft adjuster. In addition, its ease of manufacture is facilitated by the small wall thickness of the tubular component.
- the adapter sleeve may be fixedly connected to the mounting flange or the tubular sheet metal component or both.
- a filter fabric can be arranged in the region of at least one of the connections between the tubular sheet-metal component and the adapter sleeve.
- an end stop for the control piston is formed on the mounting flange and / or on the valve housing. Due to the lower complexity of the mounting flange and the valve housing, during their manufacturing procedure, the end stops are formed without additional effort. Thus, no additional components are required that fulfill this function.
- a spring receptacle for a spring element which is supported on the control piston and the spring receptacle, is formed on the valve housing.
- the spring receptacle is formed on the valve housing, for example the tubular sheet-metal component or the adapter sleeve.
- FIG. 1 shows very schematically an internal combustion engine
- FIG. 2 shows a longitudinal section through a central valve according to the invention
- Figure 3 is a longitudinal section through one attached to a camshaft
- Figure 4 shows a cross section through the device of Figure 3 along the
- crankshaft 2 is in the illustrated embodiment, each with a traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in conjunction, wherein a first and a second camshaft adjuster 11 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
- Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more Auslassgas scaffoldventile 10.
- FIG. 3 shows a longitudinal section of a camshaft adjuster 11 fastened to a camshaft 6, 7, as disclosed in DE 10 2004 038 160 A1.
- FIG. 4 shows a cross section through the camshaft adjuster 11 along the line IV-IV in FIG. 3.
- the camshaft adjuster 11 has a drive element 12 and an output element 13. On the axial side surfaces of the drive element 12, a side cover 14 is arranged in each case. The side covers 14 are rotatably connected to the drive element 12.
- the projections 20 extend radially inwardly.
- the projections 20 are formed integrally with the peripheral wall 19.
- the drive element 12 is arranged rotatably relative to the output element 13 by means of radially inward circumferential walls of the projections 20.
- the output element 13 is designed in the form of an impeller and has a substantially cylindrically designed hub element 17, from whose outer cylindrical lateral surface, in the illustrated embodiment, five vanes 18 extend outwards in the radial direction.
- the vanes 18 are formed separately from the output element 13 and arranged in vane grooves in the outer circumferential surface of the hub member 17.
- a sprocket 21 which is non-rotatably connected to the drive element 12
- torque can be transmitted from the crankshaft 2 to the drive element 12 by means of a chain drive, not shown.
- a central passage opening 22 of the output element 13 is penetrated by the camshaft 6, 7, wherein these are positively connected to the output element 13 is.
- the camshaft 6, 7 is formed in the illustrated embodiment as a hollow shaft and rotatably supported within a camshaft radial bearing 15 of a cylinder head 16. Inside the camshaft adjuster 11, a pressure chamber 23 is formed between two respective projections 20 adjacent in the circumferential direction.
- Each of the pressure chambers 23 is bounded in the circumferential direction by opposing, substantially radially extending boundary walls 24 of adjacent projections 20, in the axial direction of the side covers 14, radially inwardly of the hub member 17 and radially outwardly of the peripheral wall 19.
- In each of the pressure chambers 23 protrudes a wing 18, wherein the wings 18 are formed such that they rest against both the side covers 14, and on the peripheral wall 19.
- Each vane 18 thus divides the respective pressure chamber 23 into two counteracting pressure chambers 25, 26.
- the output member 13 is rotatably arranged in a defined Winkeibreich to the drive element 12.
- the angular range is limited in one direction of rotation of the driven element 13 in that the wings 18 come into contact with a corresponding boundary wall 24 (early stop 27) of the pressure chambers 23.
- the angular range in the other direction of rotation is limited by the fact that the wings 18 come to rest on the other boundary walls 24 of the pressure chambers 23, which serve as a late stop 28.
- phase position of the drive element 12 to the output element 13 (and thus the phase angle of the camshaft 6, 7 to the crankshaft 2) can be varied.
- phase position can be kept constant.
- a central valve 30 is arranged in a receptacle 29 of the camshaft 6.7.
- the central valve 30 has a valve housing 31 and a control piston 32.
- the valve housing 31 is formed substantially hollow cylindrical, wherein an inlet connection P, a drain connection T and two working connections A, B, in the form of annular grooves 47, which communicate with the interior of the valve housing 31 by means of radial openings 48, are formed on its cylindrical lateral surface.
- an axial discharge port T in the form of an axial opening, is provided.
- the inlet port P communicates via a formed in the cylinder head 16 pressure medium channel 33 with a pressure medium pump, not shown.
- the drain connections T communicate with a pressure medium reservoir, also not shown.
- the first working port A communicates with the first pressure chambers 25, the second working port B communicates with the second pressure chambers 26.
- pressure medium passes via the inlet port P in the interior of the valve housing 31 and piston openings 34 in the interior of the control piston 32.
- the pressure medium reaches the first or second working port A, B and thus to the respective pressure chambers 25, 26.
- pressure medium is discharged from the other pressure chambers 25, 26 via the other working port A, B and the respective discharge port T to the pressure medium reservoir.
- the axial position of the control piston 32 can be arbitrarily set by means of an electromagnetic actuator 35 between two end stops 36, 37.
- the first end stop 36 is realized by means of a snap ring, which is arranged on the open side of the valve housing 31.
- a push rod not shown
- a spring element 38 which is supported on a spring seat 39 of the valve housing 31, which forms the second end stop 37 at the same time.
- the valve housing 31 is non-rotatably and immovably mounted in the camshaft 6, 7.
- a threaded portion 41 is formed on the valve housing 31, by means of which it is screwed to the camshaft 6, 7.
- the valve housing 31 has, at its end protruding from the camshaft 6, 7, a collar 40 extending in the radial direction.
- the Collar 40 is in the axial direction of the cylinder head 16, so that an axial movement of the camshaft 6, 7 is prevented in the figure 3 to the right.
- the output member 13 is also applied to the cylinder head 16, so that an axial movement of the camshaft 6, 7 is prevented in the figure 3 to the left.
- the collar 40 forms part of the axial bearing of the camshaft 6, 7 in the cylinder head 16.
- valve housing 31 assumes the function of the pressure medium distribution to the pressure chambers 25, 26 and the axial bearing of the camshaft 6, 7.
- attachment of the central valve 30 within the receptacle 29 also takes place via the valve housing 31.
- the valve housing 31 Due to the Axiallager- and the attachment function, the valve housing 31 is formed with an increased strength. Usually this is made by cutting, for example by turning, from a solid metal blank. Due to the collar 40 and the threaded portion 41, much material must be removed from the blank during the manufacture of the valve housing 31, resulting in high material costs and low cycle times.
- Figure 2 shows an example of an embodiment of a central valve 30 according to the invention, which does not have these disadvantages.
- the thrust bearing and mounting functionalities are separated from the valve housing 31 and integrated into a mounting flange 42.
- the mounting flange 42 must have a high strength and be formed, for example, as a rotating part.
- metal-coated metal injection-molded, sintered, deep-drawn or extruded parts are, for example, metal-coated metal injection-molded, sintered, deep-drawn or extruded parts.
- the fastening flange 42 has the collar 40 required for axial bearing of the camshaft 6, 7 and a fastening section 43.
- the fixing portion 43 By means of the fixing portion 43, the fixed connection between the camshaft 6, 7 and the central valve 30 is made.
- a threaded portion 41 is formed on the attachment portion 43.
- Final elements or a surface by means of which a press fit with the camshaft 6, 7 can be realized.
- the valve housing 31 is formed as a tubular sheet metal part, wherein the cylindrical surface has four groups of housing openings 46, via the pressure medium between the interior and the outer space of the tubular sheet metal component can be replaced.
- the housing openings 46 of a group are circumferentially spaced from each other formed on the tubular member.
- the groups are arranged axially offset from one another.
- Each group of housing openings 46 forms one of the radial pressure medium connections A, B, P, T.
- valve housing 31 is inserted into the mounting flange 42 and frictionally, by means of a press fit, connected thereto.
- positive or cohesive connection methods such as screw, caulking, welding, solder or adhesive connections.
- the valve housing 31 has on the outer lateral surface of the tubular sheet-metal component is an adapter sleeve 44 which abuts in the assembled state of the central valve 30 pressure-medium-tight against the wall of the receptacle 29.
- the adapter sleeve 44 is formed in the illustrated embodiment as Kunststoffhül- se and fixedly connected both to the valve housing 31 and with the mounting flange 42.
- the adapter sleeve 44 may for example be sprayed directly onto the valve housing 31 or manufactured separately and attached to the valve housing 31 by means of an adhesive bond.
- the connection to the mounting flange 42 is realized by means of a flanging in the region of the threaded portion 41 of the mounting flange 42. Also conceivable are locking or clip connections.
- a filter element 45 is provided in the form of a filter fabric, which extends in the axial direction along the radial working ports A, B, P, T and prevents the entry of dirt particles into the valve housing 31.
- control piston 32 and the spring element 38 is arranged within the valve housing 31.
- the control piston 32 is arranged axially displaceable between the formed on the mounting flange 42 first end stop 36 and formed by the spring receptacle 39 second end stop 37.
- the spring element 38 is supported on the one hand on the spring bearing 39 and on the other hand on the control piston 32 from.
- the tubular component is first firmly connected to the mounting flange 42 and the control piston 32 and the spring element 38 are positioned within the valve housing 31. Subsequently, the valve housing 31 is completed in that the adapter sleeve 44 is sprayed onto the tubular component or a separately manufactured adapter sleeve 44 is fastened to the tubular component and / or the fastening flange 42.
- the central valve 30 in the receptacle 29 this is screwed by means of the threaded portion 41 in the camshaft 6, 7. In this case, the valve housing 31 comes into abutment against a stop 49 ( Figure 3), which is formed in the camshaft 6, 7.
- embodiments are also conceivable in which the central valve 30 is connected directly to the central passage opening 22 of the output element 13 by means of the attachment section 43.
- the camshaft 6, 7 does not pass through the central through-opening 22 at least completely and the attachment portion 43 is located directly on the wall of the central passage opening 22, which serves as a receptacle 29 in this case.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009031701A DE102009031701A1 (de) | 2009-07-04 | 2009-07-04 | Zentralventil eines Nockenwellenverstellers einer Brennkraftmaschine |
PCT/EP2010/057819 WO2011003682A1 (de) | 2009-07-04 | 2010-06-04 | Zentralventil eines nockenwellenverstellers einer brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2452052A1 true EP2452052A1 (de) | 2012-05-16 |
EP2452052B1 EP2452052B1 (de) | 2014-04-23 |
Family
ID=42556490
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20100724489 Not-in-force EP2452052B1 (de) | 2009-07-04 | 2010-06-04 | Zentralventil eines nockenwellenverstellers einer brennkraftmaschine |
Country Status (6)
Country | Link |
---|---|
US (1) | US8893676B2 (de) |
EP (1) | EP2452052B1 (de) |
KR (1) | KR20120032510A (de) |
CN (1) | CN102472127B (de) |
DE (1) | DE102009031701A1 (de) |
WO (1) | WO2011003682A1 (de) |
Families Citing this family (19)
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DE102010050812A1 (de) | 2010-11-09 | 2012-05-10 | Schaeffler Technologies Gmbh & Co. Kg | Ventilgehäuse für ein Steuerventil eines Nockenwellenverstellsystems, sowie Verfahren zur Herstellung eines Ventilgehäuses |
DE102012202520B4 (de) | 2012-02-20 | 2016-03-24 | Schaeffler Technologies AG & Co. KG | Zentralventil für einen Nockenwellenversteller |
WO2013174563A1 (de) * | 2012-05-25 | 2013-11-28 | Schaeffler Technologies AG & Co. KG | Steuerventil eines nockenwellenverstellers |
DE102012208809B4 (de) * | 2012-05-25 | 2020-11-26 | Schaeffler Technologies AG & Co. KG | Steuerventil eines Nockenwellenverstellers |
US8978493B2 (en) * | 2012-07-27 | 2015-03-17 | Westinghouse Electric Company Llc | Conduit length adjustment apparatus and method |
DE102012220830B4 (de) * | 2012-11-15 | 2018-01-18 | Schaeffler Technologies AG & Co. KG | Steuerventil für eine hydraulische Vorrichtung mit einer austauschbaren Hydraulikeinheit |
DE102012221720A1 (de) * | 2012-11-28 | 2014-06-18 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenverstelleinrichtung und Zentralventil für eine Nockenwellenverstelleinrichtung |
DE102013209930B4 (de) * | 2013-05-28 | 2016-01-28 | Schaeffler Technologies AG & Co. KG | Nockenwellenverstelleinrichtung |
DE102013220739A1 (de) * | 2013-10-14 | 2015-04-16 | Continental Automotive Gmbh | Druckregler |
DE102013221218A1 (de) * | 2013-10-18 | 2015-04-23 | Robert Bosch Gmbh | Schieberventil, insbesondere für ein Automatikgetriebe eines Kraftfahrzeugs |
DE102015200542B4 (de) * | 2015-01-15 | 2020-10-22 | Schaeffler Technologies AG & Co. KG | Zentralventil für eine Nockenwellenverstellvorrichtung |
DE102015213135B3 (de) * | 2015-07-14 | 2017-01-05 | Schaeffler Technologies AG & Co. KG | Steuerventil für einen Nockenwellenversteller |
DE102016209108A1 (de) * | 2015-12-02 | 2017-06-08 | Continental Teves Ag & Co. Ohg | Bremsdrucksteuergerät |
KR101679020B1 (ko) | 2015-12-23 | 2016-12-29 | 현대자동차주식회사 | 내연기관의 밸브타이밍 조정장치의 잠금구조 |
KR101679016B1 (ko) | 2015-12-23 | 2017-01-02 | 현대자동차주식회사 | 내연기관의 밸브타이밍 조정장치 |
KR101767463B1 (ko) | 2016-01-06 | 2017-08-14 | 현대자동차(주) | 내연기관의 밸브타이밍 조정장치의 오일 드레인 구조 |
KR101689654B1 (ko) | 2016-02-05 | 2016-12-26 | 현대자동차주식회사 | 내연기관의 밸브타이밍 조정장치용 제어밸브 |
FR3083569B1 (fr) * | 2018-07-04 | 2020-11-27 | Delphi Automotive Systems Lux | Dispositif de commande d'un dephaseur d'arbre a cames |
US11261765B1 (en) * | 2020-08-25 | 2022-03-01 | Borgwamer Inc. | Control valve assembly of a variable cam timing phaser |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19848706A1 (de) * | 1998-10-22 | 2000-04-27 | Schaeffler Waelzlager Ohg | Vorrichtung zur Relativverdrehung einer Nockenwelle gegenüber einer diese Nockenwelle antreibenden Kurbelwelle einer Brennkraftmaschine |
US6382148B1 (en) * | 1999-06-10 | 2002-05-07 | Unisia Jecs Corporation | Oil pressure control apparatus for an internal combustion engine |
DE10346443A1 (de) * | 2003-10-07 | 2005-05-04 | Daimler Chrysler Ag | Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine |
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 |
DE102004038160B4 (de) | 2004-05-14 | 2017-03-23 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
US7013854B1 (en) * | 2005-05-18 | 2006-03-21 | Ina-Schaeffler Kg | Device for the hydraulic adjustment of the angle of rotation of a camshaft in relation to a crankshaft of an internal combustion engine |
DE102005037480A1 (de) * | 2005-08-09 | 2007-02-15 | Schaeffler Kg | Steuerventil und Verfahren zur Herstellung desselben |
-
2009
- 2009-07-04 DE DE102009031701A patent/DE102009031701A1/de not_active Withdrawn
-
2010
- 2010-06-04 CN CN201080030115.5A patent/CN102472127B/zh not_active Expired - Fee Related
- 2010-06-04 US US13/381,185 patent/US8893676B2/en not_active Expired - Fee Related
- 2010-06-04 EP EP20100724489 patent/EP2452052B1/de not_active Not-in-force
- 2010-06-04 KR KR20127000087A patent/KR20120032510A/ko active IP Right Grant
- 2010-06-04 WO PCT/EP2010/057819 patent/WO2011003682A1/de active Application Filing
Non-Patent Citations (1)
Title |
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See references of WO2011003682A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN102472127B (zh) | 2014-11-19 |
EP2452052B1 (de) | 2014-04-23 |
DE102009031701A1 (de) | 2011-01-05 |
KR20120032510A (ko) | 2012-04-05 |
US20120111296A1 (en) | 2012-05-10 |
US8893676B2 (en) | 2014-11-25 |
WO2011003682A1 (de) | 2011-01-13 |
CN102472127A (zh) | 2012-05-23 |
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