EP2452052B1 - Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne - Google Patents

Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne Download PDF

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Publication number
EP2452052B1
EP2452052B1 EP20100724489 EP10724489A EP2452052B1 EP 2452052 B1 EP2452052 B1 EP 2452052B1 EP 20100724489 EP20100724489 EP 20100724489 EP 10724489 A EP10724489 A EP 10724489A EP 2452052 B1 EP2452052 B1 EP 2452052B1
Authority
EP
European Patent Office
Prior art keywords
valve housing
valve
receptacle
control piston
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.)
Not-in-force
Application number
EP20100724489
Other languages
German (de)
English (en)
Other versions
EP2452052A1 (fr
Inventor
Jens Hoppe
Ali Bayrakdar
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2452052A1 publication Critical patent/EP2452052A1/fr
Application granted granted Critical
Publication of EP2452052B1 publication Critical patent/EP2452052B1/fr
Not-in-force 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
    • 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, wherein the control piston within the valve housing is arranged axially displaceable, wherein the pressure medium flows can be controlled to and from the camshaft adjuster by appropriate positioning of the control piston within the valve housing, wherein the mounting flange is fixedly connected to a wall of the receptacle and determines the axial position of the valve housing relative to the camshaft adjuster.
  • camshaft adjusters are used to control the phase relation between crankshaft and camshaft in a defined manner Angle range, between a maximum early and a maximum late position, to make variable.
  • the camshaft adjuster is integrated into a drive train via which torque is transmitted from the crankshaft to the camshaft.
  • This drive train 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.
  • 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 for example from the DE 10 2004 038 160 A1 known.
  • 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, a discharge connection and two working connections on its outer lateral 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 at the open end of the Valve housing is arranged.
  • the second end stop is realized by the spring receiver.
  • the pressure medium volume flow delivered by the pressure medium pump to the inlet connection is conducted to the first or second working connection and thus to the first or the second pressure chambers.
  • the pressure medium is expelled from the other pressure chambers via the other working connection and one of the outflow connections into 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 manufacturing process is very time-consuming and results in a high material usage.
  • the invention has for its object to provide a central valve of a camshaft adjuster an internal combustion engine, the production cost is to be reduced.
  • the object is achieved in that the mounting flange and the valve housing are formed as two separate components and that the valve housing is positively, materially or non-positively connected to the mounting flange.
  • 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 centric 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 working port, wherein the valve housing with the wall of the receptacle cooperates such that the ports outside the valve housing are hydraulically separated from each other.
  • the receptacle is located in the overlapped area of the camshaft adjuster and may 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 mounting flange can be positively, materially or non-positively, for example by means of a welding, soldering, adhesive or screw, by means of a press fit or caulking firmly connected to the wall of the recording. 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 can be made by means of inexpensive and fast process. 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.
  • Conceivable for example, extrusion molding or the like.
  • 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 anschlie ⁇ end the mounting flange firmly connected to the wall of the receptacle.
  • the valve housing by means of the mounting flange against the recording pressed, whereby its axial position is fixed within the receptacle.
  • the mounting flange has a collar which is arranged outside of the camshaft adjuster and rests 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 of the camshaft or the camshaft adjuster can be 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, the end stops can be formed during their manufacturing process 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 an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, with 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.
  • it may be provided to equip only one of the camshafts 6, 7 with a camshaft adjuster 11, or provide only a camshaft 6, 7, which with a camshaft adjuster 11 is provided.
  • FIG. 3 shows a fixed to a camshaft 6, 7 camshaft adjuster 11 in longitudinal section, as in the DE 10 2004 038 160 A1 disclosed.
  • Figure 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.
  • the side covers 14 are rotatably connected to the drive element 12.
  • five projections 20 extend radially inwardly.
  • the projections 20 are formed integrally with the peripheral wall 19.
  • the drive element 12 is arranged by means of radially inner circumferential walls of the projections 20 relative to the output member 13 rotatable thereto.
  • the output member 13 is in the form of an impeller and has a substantially cylindrical hub member 17, of which outer cylindrical surface extend in the illustrated embodiment, five wings 18 in the radial direction outwards.
  • 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 this is positively connected to the output element 13.
  • 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.
  • a pressure chamber 23 is formed between each two circumferentially adjacent projections 20.
  • 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 element 13 is arranged rotatably in a defined Winkelbreich 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 on the cylindrical lateral surface of an inlet port P, a drain port T and two working ports A, B, in the form of annular grooves 47 which communicate by means of radial openings 48 with the interior of the valve housing 31 are formed.
  • 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. It works on the control piston 32 on the one hand a push rod, not shown, of the actuator 35 and on the other hand a spring element 38, which is supported on a spring receptacle 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 in the FIG. 3 is prevented 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 in the FIG. 3 is prevented 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 31st Due to the axial bearing and the fastening 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.
  • FIG. 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 in a Mounting flange 42 integrated.
  • the mounting flange 42 must have a high strength and be formed, for example, as a rotating part.
  • 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.
  • 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 means between the inside and the outer space of the tubular sheet metal component can be exchanged.
  • 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 in the illustrated embodiment as a plastic sleeve formed 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.
  • the adapter sleeve 44 On the outer circumferential surface of the adapter sleeve 44 four axially offset annular grooves 47 are formed in the groove bottom openings 48 are provided.
  • the openings 48 are aligned with the housing openings 46, so that pressure medium between the interior and the exterior of the valve housing 31 can be replaced.
  • 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 by the adapter sleeve 44 is sprayed onto the tubular member or a separately manufactured adapter sleeve 44 is attached to the tubular member and / or the mounting flange 42. For mounting the central valve 30 in the receptacle 29 this is screwed by means of the threaded portion 41 in the camshaft 6, 7. The valve housing 31 comes into abutment against a stop 49 (FIG. FIG. 3 ) formed in the camshaft 6, 7.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (10)

  1. Soupape centrale (30) d'un déphaseur d'arbre à cames (11) d'un moteur à combustion interne (1), comprenant un boîtier de soupape (31), un piston de soupape (32) et une bride de fixation (42),
    - le boîtier de soupape (31) étant disposé au moins partiellement à l'intérieur d'un logement (29) à l'intérieur du déphaseur d'arbre à cames (11) et comprenant au moins un raccord d'alimentation (P), un raccord d'évacuation (T) et un raccord de travail (A, B),
    - le piston de commande (32) étant disposé de manière axialement déplaçable à l'intérieur du boîtier de soupape (31),
    - les flux de fluide sous pression vers et à partir du déphaseur d'arbre à cames (11) pouvant être commandés par un positionnement approprié du piston de commande (32) à l'intérieur du boîtier de soupape (31),
    - la bride de fixation (42) étant reliée fixement à une paroi du logement (29) et déterminant la position axiale du boîtier de soupape (31) par rapport au déphaseur d'arbre à cames (11),
    - caractérisée en ce que la bride de fixation (42) et le boîtier de soupape (31) sont réalisés sous forme de deux composants séparés et le boîtier de soupape (31) est relié à la bride de fixation (42) par engagement par coopération de formes, par liaison de matière ou par engagement par force.
  2. Soupape centrale (30) selon la revendication 1, caractérisée en ce que le boîtier de soupape (31) s'applique d'une part contre une butée (49) du logement (29) et d'autre part contre la bride de fixation (42).
  3. Soupape centrale (30) selon la revendication 1, caractérisée en ce que la bride de fixation (42) comprend un collet (40) qui est disposé à l'extérieur du déphaseur d'arbre à cames (11) et s'applique dans au moins une direction axiale contre un composant (16) fixé à une culasse du moteur à combustion interne (1).
  4. Soupape centrale (30) selon la revendication 1, caractérisée en ce que le boîtier de soupape (31) est réalisé sous forme de composant en tôle essentiellement tubulaire.
  5. Soupape centrale (30) selon la revendication 4, caractérisée en ce que le composant en tôle tubulaire est pourvu d'un manchon adaptateur (44) qui entoure le composant tubulaire et dont la surface d'enveloppe extérieure s'applique contre une paroi du logement (29).
  6. Soupape centrale (30) selon la revendication 5, caractérisée en ce que le manchon adaptateur (44) est relié fixement à la bride de fixation (42) ou au composant en tôle tubulaire.
  7. Soupape centrale (30) selon la revendication 4, caractérisée en ce qu'un tissu filtrant (45) est disposé entre le composant en tôle tubulaire et le manchon adaptateur (44) dans la région d'au moins l'un des raccords (A, B, P, T).
  8. Soupape centrale (30) selon la revendication 1, caractérisée en ce qu'une butée de fin de course (36) pour le piston de commande (32) est réalisée sur la bride de fixation (42).
  9. Soupape centrale (30) selon la revendication 1, caractérisée en ce qu'une butée de fin de course (37) pour le piston de commande (32) est réalisée sur le boîtier de soupape (31).
  10. Soupape centrale (30) selon la revendication 1, caractérisée en ce qu'un logement de ressort (39) pour un élément ressort (38), lequel s'appuie contre le piston de commande (32) et le logement de ressort (39), est réalisé sur le boîtier de soupape (31).
EP20100724489 2009-07-04 2010-06-04 Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne Not-in-force EP2452052B1 (fr)

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 (fr) 2009-07-04 2010-06-04 Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne

Publications (2)

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EP2452052A1 EP2452052A1 (fr) 2012-05-16
EP2452052B1 true EP2452052B1 (fr) 2014-04-23

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EP20100724489 Not-in-force EP2452052B1 (fr) 2009-07-04 2010-06-04 Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne

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US (1) US8893676B2 (fr)
EP (1) EP2452052B1 (fr)
KR (1) KR20120032510A (fr)
CN (1) CN102472127B (fr)
DE (1) DE102009031701A1 (fr)
WO (1) WO2011003682A1 (fr)

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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
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Also Published As

Publication number Publication date
EP2452052A1 (fr) 2012-05-16
CN102472127A (zh) 2012-05-23
KR20120032510A (ko) 2012-04-05
CN102472127B (zh) 2014-11-19
WO2011003682A1 (fr) 2011-01-13
US8893676B2 (en) 2014-11-25
US20120111296A1 (en) 2012-05-10
DE102009031701A1 (de) 2011-01-05

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