EP2690261B1 - Régulateur de phase d'arbre à cames avec douille d'étanchéité - Google Patents

Régulateur de phase d'arbre à cames avec douille d'étanchéité Download PDF

Info

Publication number
EP2690261B1
EP2690261B1 EP13177506.6A EP13177506A EP2690261B1 EP 2690261 B1 EP2690261 B1 EP 2690261B1 EP 13177506 A EP13177506 A EP 13177506A EP 2690261 B1 EP2690261 B1 EP 2690261B1
Authority
EP
European Patent Office
Prior art keywords
sealing
rotor
sealing sleeve
stays
annular gap
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
EP13177506.6A
Other languages
German (de)
English (en)
Other versions
EP2690261A2 (fr
EP2690261A3 (fr
Inventor
Claus Welte
Dr. Uwe Meinig
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schwaebische Huettenwerke Automotive GmbH
Original Assignee
Schwaebische Huettenwerke Automotive GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schwaebische Huettenwerke Automotive GmbH filed Critical Schwaebische Huettenwerke Automotive GmbH
Publication of EP2690261A2 publication Critical patent/EP2690261A2/fr
Publication of EP2690261A3 publication Critical patent/EP2690261A3/fr
Application granted granted Critical
Publication of EP2690261B1 publication Critical patent/EP2690261B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—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
    • F01L2001/34479—Sealing of phaser devices
    • 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

Definitions

  • the invention relates to the sealing of a fluidic phase adjuster for adjusting the rotational angular position of a camshaft relative to a crankshaft of an internal combustion engine.
  • camshaft phasers have become popular for varying intake and exhaust timing. Due to the high reliability, but also in terms of a favorable cost-benefit ratio have hydraulic, operated by the lubricating oil for the internal combustion engine phaser proven by the principle of hydraulic swing motor.
  • the phase adjusters have a stator and a rotor, which can be rotated relative to each other by pressurization of adjusting chambers.
  • the rotor is typically connected in a rotationally fixed manner to the camshaft by means of a fastening structure which extends centrally through the rotor, for example a fastening screw.
  • the adjusting chambers can be acted upon by a pressure between the central fastening structure and the rotor annular gap with the pressurized fluid.
  • the demands on the manufacturing accuracy of the individual components of the phaser must not be set high.
  • Leaks require larger sizing of the engine, typically the engine lubricating oil pump, which supplies the phaser with the pressurized fluid. This is associated with an increase in the installation space, the weight and the power consumption of the supply unit and an increase in costs.
  • the transfer points are problematic at which the pressure fluid for pressurizing the adjusting chambers enters the annular gap and exits for pressure relief.
  • a defined game must prevail between the outer periphery of the mounting structure and the surrounding inner circumference of the rotor to undefined Reibmomente between the components in the Avoid assembly.
  • a more or less large leakage occurs as a function of the viscosity of the pressure fluid and thus in particular of the temperature.
  • a particular problem is the use of rotors made of aluminum, which are produced for example in continuous casting or by sintering and used to reduce the weight and the moment of inertia of the phaser.
  • the fastening structure is made of steel, the gap width between the rotor and the central fastening structure increases due to the greater thermal expansion of aluminum compared to steel with increasing temperature, so that with a reduction in the viscosity of the pressure fluid is accompanied by a gap width increase, especially in hot periods of idle Internal combustion engine contributes to the pressure drop in the applied actuating chambers.
  • O-rings One way to alleviate the problem of leakage is the arrangement of O-rings.
  • a seal with O-rings describes, for example, the DE 10 2008 030 057 A1 , O-rings require the arrangement in correspondingly shaped grooves and thus axial space, which is available only limited. A useful dimensioning of the O-rings is therefore not always possible.
  • the automated assembly of O-rings is complex. There is also the risk that the O-rings made of an elastomer material pose a high rotational friction coefficient during a relative rotation between mounting structure and rotor resulting in undefined friction moments in the joint assembly of camshaft, phaser rotor and mounting structure up to the destruction of the O-rings. Can lead rings.
  • the DE 10 2008 030 057 A1 also discloses the seal by means of a sealing sleeve, which seals one of the ports opening into the annular gap left and right.
  • the sealing collar is used in combination with one or more O-rings, which serve to seal the other connections in the annular gap. The effort required for the assembly and the problems referred to pure O-ring solutions are therefore not reduced.
  • the US 2012/0 097 122 A1 relates to a compactly constructed phasing for a camshaft.
  • a bearing bush having at its periphery openings through which a pressurized fluid for adjusting a phase can be supplied to a piston of the phaser.
  • the WO 2011/098361 A1 relates to a cartridge valve with a metal bush having at least two axially spaced apart ports. Coaxial to the metal bushing is a screen cartridge attached. This screen cartridge has plastic rings and a sieve embedded in them. The hydraulic separation of the two ports from each other by means of the plastic carrier rings of the screen cartridge.
  • the DE 10 2008 006 179 A1 relates to a control valve for a device for the variable adjustment of the timing of gas exchange valves in internal combustion engines.
  • the control valve comprises a hollow valve housing having at least four ports and a guide sleeve disposed within the valve housing.
  • the guide sleeve has a plastic extrusion, in which at least two of the connections are arranged. More camshaft adjusters show the US 2008/149056 A1 , the DE 10 2005 034275 A1 and the US 2006/021933 A1 ,
  • the invention is based on a phase adjuster for adjusting the rotational angular position of a camshaft relative to a crankshaft of an internal combustion engine, a rotatably driven by the crankshaft stator, a rotatably driven by the stator about a rotation axis and for driving the rotation of the camshaft with this connectable or connected rotor and a torque-fixed Connection of rotor and camshaft axially in and expediently by comprising the rotor extending attachment structure. Between the mounting structure and the rotor, optionally also between the mounting structure and the camshaft, an annular gap remains.
  • the rotor forms with the stator at least a first control chamber and at least one second control chamber, which are each acted upon by a pressurized fluid, so that the rotor by appropriate pressurization of the first or the second actuating chamber relative to the stator about the axis of rotation and thereby the rotational angular position of the rotor relative can be adjusted to the stator.
  • the phaser is preferably of the swing-wing type. In swing-gate type phasers, the pressurized fluid in the first ram acts in one circumferential direction and in the other ram in the other circumferential direction on the rotor, each with respect to its axis of rotation.
  • stator and the rotor around the axis of rotation distributed more first control chamber and a plurality of second control chambers by wings of the rotor protrude radially between jaws of the stator, so that in an axial view of the rotor in each case to one side of the wing, the first control chambers and the other side, the second adjusting chambers are formed.
  • the phase adjuster further comprises a sealing device with at least three sealing webs, which are also referred to below as the first sealing web, the second sealing web and the third sealing web.
  • the sealing webs each extend around the axis of rotation and are elastically yielding. All sealing webs can extend in the annular gap.
  • one of the sealing webs or an optionally further sealing web of the sealing device may be arranged outside the annular gap in order to seal the annular gap at an axial end, in particular sealingly abut the axial end of the annular gap on an end face of the rotor or the fastening structure.
  • a first fluid connection opens into the annular gap.
  • the pressure fluid can be supplied to the at least one or preferably a plurality of first positioning chambers.
  • a second fluid port opens into the annular gap.
  • the pressurized fluid from the at least one or preferably a plurality of second actuating chambers can be discharged. It is expedient if the pressurized fluid is also able to be discharged from the one or more first setting chambers through the first fluid connection and the first fluid connection is assigned to the one or more first adjusting chambers in this sense.
  • Such an associated first fluid connection is referred to below as usual also as A-connection.
  • the first fluid connection can also be a pressure connection situated in the inflow of the pressure fluid at an upstream end of a control valve or upstream of a control valve for the phaser, the so-called P connection, via which the pressure fluid is controlled by the control valve or regulated can be fed to both types of adjusting chambers.
  • the pressurized fluid can also be supplied to the one or more second actuating chambers through the second fluid port and the second fluid port is assigned to the second actuating chamber in this sense.
  • Such an associated second fluid connection is referred to as B connection in the following as usual.
  • the second fluid connection can also be a tank connection which lies on the path of the pressure fluid flowing out of the phaser at a downstream end of a control valve or downstream of a control valve for the phaser.
  • This tank connection can be assigned only to the one or more second setting chambers, which thus discharge the pressure fluid only from these chambers, or else serve as a tank connection for the one or more first setting chambers.
  • a sealing sleeve in one piece forms the sealing webs and also connecting webs which are located axially between the sealing webs and connect the sealing webs together.
  • the sealing sleeve is fastened to the rotor or to the fastening structure, which also includes installation situations in which the sealing sleeve is first fixed by the joining assembly of rotor and fastening structure.
  • the sealing sleeve is molded in one piece in a process of primary forming or forming. It may in particular be formed from an elastomer material and preferably by injection molding.
  • the invention means elastomeric plastics and also materials based on natural rubber.
  • the sealing sleeve may contain one or more molded parts, for example one or more filter elements for cleaning the pressurized fluid, one or more stiffening parts or one or more connecting parts, the one or more can form one or more of the connecting webs.
  • At least one of the connecting webs for example, stiffen the sealing sleeve or be developed into a filter element, so combine connecting and stiffening or filtering function together.
  • the sealing sleeve may alternatively be made of plastic at least substantially of a Metallwerksloff and in such embodiments preferably by forming, for example by the metallic sealing webs in such embodiments are resiliently corrugated.
  • a support structure of metal or plastic may further be overmolded with an elastomeric material to form the sealing sleeve.
  • the carrier structure may already have radially elastically yielding webs in the areas of the sealing webs which are coated with elastomer material during the encapsulation. But the elasticity of the sealing webs can also be given only by the elastomer material alone. If the sealing device has one or more further sealing webs, the sealing sleeve preferably also forms this in one piece with the at least three sealing webs.
  • the sealing sleeve can also be produced directly on the fastening sleeve or on an inner periphery of the rotor by primary shaping, in particular injection molding.
  • one of the fluid ports is formed. This means that the respective connecting web can be flowed through by the pressure fluid.
  • one of the fluid connections is formed in the region of each of the at least two connecting webs, one of which connects the first sealing web to the second sealing web and the other connects the second sealing web to the third sealing web.
  • sealing webs as a unit, namely in the form of the sealing sleeve, facilitates and speeds up the assembly considerably. It is not necessary to mount several sealing elements, such as individual sealing rings, separately per phase adjuster. In order to seal two fluid connections of the phaser against each other and additionally on the left and right outside, the at least three sealing webs of the sealing sleeve, which can be mounted as a unit, are sufficient. The risk of incorrect installation is reduced. By mounting the sealing sleeve as a unit, the axial positions of the at least three sealing webs are at the same time sufficiently accurately determined.
  • a positionally accurate mounting of the sealing sleeve ensures a positionally accurate mounting of the sealing webs in one step, it must be made sufficiently accurate only the sealing sleeve as a whole in their formation.
  • the formation of the sealing sleeve in such a way that the at least three sealing webs and the connecting webs connecting them to one another are produced during molding also simplifies the manufacture of the sealing device compared to sealing devices with three separate sealing rings or a combination of one or more sealing rings and a sealing collar with two Stegen.
  • the quality control will likewise simplified, since in a single step the quality, in particular the dimensional accuracy, of the sealing sleeve as a whole and thus at the same time of at least three sealing webs only has to be carried out
  • the claimed phaser may include a control valve serving to control the pressurized fluid, which in preferred embodiments forms the attachment structure.
  • a valve housing of the control valve can form the attachment structure.
  • the control valve comprises such a valve housing and a valve piston axially movable valve piston.
  • the valve housing has a pressure port for supplying the pressurized fluid into the valve housing, a first control port connected to the first or more first actuation chambers, a second control port coupled to the second or the plurality of second actuation chambers, and at least one tank port for discharging the pressurized fluid therefrom Valve housing on.
  • connection of the valve housing in particular either the pressure connection or the first control connection can form the first fluid connection opening into the annular gap, and one of the other connections of the valve housing, namely either the second control connection or the at least one tank connection, the second fluid connection opening into the annular gap ,
  • the control valve may be stirred as a switching valve or as a proportional valve.
  • the function of the control valve may be a pure control operation without feedback or a control action.
  • the concept of controlling is understood as a generic term and should also include the meaning of rules. Accordingly, the control valve may be incorporated in a control loop and the movements of the valve piston in response to one or more different, based on measurement control variables are controlled. As a control variable, for example, serve the speed of the crankshaft or the camshaft.
  • a control valve for the phaser is not centrally located, so does not protrude into or through the rotor, but is arranged externally with respect to the arrangement of stator and rotor.
  • the central mounting structure can serve in such embodiments solely for the purpose of mounting the rotor on the camshaft or optionally fulfill other additional functions, which serve as the guide of the pressurized fluid to or from the adjusting chambers.
  • the fluid connections opening out in the annular gap are, for example, the openings of fluid channels of the rotor which open into the annular gap and which connect the setting chambers of the phaser with the annular gap.
  • the annular gap formed between the attachment structure and the rotor can be extended axially by an annular gap formed between the attachment structure and the camshaft. This applies both for embodiments in which the attachment structure is formed by a central control valve as well as for embodiments with externally to the stator-rotor assembly arranged control valve.
  • the first fluid port or the second fluid port may or may also be arranged in the region of such an annular gap between the attachment structure and the camshaft.
  • the sealing sleeve may be connected to the fastening structure or the rotor either only positively or only frictionally, preferably positively and frictionally, to fix the sealing sleeve relative to the mounting structure and the rotor in position.
  • the sealing sleeve can also be materially connected to the fastening structure or the rotor, optionally purely materially.
  • the sealing sleeve can be adhesively bonded to the fastening structure or the rotor.
  • a cohesive connection is advantageously combined with a positive connection or a frictional connection.
  • the sealing sleeve has an engagement element and the attachment structure or the rotor has an engagement counter element.
  • the engagement element is with the engagement counter-element in a positive or frictional engagement, preferably in a both positive and frictional engagement, which fixes the sealing sleeve on the mounting structure or on the rotor axially or in the circumferential direction, preferably axially and in the circumferential direction.
  • One of engagement member and engagement counter member is a recess, and the other is a protruding into the recess recess. This is preferably a radial depression and correspondingly a radial projection.
  • a positive and frictional engagement may be formed in particular as a latching connection of engagement element and engagement counter-element.
  • the sealing sleeve may comprise a plurality of engagement elements and the attachment structure or the rotor corresponding to a plurality of engagement counter-elements, so that the engagement elements are in each case with one of the engagement counter-elements in a positive or frictional engagement. It is advantageous if a plurality of engagement elements distributed around the axis of rotation and a plurality of engagement counterparts matched thereto are present.
  • a positive or frictional engagement can be produced in an elegant manner by using the first fluid connection or the second fluid connection or an optional further fluid connection opening into the annular gap, in that the relevant fluid connection forms the engagement counter element of either the attachment structure or of the rotor and the engagement element of FIG Sealing sleeve is flowed through by the pressurized fluid. Since the fluid connection used for the intervention opens into the annular gap, it comprises at least one opening located in the annular gap, which in such embodiments at the same time for engagement with the Engagement element is used by the engagement member preferably projects into the respective opening.
  • each of these openings can form an engagement counter element and can be in positive or frictional engagement with in each case one engagement element of the sealing sleeve.
  • the production of an intervention with only one opening is sufficient.
  • the preparation of the engagement with a plurality of openings, for example all openings of the respective fluid port, however, is preferred.
  • Such a solution has the particular advantage that no additional structure must be formed on the attachment structure or the rotor to form the one or more engagement counter-elements.
  • An engagement such as that explained above, in which the sealing sleeve comprises at least two engagement elements and either the attachment structure or the rotor corresponding to two engagement counter elements that are circumferentially offset from each other, also has the advantage that the sealing sleeve in the annular gap not only axially, but is also fixed in the circumferential direction.
  • the one or more engagement elements are or are each preferably shaped as a neck or ring.
  • the respective neck or ring preferably protrudes into the respective counter-engagement element, preferably, as stated, in each case one mouth opening.
  • a positive or frictional engagement can also be produced in that at least one of the sealing webs in a circumferential axis about the rotation recess, such as a circumferential groove, the mounting structure or the rotor protrudes or extending around the axis of rotation, radially projecting rib, preferably to the axis of rotation rotates, embraces.
  • the attachment structure may additionally or instead on an outer peripheral surface or the rotor on one of the mounting structure facing inner peripheral surface riffled, knurled or roughened in some other way, in particular roughened, his and the sealing sleeve on the roughened Abut peripheral surface.
  • the sealing sleeve is mounted with radial pressure on the outer circumference of the mounting structure or the inner circumference of the rotor, which circumference may be basically smooth, so that the engagement of the sealing sleeve with the mounting structure or the rotor is based only on frictional engagement by the sealing sleeve with elastic tension, which can be generated by a material elasticity or a formula elasticity of the sealing sleeve, rests against the respective peripheral surface.
  • Radial compression of the sealing sleeve against the outer circumference of the attachment structure or the inner circumference of the rotor may also be combined with any of the other measures, such as the interlocking engagement of the engagement member and engagement counter member or the roughened peripheral surface. Likewise, two or more of said other measures for a positive, frictional or cohesive engagement in combination can be realized.
  • the seal sleeve may be manufactured separately and joined to the attachment structure or the rotor, or may be obtained by overmolding an outer circumference of the attachment structure or an inner circumference of the rotor with an elastomeric material. It is sufficient, for example, that only one of the sealing webs is formed by the encapsulation and the other sealing webs and the connecting webs are firmly connected in this injection molding with the sealing web made by encapsulation. More preferably, however, several and particularly preferably all the sealing webs of the sealing sleeve are produced directly by the encapsulation. Preferably, the connecting webs are generated during the injection process, so that the sealing sleeve is formed as a whole in the encapsulation.
  • connecting webs or a carrier structure forming the connecting webs as a unit may or may also be positioned as an insert part (e) in the injection mold and encapsulated with the plastic forming the sealing webs and thereby firmly embedded in the overmolding.
  • the fastening structure in a protruding from the annular gap portion on a circumferential axis of rotation about the shoulder, which is clamped for torque-tight connection of the rotor and the camshaft axially in the direction of the rotor.
  • One of the at least three sealing webs or an optionally further sealing web of the sealing sleeve protrudes radially into a gap circulating about the axis of rotation, which gap is formed between the rotor and the shoulder of the fastening structure.
  • the fastening structure In the connected state of the rotor and the camshaft, the fastening structure therefore presses axially against the rotor with this shoulder via the sealing web, and the sealing web consequently seals the annular gap.
  • Such a configuration can be combined with any other of the above types of attachment, in particular axial fixation, the sealing sleeve or only be realized alone.
  • one or two or all three sealing ribs may be at least in a relieved state in which they are located before assembly of the rotor and mounting structure towards an outer circumferential surface of the mounting structure, ie radially inwardly of the axis of rotation , or in the direction of an inner circumferential surface of the rotor, ie, radially outwardly of the axis of rotation, taper, for example conically.
  • the radial spring travel of the respective sealing web can be increased in comparison to a sealing web of constant axial width.
  • Such a configuration may be particularly advantageous if, due to a difference in the thermal expansion of the rotor and the thermal expansion of the fastening structure, the gap width of the annular gap varies depending on the temperature, as is the case for example when the mounting structure and the Rotor are made of different materials, the mounting structure, for example made of steel and the rotor made of an aluminum material.
  • the sealing sleeve for cleaning the pressurized fluid comprises a filter device as an integrated component.
  • the filter device can be formed in particular in the region of at least one of the connecting webs. If the filter device is formed by or with one or more inserts, the elastically yielding material of the sealing sleeve may form a support structure for such one or more inserts.
  • the sealing webs in particular of injection molded plastic injection molded structures and the filter device by encapsulation with the plastic with at least one of the injection molding, preferably with two of the injection molding structures to be firmly connected.
  • a filter device formed by an insert part is preferably encapsulated only peripherally with plastic and accordingly embedded only at their axial lateral edges in the plastic material.
  • Such a sealing sleeve produced as a composite part may, for example, comprise the at least three sealing webs as injection-molded structures of elastomeric plastic and a filter device of metal or plastic embedded in at least one axial edge in one of these injection-molded structures.
  • a filter device can form one of the connecting webs axially between two adjacent sealing webs, or protrude at an axial end of only one of the sealing webs.
  • the filter device can also be formed by a carrier structure of the sealing sleeve.
  • a support structure can in particular form the at least two connecting webs of the sealing sleeve in one piece. It can extend over the entire or almost entire axial length of the sealing sleeve.
  • the sealing webs are produced by encapsulation of such an integrally formed carrier structure with elastomer material.
  • the support structure expediently has perforations through which the elastomer material can penetrate during encapsulation in order to anchor the elastomeric sealing webs to the support structure.
  • the sealing sleeve can have at least one axially extending channel, which is preferably open on a peripheral surface of the sealing sleeve, for example a groove, for guiding the pressurized fluid.
  • the pressure fluid can be axially, optionally additionally in the circumferential direction, for example to a pressure port of a control valve forming the fastening structure or else to the pressure port of a central arranged, projecting into the rotor control valve, which performs no attachment function, are guided.
  • the invention is particularly advantageous for the here claimed phaser, namely for sealing fluid connections in the annular gap between the central mounting structure and rotor and optionally the camshaft, in principle, the molded in one piece sealing sleeve with at least three sealing webs and connecting connecting webs for example for lubricating oil pumps of internal combustion engines such as automotive engines advantage, but also for pumps in general, if they are controlled or regulated in terms of their delivery volume by means of a control valve.
  • a sealing sleeve according to the invention can also be used to seal the annular gap between a valve housing of the control valve of the pump and a surrounding the valve housing other machine part, in particular in such an annular gap opening fluid connections of the control valve or fluid connections for the control valve fluidly separated from each other.
  • a sealing sleeve with at least one sealing web and at least one axially adjoining connecting web, in the region at least one engagement element of the type described here is arranged, in particular at least one engagement element for engagement in an orifice region of a fluid channel, on an outer peripheral surface of a Control valve or an inner peripheral surface of a surrounding the control valve component, such as the rotor of the here claimed phaser, is provided or provided for such engagement.
  • the sealing web can in particular be formed as explained here and rotate around a central axis of the control valve.
  • Such a sealing sleeve preferably has at least one further sealing web which rotates axially adjacent to the sealing web.
  • the sealing sleeve may further comprise an axial extension, in which the at least one or preferably a plurality of engagement elements is or are arranged instead of in the region of the connecting connecting web.
  • a sealing sleeve with one or preferably two or even more sealing webs can also be produced by insert molding a control valve or possibly an inner circumference of a component surrounding the control valve. Examples of such sealing sleeves and their arrangement show the FIGS. 19 to 23 , which, however, are not the subject of the claimed invention.
  • the Applicant reserves the right to such a sealing sleeve as such and also to an arrangement with a control valve which projects with a surrounding machine component, such as a housing or the rotor of a phaser and forms an annular gap with this component, in which the sealing sleeve arranged is to make your own claims.
  • FIG. 1 shows a camshaft phaser in a longitudinal section.
  • the camshaft phaser is arranged at an end face of a camshaft 1 and serves to adjust the phase position, ie the rotational angular position of the camshaft 1 relative to a crankshaft of an internal combustion engine, for example a drive motor of a motor vehicle.
  • the camshaft 1 is rotatably mounted about an axis of rotation R on a machine housing of the internal combustion engine, for example on a cylinder head and can be covered with a cylinder head cover.
  • the camshaft phaser comprises a stator 3, which can be rotated by the crankshaft, and a rotor 7, which is non-rotatably connected to the camshaft 1.
  • the stator 3 is composed of a drive wheel 4, for example a sprocket, a cover 6 and an impeller 5 arranged axially between the drive wheel 4 and the cover 6.
  • the drive wheel 4, the impeller 5 and the lid 6 are rotatably connected to each other.
  • the assembly of the stator 3 is only an example.
  • the stator 3 may alternatively be made of more or instead of the three parts 4, 5 and 6 may be joined from only two parts, such as a one-piece part 4, 5 and the part 6 or the part 4 and a one-piece part 5, 6.
  • the drive wheel 4 for example, on the outside of the impeller 5 circumferentially formed and the lid portion of the drive wheel 4, which laterally seals the stator-rotor assembly, be part of the rotor 7.
  • the cover 6 may be part of the rotor 7.
  • the stator 3 and the rotor 7 form a hydraulic pivot motor according to the vane principle.
  • the camshaft phase adjuster has a fixing structure 10 arranged centrally in relation to the stator-rotor arrangement 3, 7, which, as in the exemplary embodiment, projects centrally through the rotor 7 in the exemplary embodiment and connects the rotor 7 to the camshaft 1 in a torque-tight manner.
  • the stator 3 is supported by the rotor 7.
  • the fastening structure 10 has a connecting portion 12 in which it is fixedly connected to the camshaft 1.
  • the mounting structure 10 projects into a receptacle formed at the front end of the camshaft 1 and is bolted to the camshaft in the receptacle, i. the connecting portion 12 is an external thread.
  • the phase adjuster comprises a control valve, which serves for the fluidic, preferably hydraulic adjustment of the rotational angular position, which the rotor 7 occupies relative to the stator 3.
  • the control valve comprises a valve housing, which is formed by the mounting structure 10 and hereinafter also referred to as a valve housing 10, and a valve housing 10 axially adjustable back and forth arranged valve piston 20.
  • the valve housing 10 thus serves in a dual function as a central attachment means for the torque-fixed connection of camshaft 1 and rotor 7, by pressing the rotor 7 against an end face of the camshaft 1 in the assembled state after production of the joint, in the example a screw connection.
  • FIG. 2 shows the phaser of the first embodiment in cross section 11-11 of FIG. 1 ,
  • the impeller 5 forms an outer component and the rotor 7 an inner component of the pivot motor.
  • the hollow impeller 5 has at its inner periphery radially projecting jaws 5a on.
  • the rotor 7 has radially outwardly projecting wings 8, which form with the jaws 5 a of the stator 3 first actuating chambers K 1 and second actuating chambers K 2 .
  • the adjusting chambers K 1 are arranged in the circumferential direction in each case to one side and the adjusting chambers K 2 in each case to the other side of the wings 8 of the rotor 7.
  • the rotor 7 rotates relative to the stator 3 or impeller 5 in FIG FIG. 2 in the Clockwise to maximum in the FIG. 2 assumed end position. If the adjusting chambers K 2 are pressurized and the adjusting chamber K 1 is relieved of pressure, the rotor 7 rotates counterclockwise relative to the stator 3. The rotational movement relative to the stator 3 in one direction of rotation corresponds to an overfeed and the relative rotational movement in the other direction to a lag of the camshaft 1 relative to the crankshaft.
  • the stator 3 is driven in the direction of rotation D, in the clockwise direction.
  • the adjusting chamber K 1 are therefore early adjusting chambers and the adjusting chambers K 2 late setting chambers.
  • FIG. 2 takes the rotor 7 relative to the stator 3, the early position in which the camshaft 1 leads relative to the crankshaft. If the late actuating chambers K 2 acted upon by the pressurized fluid and the spring actuator chambers K 1 relieved, the rotor 7 rotates in the direction retardation to a maximum in a late position. In the early position, the rotor 7 is locked by means of a Vernageungspins 80.
  • Pin 80 may be moved from the latched position to a release position by pressurizing a pressure chamber 81 against the force of a latch spring 82 to move the rotor 7 toward the retarded position.
  • it is fluidically connected to the nearest late setting chamber K 2 .
  • the early position and the late position are each specified by a stop contact.
  • at least one of the rotor blades 8 is in abutting contact with one of the stator jaws 5a.
  • the rotor 7 can not only be rotated back and forth relative to the stator 3 between these two rotational angle end positions, but can also be hydraulically fixed in any desired intermediate position by appropriate pressurization of both the advance chambers K 1 and the retard chambers K 2 .
  • a torsion spring 17 which is supported with one spring end on the stator 3 and with another spring end on the rotor 7, biases the rotor 7 in the direction of one of its two rotation angle end positions, expediently in the direction of the rotational angle position in which the rotor 7 is locked by means of the locking mechanism can be, in the embodiments, the early position.
  • FIG. 3 shows the rotor 7 and the mounting structure 10, ie the control valve with the valve housing 10 with the valve piston 20, and further components of the phaser released from the joint assembly with the camshaft 1.
  • the components are a filter device 30 and a locking member 40, forming with the valve housing 10 and the valve piston 20 is a separate unit that can be pushed through a central passage of the rotor 7 pre-assembled, and a sealing sleeve 50th
  • the valve piston 20 is hollow with an axially extending cavity 22 which is open at one axial end of the valve piston 20 and forms an axial piston inlet 21 there.
  • the valve piston 20 also has a piston outlet 23, which leads radially through a jacket 22 surrounding the cavity of the valve piston 20.
  • the valve piston 20 has at its side facing away from the piston inlet 21 other axial end a coupling member 25 for coupling with an actuator, which causes the axial displacement of the valve piston 20.
  • the coupling member 25 acts as an actuating tappet of the valve piston 20.
  • the coupling member 25 protrudes at the front end of the valve piston 20, which faces the actuator axially.
  • the coupling member 25 extends through an end closure wall 11 of the valve housing 10.
  • the end closure wall 11 surrounds the coupling member 25 in close fit and thus ensures, despite the reciprocating coupling member 25 for a fluid-tight closure of the valve housing 10th
  • the actuator may in particular be an electromagnetic actuator, such as an axial-stroke solenoid, with a current-supply coil and an armature.
  • the spool is rotatably connected to the engine housing of the internal combustion engine, for example with a lid which is mounted on the machine housing.
  • the armature is axially movable relative to the coil. It is with the coupling member 25 directly in a coupling engagement, which is formed as an axial pressure contact.
  • energizing the coil acts on the armature axially directed towards the coupling member 25 actuating force acting on the coupling member 25 and thus on the valve piston 20 in the coupling engagement, for example, a pure axial pressure contact.
  • the control valve comprises a valve spring 14 whose spring force counteracts the actuating force of the actuator.
  • the valve spring 14 is supported on the valve housing 10 and in the direction of the actuator on the valve piston 20.
  • the actuator is controlled by a controller of the internal combustion engine, for example energized.
  • the control is preferably carried out via a stored in a memory of the engine control map, for example, depending on the speed of the crankshaft, the load or other or other relevant for the operation of the internal combustion engine parameters.
  • the valve piston 20 is arranged in a central axial cavity of the valve housing 10 in the manner explained back and forth movable.
  • the valve housing 10 has at its axial end facing away from the actuator to an axially, centrally in the housing cavity leading pressure port P, via the camshaft 1 (FIG. FIG. 1 ) pressurized fluid can be supplied.
  • the fluid may, in particular, be a lubricating oil which serves to lubricate the internal combustion engine act, which also serves for lubrication, for example, the camshaft bearing of the camshaft 1, so that the pressure port P is connected to the lubricating oil supply to the camshaft 1.
  • This pressurized fluid flows through the axial pressure port P into the valve housing 10 and into the cavity 22 through the piston inlet 21 in axial alignment with the pressure port P.
  • the piston outlet 23 branches off laterally, by way of example, preferably in the radial direction, through which Pressure fluid as a function of the axial position of the valve piston 20 either the Vietnamesestellhuntn K 1 or bossstellhuntn K 2 is supplied to adjust the phase angle of the rotor 7 relative to the stator 3 and thus the phase angle of the camshaft 1 relative to the crankshaft.
  • the piston outlet 23 is formed by radial passages distributed over the circumference of the valve piston 20 through the jacket of the valve piston 20.
  • the valve housing 10 has through its jacket leading connections for the supply and discharge of the fluid to and from the control chambers K 1 and K 2 , namely a control port A, a control port B and valve outlets or tank ports T A and T B.
  • the ports A and B and also the ports T A and T B are straight passageways through the shell of the valve housing 10.
  • the control ports A and B extend as preferred, but only by way of example by the shortest route radially through the shell.
  • FIGS. 1 and 3 show the valve piston 20 in a first axial piston position in which it holds the spring member 14.
  • the piston outlet 23 is connected to the control port A.
  • the pressure fluid supplied via the pressure port P flows in the axial direction through the axial piston inlet 21 into the cavity 22 and from there through the branching piston outlet 23 to the actuating chambers K 1 , which are assigned to the control port A.
  • the adjusting chambers K 2 are connected via the control port B and the outlet or tank port T B to a reservoir and thus relieved in pressure.
  • a recess 26 which connects the control port B to the tank port T B in the first piston position.
  • a further axially extending recess 27 is formed on the outer periphery of the valve piston 20, which also extends circumferentially about the outer periphery of the valve piston 20.
  • the recess 27 is connected in the first piston position with the tank connection T A.
  • the tank connection T A is assigned to the control connection A.
  • it is fluidically separated from the control port A by a sealing web of the valve piston 20 formed between the piston outlet 23 and the recess 27.
  • the actuator pushes the valve piston 20 from the illustrated first piston position axially in the direction of the pressure port P and with correspondingly large actuating force into an axially second piston position in which no longer the control port A, but the other control port B is connected to the piston outlet 23.
  • a molded between the piston outlet 23 and the recess 26 seal ridge of the valve piston 20 separates the control terminal B from the associated tank connection T B so that the actuating chambers K 2 are acted upon by the pressure fluid in the second piston position.
  • the recess 27 connects the control port A to the valve outlet or tank port T A , so that the fluid can flow out of the actuating chambers K 1 and these are relieved of pressure.
  • the rotor 7 moves accordingly in the illustration of FIG. 2 counterclockwise relative to the impeller 5 and thus to the stator 3 in the direction of the late position.
  • the rotatably connected to the rotor 7 camshaft 1 is adjusted in its phase position relative to the crankshaft by the same angle of rotation.
  • the fluid of the high-pressure side flowing through the pressure port P into the control valve acts on the valve piston 20 with a first axial force acting in the direction of the actuator.
  • a first axial force of the valve piston 20 can be flowed through in the direction of the actuator, so that at its rear side facing the actuator between this back and the end closure wall 11, a fluid pressure builds up, which exerts on the back of the valve piston 20, a counterforce, a second axial force , Since the projected by the pressurized fluid projection surface is reduced by the cross-sectional area with which the coupling member 25 protrudes through the end closure wall 11, the axial counterforce, the second axial force corresponding to the cross-sectional area of the coupling member 25 would be less than the first axial force.
  • the valve piston 20 has a radially expanded piston portion 28 and the valve housing 10 has a suitably widened housing portion 18, which surrounds the widening 28 in a tight fit.
  • the valve piston 20 at its outer periphery with the exception of the expansion 28, for example everywhere the same cylindrical cross-section.
  • a feed 24 which are formed by a plurality of distributed around the central axis R through channels in a valve piston bottom.
  • the widening 28 and corresponding to the housing section 18 are dimensioned such that the enlargement of the projection surface facing the actuator 15 due to the widening 28 compensates for at least a predominant part of the cross-sectional area of the coupling element 25 "lost" for the compensation.
  • the control valve can with respect to the compensation of the axial force of the control valve of the DE 10 2010 002 713 A1 correspond, in particular the claimed there embodiments.
  • a fluid connection 29 is formed, which is always in communication with the supply 24.
  • the fluid connection 29 may be shaped, for example, as a notch or groove or as a pocket-shaped recess connected to the feed 24 on the relevant end face of the valve piston 20:
  • a fluid connection 29 may also be formed on the end face of the end closure wall 11 which faces the piston head, such a fluid connection 29 being always connected to the supply 24 and an end face region of the piston 20 must be axially opposite.
  • a comparable fluid connection 29 may be provided, as in the FIGS. 1 and 3 shown to always ensure at this end face that the relevant end face of the valve piston 20 is also applied to the pressure fluid, when the valve piston 20 is in the direction of the pressure port P in a stop position.
  • this fluid connection 29 is always connected to the piston cavity 22.
  • a fluid connection 29 may be formed analogously to the opposite end face of the valve housing 20 or another structure against which the valve piston 20 can be moved to axial stop.
  • the filter device 30 extends axially over part of its length in the valve piston 30. It is to form a filter cross-section effecting the cleaning of the pressurized fluid in the form of a hollow structure, ie as a filter envelope structure or filter bag or basket.
  • the Filterhüll strig consists of a jacket 31, which is cylindrical in the embodiment, and a bottom 32, which forms an in the cavity 22 of the valve piston 20 located axial end of the filter wrap structure.
  • the coat 31 is open at its upstream end with respect to the inflowing pressure fluid, so that there is formed a filter inlet 34 over at least substantially the entire inner cross section of the jacket 31. Between the bottom 32 and the filter inlet 34, the jacket 31 surrounds a filter interior.
  • a filter material which can be flowed through by the pressurized fluid and which retains dirt particles during the throughflow and thereby cleans the pressurized fluid forms almost the entire circumference of the jacket 31.
  • the filter cross section forms the surface of the filter envelope structure 31, 32, which is flowed through by the inflowing fluid through the filter inlet 34 before the pressure fluid reaches the piston outlet 23, and which is covered with a suitable for the purification of the pressurized fluid filter material.
  • the filter device 30 is supported on the valve housing 10 and thereby fixed in particular axially.
  • the filter device 30 has the shape of an elongated cylinder cap with a jacket 31 which is preferably corrugated in the circumferential direction.
  • the blocking member 40 is also arranged in the valve housing 10 upstream of the filter device 30. It is formed as a check valve with a locking body 31 and a locking spring 42 which presses the locking body 41 against a locking body seat.
  • the locking body 41 lifts from its locking body seat and releases the pressure port P.
  • the pressurized fluid flows through the pressure port P while flowing around the blocking body 41 into the valve housing 10 and through an axial passage of the blocking member 40 and the axially adjoining filter inlet 34 into the filter enveloping structure 31, 32, ie into the filter interior. From there, the pressure fluid flows through the filter cross-section, is cleaned as it flows through and enters the piston cavity 22 located downstream of the filter device 30 over the entire filter cross-section.
  • the piston cavity 22 is connected via the piston outlet 23 corresponding to the axial position of the valve piston 20 with the further control port A or B and via this with the actuating chambers K 1 or K 2 , which are assigned to the respective control port A or B.
  • the other group of the control chambers K 1 and K 2 is assigned via this group Control terminal A or B with the associated tank connection T A or T B and connected correspondingly relieved in pressure.
  • valve inlet P, the downstream passage of the obturator 40, the filter inlet 34 and the piston inlet 21 are respectively disposed on an axial end side of the valve housing 10, the obturator 40, the filter device 30 and the valve piston 20.
  • the aforementioned inlets and outlets are located on a common axial alignment, as preferred, but only by way of example on the axis R. In this way, the pressure fluid from the pressure port P to the piston outlet 23 undergoes least possible deflections and thus correspondingly low flow losses. This contributes to increasing the positioning speed of the phaser.
  • the inlets and outlets are axially behind one another. In principle, one or more inlets or an inlet and a passage can be located axially at the same height, as is almost the case with the passage of the blocking member 40 and the filter inlet 34.
  • the large filter cross-section made possible by the use of the piston cavity 22 also acts.
  • Another factor that makes possible large filter cross sections is the design of the filter device 30 as a hollow structure or filter envelope structure 31, 32.
  • the filter envelope structure 31 and 32 has a planar bottom 32 in the exemplary embodiment.
  • the bottom 32 may, for example, also bulge outward or even form a filter cross section.
  • the jacket 31 may, for example, also have a conically tapering taper, so that a bottom 32 is not present in the narrower sense.
  • different expiring coats 31 can be realized.
  • the provision as a cylindrical Filterhüll Fabric 31, 32 has manufacturing advantages.
  • the sealing sleeve 50 is arranged in an annular gap 16 which is formed between the fastening structure 10 formed by the valve housing 10 and the rotor 7.
  • the pressurized fluid can be supplied to the setting chambers K 1 and K 2 via the annular gap 16 as already described above and can also be discharged via the annular gap 16 from the setting chambers K 1 and K 2 .
  • the control ports A and B and the tank port T B of the control valve open at the outer periphery of the valve housing 10 in the Annular gap 16.
  • the control terminal A forming channels of the valve housing 10 and the associated connection channels 7a of the actuating chambers K 1 open at least substantially the same axial height in the annular gap 16.
  • the control terminal B forming channels of the valve housing 10 and the associated connection channels of the control chamber K 2 open at least substantially the same axial height, but at an axial distance from the control port A, in the annular gap 16.
  • the control terminals A and B are fluidly separated from each other in the annular gap 16 of the sealing sleeve 50. Furthermore, the sealing sleeve 50 separates the control port B from the tank port T B in the annular gap 16. Finally, it also seals the control connection A in the annular gap 16 at the side remote from the control connection B. It also separates the connections A and B from the environment.
  • the sealing sleeve 50 comprises three sealing webs, namely a first sealing web 51, a second sealing web 52 and a third sealing web 53, with which it fulfills the aforementioned sealing functions.
  • the sealing bar 51 seals the annular gap 16 at one axial end and at this axial end also the control port A.
  • the sealing web 52 separates the two control connections A and B from one another, and the sealing web 53 separates the control connection B in the annular gap 16 from the tank connection T B.
  • the sealing sleeve 50 further includes a connecting web 56 which extends axially between the sealing webs 51 and 52 and connects them firmly together, and a connecting web 57 which extends axially between the sealing webs 52 and 53 and these two sealing webs 52 and 53 firmly connected ,
  • the sealing sleeve 50 extends axially substantially over the entire length of the rotor. 7
  • the sealing sleeve 50 extends axially beyond the ports A, B and T B , to form on the one hand the sealing web 51 and on the other a positive and frictional engagement with the tank port T B. It has axially in the region of the tank connection T B a plurality of engagement elements 59, which are each formed as a radially inner Abragung the sealing sleeve 50, in the example as a nozzle, and in each case into an engagement counter-element 19 of the valve housing 10 protrude.
  • the engagement counter-elements 19 are formed by areas near the mouth of the tank connection T B , by each one of the engaging elements 59 projects into one of the tank connection T B forming channels of the valve housing 10 and rests in the mouth region of the respective channel with a certain elastic tension.
  • the sealing sleeve 50 is held by this engagement form and frictionally engaged on the outer circumference of the valve housing 10 axially and in the circumferential direction in position. Further lie all sealing webs 51 to 53 each with elastic clamping force on the outer circumference of the valve housing 10 at.
  • the sealing webs 51 to 53 each press with elastic clamping force against the inner circumference of the rotor 7 in order to fulfill their sealing function in this way.
  • the sealing webs 51, 52 and 53 each taper in the radial outward direction towards the inner periphery of the rotor 7, as is preferred, but only by way of example, conically. Due to the radially tapering profile of the radial travel of the sealing webs 51 to 53 is increased compared to, for example, a rectangular profile and the respective sealing webs 51 to 53 respectively desired seal with a variation of the measured width in the radial direction of the annular gap 8 ensures higher security.
  • the sealing sleeve 50 is molded in one piece from an elastically yielding material. It may in particular be formed of an elastomer material, preferably of an elastomeric plastic material, expediently by injection molding. In this way, all functional elements of the sealing sleeve 50, such as in particular the sealing webs 51 to 53, the connecting webs 56 and 57 and the engagement elements 59 serving for a type of locking connection with the valve housing 10, can be produced right from the initial molding.
  • each of the ports A, B, T A and T B is formed by a plurality of channels opening on the outer peripheral surface of the valve housing 10.
  • the sealing sleeve 50 has in the region of its connecting webs 56 and 57 and in an axial extension which axially overlaps with the tank port T B , radial passages which are preferably arranged over the circumference of the sealing sleeve 50 so that they are positioned in and thus simultaneously fixed state of the sealing sleeve 50 with the mouth openings of the respective associated terminal A, B or T B forming channels of the valve housing 10 are in overlap.
  • the sealing sleeve 50 extends the channels of the valve housing 10 thereby quite simply in the radial direction, whereby the flow resistance for the pressurized fluid can be kept low.
  • FIG. 5 shows a fastening structure 10 with a sealing sleeve 50 in a second embodiment.
  • the mounting structure 10 is formed as in the first embodiment of a central with respect to the stator-rotor assembly control valve. It is the same control valve as in the first embodiment. From the first embodiment, only the sealing sleeve 50 differs in that the axial extension, in the region of which the engagement elements 59 of the first embodiment are arranged, is omitted. Instead of the engagement with the openings of the tank connection T B , the positive and frictional engagement of sealing sleeve 50 and fastening structure 10 or valve housing 10 is formed in the region of the control connection A.
  • the sealing sleeve 50 in the region of the connecting web 56 distributed over the circumference a plurality of engagement elements 59, which are formed as in the first embodiment as a flow-through, radial inner Abragungen, for example, again as a nozzle, and each in one of the control port A forming channels of the valve housing Protrude 10 and abut in the mouth-near area on the circumference of the respective channel with elastic tension.
  • This latching connection corresponds to that of the first embodiment, as I said only with the difference that the engagement is not formed with the tank port T B , but with the control port A.
  • the sealing sleeve 50 corresponds to that of the first embodiment. It can replace the sealing sleeve 50 of the first embodiment.
  • the engagement could instead also be formed with the control connection B by forming corresponding engagement elements 59 in the area of the connecting web 57.
  • the at least one engagement element 59 or the plurality of engagement elements 59 can also be provided on one of the connecting webs 56 and 57 instead of on the extension.
  • the engagement elements 59 need not be limited to only one of the connecting webs or an extension of the sealing sleeve 50, in principle, one or more engagement elements 59 may also be provided on a plurality of such webs, for example on both connecting webs 56 and 57. However, one or more engagement elements 59 only in the region of one of the connecting webs or in the region of the extension is sufficient for the positioning and facilitates the attachment of the sealing sleeve 50.
  • FIG. 6 shows from a phaser of a third embodiment, the central region, in particular the joint assembly of camshaft 1 and rotor 7 and central mounting structure 10, which is formed as in the embodiments described above of a valve housing 10 of a central control valve.
  • the control valve differs from the control valve of the first and the second embodiment in that the valve integrated in the filter device 30 accounts, the locking member 40 structurally modified, but unchanged in terms of its function and is also integrated in the control valve, and the pressure port P is in the valve body 10 extends radially. From these from the FIG. 6 without further apparent differences, the control valve 10 corresponds to that of the first embodiment.
  • the sealing sleeve 50 is extended beyond the sealing functions already described both in terms of the sealing function and further by a filter function. It again comprises the three sealing webs 51, 52 and 53 and the connecting webs 56 and 57, with which it performs the same functions as the sealing sleeve 50 of the first embodiment. It further comprises further sealing webs, namely a fourth sealing web 54 and a fifth sealing web 55. With the sealing webs 51 to 55, the pressure port P, the control ports A and B and the tank port T B in the annular gap 16 are fluidly separated from each other and this entire, in the annular gap 16 located terminal assembly at the two axial ends by the outer sealing webs 51 and 55 sealed.
  • the annular gap 16 comprises a first axial section which the rotor 7 and the valve housing 10 form with one another, and subsequently a second axial section, which the valve housing 10 forms with the camshaft 1, by the camshaft 1 having a cavity at its axial end, in which the valve housing 10 protrudes into and projects through it to form by means of the connecting portion 12, the torque-fixed connection with the camshaft 1.
  • the sealing sleeve 50 of the third embodiment comprises a filter device 300, which replaces the filter device 30 of the first embodiment.
  • the filter device 300 is arranged axially between the sealing webs 54 and 55 and connects the sealing webs 54 and 55 with each other, thus forming a connecting web within the sealing sleeve 50.
  • the filter device 300 is sleeve-shaped and may in particular consist of a plastic or metal. It is permeable to the pressurized fluid according to a filter screen, so that the pressurized fluid is cleaned by particulate dirt during the flow through the filter device 300.
  • the filter device 300 forms a flow cross-section for the pressure fluid flowing into the valve. As preferred, it surrounds the pressure port P.
  • the filter device 300 may comprise, for example, a metal fleece or fabric, plastic fleece or fabric or as a metal-plastic fleece or fabric or in particular consist of such a fleece or fabric.
  • the filter device can also be a perforated or perforated metal foil or plastic foil or be formed by such a film.
  • the pressurized fluid is supplied to the phaser via the camshaft 1, flows through a port P of the camshaft 1 in the annular gap 16, flows through the filter device 300 and flows through the opening into the annular gap 16 pressure port P of the control valve and the locking member 40 into the cavity 22nd of the valve piston 20 and is from there according to the axial position of the valve piston 20 as already explained optionally via the port A or port B of the respective associated group of actuating chamber K 1 and K 2 supplied and from the other group of control chambers K 1 and K second dissipated.
  • the port P of the camshaft 1 is disposed in the hollow end portion of the camshaft 1.
  • the filter device 300 overlaps axially with both associated P-terminals.
  • the sealing sleeve 50 can, as already explained for the first exemplary embodiment, be molded in particular from an elastomer material by injection molding.
  • the filter device 300 is formed in the injection process by circumferentially encapsulating it during injection molding to form the sealing webs 54 and 55 at their axial ends and thereby embedded in the elastomeric matrix of the sealing sleeve 50.
  • the sealing webs 51 to 55 are modified in comparison to the first embodiment in that they are radially tapered both radially inward toward the circumferential surface of the valve housing 10 and radially outward to the circumferential surface of the rotor 7 and the camshaft 1 out.
  • the profile of the sealing webs 51 to 55 is at least substantially diamond-shaped, wherein two of the tapered diamond areas are in sealing contact with the respective facing peripheral surface of the valve housing 10 and the rotor 7 and in the region of the two remaining Rauteneck Schemee the connecting webs 56, 57, 58 and the filter device Connect 300 as another connecting bridge.
  • FIG. 7 shows a phaser of a fourth embodiment, which differs from the embodiments described so far in that the sealing sleeve 50 is not attached to the central mounting structure 10, but on the rotor 7.
  • the fastening structure 10 is again from a central control valve of the phaser, namely of the valve housing 10th educated.
  • the control valve corresponds to the control valve of the first embodiment including the integrated filter device 30 and the integrated obturator 40 in all respects.
  • the sealing sleeve 50 is positively connected in the fourth embodiment and preferably also frictionally engaged with the rotor 7. It rests with an outer periphery on the inner circumference of the rotor 7. It comprises a first sealing web 51, a second sealing web 52 and a third sealing web 53 and a further sealing web 54, which serves primarily to improve the fixation on the rotor 7, but optionally also in the joint assembly with the in FIG. 7
  • Camshaft can assume a sealing function by the camshaft optionally axially pressing against the sealing web 54 when the phaser is mounted on the camshaft.
  • the sealing ridge 52 separates the control port A from the control port B, as in the first embodiment, and the sealing ridge 53 separates the control port B from the axially adjacent tank port T B, likewise in the first exemplary embodiment.
  • the sealing bar 51 seals, in principle also as in the first embodiment, the annular gap A and thereby also the control terminal A on the side remote from the control terminal B side.
  • the connecting webs 56 and 57 as in the first embodiment, passages are formed to establish the fluid connection between the control terminals A and B and the associated connection channels of the rotor 7.
  • the control port A is the connection channels 7a ( Fig. 2 ) and the control terminal B are associated with further connecting channels 7b, which connect the control terminal B with the adjusting chambers K 2 .
  • the sealing webs 52 and 53 taper, for example, conically, radially inward, ie in the direction of the facing peripheral surface of the valve housing 10, against which they press with a certain elastic tension.
  • the two outer sealing webs 51 and 54 serve to fix the sealing sleeve 50 in the axial direction. They protrude radially outward into a corresponding recess, in the exemplary embodiment in each case a circumferential shoulder at the respective axial end of the rotor 7.
  • the valve housing 10 presses with a projecting radially outwardly shoulder axially against the rotor 7 and the Seal ridge 51, whereby the rotor 7 pressed in the joint assembly on the one hand axially against a facing end face of the camshaft and thereby the torque-fixed connection of camshaft and rotor 7 is formed and on the other hand by means of the sealing ridge 51 of the annular gap 16 is tightly closed.
  • the sealing web 54 can be omitted.
  • the sealing web 51 and preferably also the sealing web 54 may or may each have on one of its end faces one or more recesses, for example one or more grooves encircling the axis of rotation R.
  • Such measures are intended to prevent the sealing webs 51 and optionally the sealing web 54 from being so strongly compressed in the respective gap that the axial pressing force with which the fastening shoulder of the fastening structure 10 presses the rotor 7 against the camshaft 1 is of practically relevant magnitude is influenced by the sealing web 51 or the sealing ridge 54.
  • the reason is that plastic material tends to creep under load, and therefore, the tightening torque set during installation, and accordingly, the axial pressing force, may decrease in the course of operation of the phaser when the sealing ridge 51 or 52 plastically deforms.
  • the sealing web 51 and preferably also the sealing web 54 is axially only so thick that it is not compressed during assembly.
  • the plastic material of the sealing sleeve 50 has the possibility to avoid, so that the problem of decreasing axial pressing force is avoided.
  • the sealing sleeve 50 is molded as in the first embodiment of an elastomeric material by injection molding in one piece. Apart from the differences described, the phase adjuster of the fourth embodiment corresponds to the phaser of the first embodiment.
  • FIGS. 8 to 10 show the central area of a phaser in a fifth embodiment.
  • the longitudinal sections of the FIGS. 8 and 9 are offset from each other in the circumferential direction, and
  • FIG. 10 shows the in FIG. 9 registered section XX.
  • the attachment structure 10 is formed by the valve housing 10 of a central control valve of the phaser.
  • a valve piston 20 is arranged axially reciprocally movable. It is acted upon by a valve spring 14 in the one direction of its mobility and by means of an electromagnetic actuator of the valve spring 14 against a restoring force as in the other embodiments.
  • the rotor 7 is pressed by the valve housing 10 axially against the camshaft 1 and thereby connected to this torque.
  • the valve housing 10 has, as also in the first embodiment, a control connection A connected to the control chambers K 1 and a control connection B connected to the control chambers K 2 , each opening into the annular gap 16 between the rotor 7 and the valve housing 10 and via the Annular gap 16 with the respective associated connection channels of the rotor 7 and connected via this with the respective associated Stelthuntn K 1 or K 2 .
  • the annular gap 16 also opens, in particular in FIG. 9 recognizable, formed in the valve housing 10 pressure port P, via which the phaser is supplied with the pressurized fluid.
  • the positioning chambers K 1 and K 2 of the stator-rotor arrangement ( Fig.
  • valve piston 20 assumes an axial position in which the pressure port P of the control valve is connected to the control port A for pressurizing the actuating chambers K 1 , while the actuating chambers K 2 via the control port B and through the interior of the valve piston 20 and one of the valve piston 20 formed Tank connection T B are relieved of pressure.
  • valve piston 20 If the valve piston 20 is acted upon by the force of the valve spring 14 with a sufficiently large actuating force, the valve piston 20 closes the control port A with the tank port T A , which is identical to the tank port T B , and connects the pressure port P of the control valve with the other Control connection B.
  • a sealing sleeve 50 is arranged, which essentially according to the first embodiment around the rotation axis R circumferential sealing webs, namely a first sealing bar 51, a second sealing bar 52 and a third sealing bar 53 has.
  • the sealing web 52 located between the connections A and B separates the connections A and B fluidly from one another.
  • the sealing sleeve 50 has two sealing ridges 52 which are axially spaced apart and each provide a seal.
  • the two sealing webs 52 could be combined into one, or it could be one.
  • the sealing web 53 separates the control port B from the pressure port P, to which also the port P formed by the camshaft 1 is calculated, through which the pressure fluid flows into the annular gap 16.
  • the annular gap 16 accordingly comprises a gap section formed between the valve housing 10 and the rotor 7 and an adjoining further gap section formed between the camshaft 1 and likewise the valve housing 10, such as in the third exemplary embodiment (FIG. Fig. 6 ).
  • the sealing sleeve 50 extends into this further gap section of the annular gap 16.
  • the sealing sleeve 50 of the fifth embodiment includes, as in the third embodiment, a filter device 300, which is arranged on the flow path of the pressurized fluid in the annular gap 16 between the port P of the camshaft 1 and the pressure port P of the valve housing 10.
  • the filter device 300 is flowed through axially in the annular gap 16 and accordingly has a filter cross-section with an axial projection surface.
  • the sealing sleeve 50 further has a plurality of axially extending channels 60 distributed around the rotation axis R on its inner peripheral surface facing the valve housing 10 (FIG. Fig. 9 ), which are as preferred, but only by way of example on the inner peripheral surface of the sealing sleeve 50 open.
  • the channels 60 may in particular be groove-shaped.
  • the channels 60 extend from the end face of the sealing sleeve 50, which faces the camshaft 1, in each case to the pressure port P of the valve housing 10, thus connecting the port P of the valve housing 10 to the port P of the camshaft 1.
  • the sealing sleeve 50 is provided with one or more additional channels 60 in which or in which the pressurized fluid in the annular gap 16 and optionally distributed, for example, the P-connection of the valve housing 10 is supplied, opens up additional possibilities for the design of the fluid guide for the phaser.
  • One or more such additional channels 60 may or may also be provided in any other of the embodiments, for example as in the fifth embodiment in the supply of the pressurized fluid to a central control valve or, for example, also in the lead to a tank port such as one of the tank ports T A and T B , to give just examples.
  • the respective sealing sleeve 50 need only be sufficiently thick in the region of the one or more channels 60 in order to be able to form the one or more channels 60 by means of the respective sealing sleeve 50.
  • FIG. 11 shows a arranged on the camshaft 1 phaser a sixth embodiment in a central region in which, as in the other embodiments, the non-rotatable joint assembly of camshaft 1 and rotor 7 is formed. From the stator, the two covers 4 and 6 can be seen.
  • the rotor 7, as in the other embodiments by means of a central mounting structure 100 rotatably connected to the camshaft.
  • the fastening structure 100 projects axially into and through the rotor 7 and into a hollow end section of the camshaft 1 and is connected, preferably screwed, in the region of its connecting section 12 to the camshaft 1.
  • the mounting structure 100 presses the rotor 7 axially in the direction of the camshaft 1, as in the other embodiments directly against the camshaft 1, and thereby establishes the rotationally fixed connection.
  • the stator is movable in the region of its cover 4 relative to the camshaft 1 and in the region of its cover 6 relative to the fastening structure 100 as part of its rotational angle adjustability, preferably in each case with rotational sliding bearings.
  • the stator and the Rotor 7 are designed as in the other embodiments, so that reference can be made in this regard to the description of the first embodiment.
  • the attachment structure 100 is not formed by a control valve in deviation from the embodiments described so far.
  • the control valve which controls the rotational angle adjustments of the rotor 7 relative to the stator, is arranged externally with respect to the stator-rotor arrangement, preferably close to the stator-rotor arrangement.
  • the pressure fluid is the adjusting chambers K 1 and K 2 ( FIG. 2 ) supplied to the stator-rotor assembly for pressurizing and discharged from the adjusting chambers K 1 and K 2 also via the annular gap 16 for pressure relief.
  • the annular gap 16 comprises two adjacent axial sections, one of which is formed between the attachment structure 100 and the rotor 7 and the other between the attachment structure 100 and the hollow end portion of the camshaft 1.
  • the two tank connections T A and T B also form the pressure connection P of the phaser in dependence on the state which the external control valve assumes.
  • the pressure fluid from the control valve flows through the pressure port P, which forms the tank port T A in another state of the control valve in the annular gap 16 and the annular gap 16 and the opening in the annular gap 16 terminal A, the Connection channels 7a ( FIG. 2 ) of the rotor 7, into the control chambers K 1 .
  • the adjusting chambers K 2 are simultaneously relieved of pressure in the annular gap 16 and from there via the tank connection T B to the control valve via connecting channels formed in the rotor 7 whose mouth regions jointly form the control connection B.
  • the pressure fluid from the control valve flows through the openings forming the tank connection T B , which form the pressure port P of the phaser in this valve state, into the annular gap 16 and over the annular gap 16 and the further connecting channels of the rotor 7 Connection B in the adjusting chambers K 2 .
  • the adjusting chambers K 1 are relieved of pressure by the pressure fluid flows out of the adjusting chambers K 1 via the port A and the annular gap 16 and the tank port T A in the direction of the control valve.
  • a sealing sleeve 50 is arranged to fluidly separate the ports A, B, P and T A and P and T B from each other.
  • the tank connection T A forms the pressure connection P
  • the tank connection T B forms the pressure connection P of the stator-rotor arrangement.
  • the control valve may also be formed in such a way that it simultaneously conducts the pressurized fluid to both ports T A and T B , so that both tank ports form the pressure port P together to pressurize both sets of control chambers K 1 and K 2 simultaneously with the pressurized fluid and the rotor 7 in a rotational angular position between the early position and to hold the late position.
  • the sealing sleeve 50 comprises a first sealing web 51, a second sealing web 52 and a third sealing web 53 and a connecting web 56 which extends axially between the sealing webs 51 and 52 and connects them together, and a connecting web 50 extending axially between the sealing webs 52nd and 53 and connects them together.
  • the sealing web 52 seals the connections A and B against each other.
  • the sealing ridge 53 seals the ports B and T B from against the tank connection T A.
  • the sealing sleeve thus fluidly separates the two groups of actuating chambers K 1 and K 2 in the annular gap 16.
  • the ports B and T B open axially between the sealing webs 52 and 53 in the region of the connecting web 57 in the annular gap 16.
  • the terminals A and T A open on the left and right outside the sealed by the sealing webs 52 and 53 gap portion in which the terminals B and T B lead.
  • the sealing bar 51 protrudes into a recess, which is formed on the side facing away from the camshaft 1 side as a circumferential shoulder on the rotor 7.
  • the fastening structure 100 presses with a fastening shoulder axially against the rotor 7 and at the same time against the sealing web 51.
  • the fastening shoulder of the fastening structure 100 does not press directly against the sealing web 51, but via a pressure body, on the outer circumference of the stator , namely the lid 6, is mounted.
  • the sealing sleeve 50 rests with its sealing webs 51, 52 and 53 only on the rotor 7 and on an inner circumference of the camshaft 1. Between the outer circumference of the mounting structure 100 and the sealing sleeve 50 remains an annular gap 61, which connects the port A to the tank port T A.
  • the sealing sleeve 50 may be supported on the circumference of the fastening structure 100, and on the inner circumference of the sealing sleeve 50, at least one axial channel open on the inner peripheral surface of the sealing sleeve 50 may be formed. More preferably, in such a modification, a plurality of such channels may be formed distributed over the inner circumference of the sealing sleeve 50.
  • the one or more channels would replace the annular gap 61 by the one or more channels connecting or connecting terminals A and T A.
  • Advantage of the modification would be that the sealing sleeve 50 is supported radially inwardly of the mounting structure 100.
  • the sealing sleeve 50 is seen over its axial length sufficiently rigid to the required contact pressure for sealing with the inner To ensure peripheral surface of the rotor 7 and the inner circumferential surface of the camshaft 1.
  • the sealing sleeve 50 may, for example, comprise a rigid support sleeve extending from the sealing web 51 to the sealing web 53, which is encapsulated with an elastomer material in order to obtain the sealing webs 51, 52 and 53 in the required elasticity.
  • the support structure may be formed, for example, of a metal material or a sufficiently rigid plastic.
  • a carrier sleeve can directly form the sealing web 52 or the sealing web 53 by the sealing web 52 or 53 by appropriate shaping not material elastic but elastic in form elastic against the inner peripheral surface of the rotor 7 or the camshaft 1 or press respectively ,
  • FIGS. 12 and 13 show a mounting structure 10, which is molded with a sealing sleeve 50 made of an elastomeric material.
  • the sealing sleeve 50 comprises the sealing webs 51, 52 and 53 and the axially extending between each two adjacent sealing webs connecting webs 56 and 57 which connect the left and right adjacent sealing webs together.
  • the attachment structure 10 is, as in other embodiments, a valve housing 10 of a control valve of the phaser.
  • the control valve corresponds to that of the first embodiment.
  • the integrally formed by encapsulation sealing sleeve 50 has in the region of the connecting webs 56 and 57 distributed over the circumference of a plurality of passages which are in registration with openings of the control terminals A and B forming control channels of the valve housing 10. In this way, a short, low-resistance fluid connection between the control valve 10 and the surrounding rotor is obtained in the mounted state for the stator-rotor assembly.
  • the mounting structure 10 at its outer periphery in the axial overlap with the sealing sleeve 50 has a relief-like, knurled, for example, a roughened circumference 70 with a plurality of flat elevations and corresponding recesses into which the elastomer material penetrates during injection molding.
  • the contact surface of the fastening structure 10 and the sealing sleeve 50 is increased and obtained both in the axial direction and in the circumferential direction, a tight fit between these two structures 10 and 50.
  • the outer circumferential surface of the fastening structure 10 in the region of the sealing sleeve 50 can also be smooth. It should also be added to the sealing webs 51-53 that, as in the first exemplary embodiment, they taper radially outward, in the direction of the inner peripheral surface of the rotor.
  • the phase adjuster of the seventh embodiment corresponds to that of the first embodiment.
  • the fastening structure 10 with the integrally formed sealing sleeve 50 can replace the fastening structure 10 and the sealing sleeve 50 of the first exemplary embodiment.
  • FIG. 14 shows the central mounting structure 10 and a sealing sleeve 50 mounted on the outer periphery of the mounting structure 10, from a phaser of an eighth embodiment.
  • the sealing sleeve 50 is manufactured separately from the mounting structure 10 and pressed or glued to the outer circumference of the mounting structure 10 at 71. Press and adhesive connection 71 can each be realized exclusively or in combination.
  • the arrangement of fastening structure 10 and sealing sleeve 50 corresponds to that of the seventh embodiment.
  • FIG. 15 For example, a central mounting structure 10 and a sealing sleeve 50 mounted thereon are shown in a ninth embodiment.
  • the attachment structure 10 is again formed by a valve housing 10 of a control valve according to the first embodiment.
  • the sealing sleeve 50 is positively and frictionally connected to the mounting structure 10. It has in the region of its sealing webs 51, 52 and 53 engagement elements 72 which are engaged with engaging counter-elements 73 of the mounting structure 10 in engagement.
  • the engaging elements 72 are in relation to the engagement Abragept and the engagement counter-elements 53 accordingly depressions.
  • the engagement counter elements 73 are circumferential, groove-shaped channels around the rotation axis R.
  • the engagement elements 72 are formed as round the axis of rotation R annular circumferential projections.
  • the sealing webs 51, 52 and 53 are as in the third embodiment ( FIG. 6 ) in profile diamond-shaped, wherein the radially opposite Rauteneck Schemee outside sealingly abut the inner peripheral surface of the rotor 7 when the mounting structure 10 is inserted into the central passage of the rotor 7 or in particular the phaser mounted on the camshaft, and form the radially inner Rauteneck Schemee the engagement elements 72, ie, one engagement element per sealing ridge 51, 52 and 53.
  • the engagement elements 72 and engagement counter-elements 53 also form the seal with the attachment structure 10 in engagement with each other.
  • the sealing sleeve 50 may additionally be fixed in the circumferential direction, for example by an adhesive connection or an additional Fonn gleichENS to prevent rotation of the sealing sleeve 50 relative to the mounting structure 10 safer.
  • the arrangement of fastening structure 10 and sealing sleeve 50 corresponds to those of the seventh and eighth embodiments.
  • FIG. 16 shows the rotor 7 and the central mounting structure 10 of a phaser in a tenth embodiment.
  • a sealing sleeve 50 is positioned and fixed.
  • the sealing sleeve 50 is axially framed between an end face 10 a of the fastening structure 10 and an end face 7 c of the rotor 7.
  • the end face 10a is an inner annular surface area of the attachment shoulder of the attachment structure 10.
  • the axially opposite end face 7c is a shoulder surface of the rotor 7, over which the diameter of the central passage of the rotor 7 is reduced.
  • the two outer sealing webs 51 and 53 are axially against the respectively facing end face 10a and 7c and seal the connections A and B to the environment.
  • the middle sealing web 52 seals the connections A and B against each other.
  • the sealing webs 51, 52 and 53 are substantially rectangular, that is not tapered. Accordingly, it is advantageous if, when the sealing sleeve 50 is designed as an injection-molded sleeve, a softer elastomer material is used in comparison with other embodiments. In a modification, however, the sealing webs 51 to 53 can taper towards the rotor 7 or the fastening structure 10, although care must be taken that the sealing webs 51 and 53 bear sealingly against the end faces 10a and 7c, the sealing sleeve 50 thus after is axially framed between the end faces 10a and 7c, and seal to the outside.
  • the phase adjuster corresponds to that of the first exemplary embodiment.
  • the diameter of the central passage of the rotor 7 is reduced in several stages, one step per sealing ridge of the sealing sleeve 50.
  • the sealing sleeve 50 again comprises the first sealing ridge 51, the second sealing ridge 52 and the third sealing ridge 53 and connecting webs connecting them 56 and 57.
  • the sealing sleeve 50 is axially enclosed between an end face 10a of the fastening structure 10 and an end face 7c of the rotor 7 and seals the annular gap 16 over the axial length of the sealing sleeve 50 by contact with the shoulder face 10a and contact with the shoulder surface 7c to the outside, to the environment.
  • the sealing web 51 abuts against an end face 7d of the rotor 7 and the sealing web 52 abuts on a further end face 7e of the rotor 7 on its side remote from the end face 10a.
  • the phase adjuster corresponds to that of the previous embodiment ( FIG. 16 ).
  • FIG. 18 shows a phaser of a twelfth embodiment, which differs from the first embodiment only in the sealing sleeve 50.
  • the sealing effect of the respective sealing sleeve 50 was based at least in the Essentially on material elasticity, ie on the elastic properties of the elastomer material used.
  • the sealing effect is obtained at least essentially by a corresponding shaping and thus by the elasticity of the sealing sleeve 50.
  • the sealing sleeve 50 comprises the sealing webs 51, 52 and 53 and the sealing webs interconnecting connecting webs 56 and 57.
  • the sealing sleeve 50 may be formed in particular of a metal material, for example spring steel.
  • the sealing webs 51, 52 and 53 are corrugated in profile. Each of the seal lands 51, 52, and 53 is in sealing contact with the outer peripheral surface of the mounting structure 10 around the rotation axis R and sealingly contacts the inner peripheral surface of the rotor 7 to seal the terminals A and B in the annular gap 16 from each other and the environment ,
  • the phase adjuster corresponds to that of the first exemplary embodiment.
  • FIG. 19 shows a mounting structure 10 with a sealing sleeve 50 attached thereto, which differs from the sealing sleeve 50 of the first embodiment in that the sealing web 51 and the connecting web 56 of the first embodiment have been omitted. Apart from this difference, the sealing sleeve 50 and also the attachment structure 10 corresponds to the first embodiment.
  • the sealing sleeve 50 can easily replace that of the first embodiment, wherein the missing sealing ridge 51 is replaced by another, separate seal.
  • FIG. 20 shows the mounting structure 10 of the first embodiment with a sealing sleeve 50, which has only the two sealing webs 52 and 53 and the connecting web 57 connecting them.
  • the engagement elements 59 are formed in the region of the connecting web 57.
  • FIG. 21 shows an embodiment in which the sealing sleeve 50 has only two sealing webs, namely the sealing web 52 and the sealing web 53, and a connecting web 57 connecting these sealing webs 51 and 52 together.
  • the sealing webs 52 and 53 take over the embodiments of the FIGS. 1 to 18 to the local sealing webs 52 and 53 explained functions.
  • the sealing sleeve 50 is the embodiment of FIGS. 12 and 13 arranged correspondingly on the outer periphery of the attachment structure 10.
  • the fastening structure 10 is with the sealing sleeve 50th encapsulating elastomeric material.
  • the attachment structure 10 has a roughed circumference 70 in the overmolded axial section, preferably a relief-like surface, in order to improve the firm connection with the sealing sleeve 50.
  • the fastening structure 10 and the sealing sleeve 50 correspond to those of the exemplary embodiment of FIGS. 12 and 13 , so that reference is made to the local description and incidentally to the first embodiment.
  • FIG. 22 a fastening structure 10 is shown with a sealing device fixedly arranged thereon, which is not formed as a sealing sleeve, but by two separate sealing webs 52 and 53.
  • the attachment structure 10 is in each case an axial section between the terminals A and B and the terminals B and T B encapsulated with an elastomer material, which forms one of the sealing webs 52 and 53, respectively.
  • the mounting structure 10 has radially below the sealing webs 52 and 53 circumferentially each have a narrow, radially outwardly projecting rib, which is molded with the elastomer material on each of the peripheral surface and on both axial sides.
  • a connecting web interconnecting these two webs is formed corresponding to the connecting web 57 of the other embodiments and the separate sealing webs 52 and 53 are thereby further developed into a sealing sleeve.
  • the formation of the flat, circumferential ribs on the mounting structure 10 can be seen as another example of a positive connection, by the example, the engagement of the at least one engaging element 59 and the at least one engagement counter-element 19 of the first embodiment or the roughened peripheral surface in the embodiments of FIGS. 12, 13 and 21 can be replaced.
  • FIG. 23 shows in an isometric view of a fastening structure 10 with a likewise modified sealing sleeve 50, as in the embodiments of the FIGS. 19 to 21 only the sealing webs 52 and 53 and a connecting web 57 connecting them together.
  • the sealing sleeve 50 is not pushed or pulled axially onto the mounting structure 10, but mounted from the side. It is once axially divided for this purpose, the division is designated 50a, so that it can be bent sufficiently far against its elastic restoring force and placed in the bent state from the side, radially, on the outer circumference of the mounting structure.
  • the Fixing structure 10 is as in the embodiments of FIGS. 21 and 22 formed by the valve housing 10 of a centrally disposed control valve according to the first embodiment.
  • Each of the sealing sleeves 50 connected to the fastening structure 10 in a joining process can, according to the exemplary embodiment of FIG. 23 have a partition 50a to be able to be placed from the side around the mounting structure 23.
  • non-split seal sleeves 50 are preferred.
  • FIG. 24 shows a phaser with a comparison with the first embodiment modified stator-rotor assembly.
  • the central fastening structure 10 with integrated filter device 30 and integrated blocking element 40 corresponds to the first exemplary embodiment.
  • the annular gap 16 and the sealing sleeve 50 of the first embodiment is arranged.
  • the stator 3 is only in two parts.
  • the middle part 5 and the lid 6 are molded in one piece.
  • the locking mechanism comprises a locking pin 83 which is received in a stepped bore of the rotor 7 and axially guided.
  • the pin 83 may, upon pressurization of a pressure chamber 84 against the force of a locking spring 85 from the in FIG. 24 assumed locked position to be moved to a release position to move the rotor 7 toward the late position can.
  • it is fluidically connected to the nearest late setting chamber K 2 .
  • the locking pin 83 comprehensive locking mechanism of the DE 10 2011 004 539 Apart from the application of one of the late setting K 2 corresponds to the locking pin 83 comprehensive locking mechanism of the DE 10 2011 004 539 ,
  • the locking mechanism of the first embodiment ( Figures 1-4 ) Special features.
  • the locking pin 80 is received in the rotor 7 in a simple, non-stepped bore and guided axially.
  • This bore is formed in the rotor 7 of the first embodiment as a blind bore, so that the locking spring 82 directly on the rotor 7 and not as in the embodiment of FIG. 24 supported on an inserted support member 86. Because of the support of the locking spring 82 directly on the rotor, in the first embodiment directly to a rear wall of the blind bore formed by the rotor 7, eliminates a separate to be manufactured and mounted support member, such as the support member 86.
  • Such support elements are usually made of plastic, resulting in the risk arises that the support member 86 move axially during operation of the phaser and thereby axial friction pressure on the opposite end face of the stator 3, in FIG. 24 of the stator cover 4, can exercise. This is prevented in the locking mechanism of the first embodiment by the direct support on the rotor 7.
  • Another difference is that in the first embodiment, the pressure chamber 81 immediately adjacent to the locking opening of the stator 3, here the stator cover 4, and the end face of the locking pin 80, which limits the pressure chamber 81 and is therefore acted upon by the pressure prevailing therein, directly to the stator end face, here the stator cover 4, axially opposite.
  • the pressure chamber 81 is in fluid communication with the locking opening of the stator 3, in which the locking pin 80 is immersed in the locked state, so that also immersed in the locking opening end face of the locking pin 80 with the pressurized fluid is acted upon from the pressure chamber 81.
  • a locking mechanism is obtained which is as safe as in the embodiment of FIG. 24 locked and unlocked, but on the other hand structurally simplified, improved with regard to the described friction problems and not least for these two reasons is also more robust.
  • the pressure chamber 81 may be connected to an adjacent parking chamber K 2 or directly to the B port.
  • the phase adjuster comprises a counter-holder 75 which projects at an end facing the camshaft 1 with a flange in an axial gap between the rotor 7 and the attachment shoulder of the mounting structure 10.
  • This flange of the counter-holder 84 acts like a washer. He intercepts frictional forces during assembly and thereby relieves a stakeout with which the rotor 7 or the camshaft 1 is or will be secured during assembly of the phaser.
  • the anvil 75 further terminates a space at the rear, in which the torsion spring 17 is arranged.
  • the counter-holder 75 serves in this way as a captive in the event that the torsion spring 17 should break.
  • the counter-holder 75 can also be used as a rotary encoder whose angular position and thus the rotational angular position of the rotor 7, relative to the stator 3 can be detected by means of a sensor.

Landscapes

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

Claims (15)

  1. Déphaseur pour régler la position d'angle de rotation d'un arbre à cames par rapport à un vilebrequin d'un moteur à combustion interne, le déphaseur comportant:
    (a) un stator (3) pouvant être entraîné en rotation par le vilebrequin,
    (b) un rotor (7) pouvant être entraîné en rotation par le stator (3) autour d'un axe de rotation (R), lequel rotor forme avec le stator (3) une première chambre de réglage (K1) et une seconde chambre de réglage (K2) auxquelles peut être appliqué un fluide sous pression afin de pouvoir régler le rotor (7) par rapport au stator (3) autour de l'axe de rotation (R),
    (c) une structure de fixation (10 ; 100) s'étendant axialement à travers le rotor (7) pour relier le rotor (7) à l'arbre à cames (1) de manière fixe en termes de couple, laquelle structure de fixation forme un espace annulaire (16) avec le rotor (7) et facultativement également avec l'arbre à cames (1) lorsqu'il est relié au rotor,
    (d) une première nervure d'étanchéité (51), une deuxième nervure d'étanchéité (52) et une troisième nervure d'étanchéité (53) qui s'étendent respectivement autour de l'axe de rotation (R) et sont élastiquement souples,
    (e) un premier raccordement fluidique (A, P, 7a) débouchant axialement dans l'espace annulaire (16) entre la première nervure d'étanchéité (51) et la deuxième nervure d'étanchéité (52), premier raccordement fluidique à travers lequel le fluide sous pression peut être transféré vers la première chambre de réglage (K1),
    (f) un second raccordement fluidique (B, TB, 7b) débouchant axialement dans l'espace annulaire (16) entre la deuxième nervure d'étanchéité (52) et la troisième nervure d'étanchéité (53), second raccordement fluidique à travers lequel le fluide sous pression peut être évacué de la seconde chambre de réglage (K2),
    (g) et une bague d'étanchéité (50) fixée sur le rotor (7) ou la structure de fixation (10 ; 100), laquelle bague d'étanchéité forme d'une seule pièce les nervures d'étanchéité (51, 52, 53) et des nervures de liaison (56, 57) axialement agencées entre les nervures d'étanchéité (51, 52, 53) et reliant celles-ci les unes aux autres, dans lequel l'un des raccordements fluidiques (A, P, 7a, B, TB, 7b) est formé dans la zone d'au moins une des nervures de liaison (56, 57).
  2. Déphaseur selon la revendication précédente, comportant une soupape de commande servant à commander le fluide sous pression, ayant un boîtier de soupape (10) formant la structure de fixation (10) et s'étendant axialement dans le rotor (7), et un piston de soupape (20) axialement mobile dans le boîtier de soupape (10), dans lequel le boîtier de soupape (10) comporte un raccordement de pression (P) pour transférer le fluide sous pression dans le boîtier de soupape (10), un premier raccordement de commande (A) relié à la première chambre de réglage (K1), un second raccordement de commande (B) relié à la seconde chambre de réglage (K2) et un raccordement de réservoir (TA, TB) pour l'évacuation du fluide sous pression à partir du boîtier de soupape (10), et l'un des raccordements du boîtier de soupape (10), de préférence le premier raccordement de commande (A), forme le premier raccordement fluidique(A, P, 7a) ou est relié à celui-ci dans l'espace annulaire (16), et un autre des raccordements du boîtier de soupape (10), de préférence le second raccordement de commande (B), forme le second raccordement fluidique (B, TB, 7b) ou est relié à celui-ci dans l'espace annulaire (16).
  3. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que la bague d'étanchéité (50) comporte un élément de prise (59) et la structure de fixation (10) ou le rotor (7) comporte un élément de prise complémentaire (19), et l'élément de prise (59) est en prise avec l'élément de prise complémentaire (19) par complémentarité de formes ou par friction, de préférence par complémentarité de formes et par friction, laquelle prise fixe la bague d'étanchéité (50) sur la structure de fixation (10) ou le rotor (7) de manière axiale ou dans une direction circonférentielle, dans lequel un élément parmi l'élément de prise (59) et l'élément de prise complémentaire (19) est un évidement et l'autre est une saillie faisant saillie dans l'évidement.
  4. Déphaseur selon la revendication précédente, caractérisé en ce que le premier raccordement fluidique (A, P, 7a) ou le second raccordement fluidique (B, TB, 7b) forme l'élément de prise complémentaire (19) et le fluide sous pression peut s'écouler à travers l'élément de prise (59).
  5. Déphaseur selon l'une des revendications précédentes, caractérisé en ce qu'au moins une des nervures d'étanchéité (51, 52, 53) fait saillie dans un évidement circulaire (73) de la structure de fixation (10) ou du rotor (7) autour de l'axe de rotation (R), ou au moins une des nervures d'étanchéité (51, 52, 53) présente un évidement circulaire autour de l'axe de rotation (R), dans lequel une saillie circulaire autour de l'axe de rotation (R) fait saillie à partir de la structure de fixation (10) ou du rotor (7).
  6. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que les nervures d'étanchéité (51, 52, 53), de préférence également les nervures de liaison (56, 57), sont des nervures en matière plastique moulées par injection, obtenues en moulant par injection une circonférence extérieure (70) de la structure de fixation (10) ou une circonférence intérieure du rotor (7).
  7. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que la bague d'étanchéité (50) est fixée par pression radiale sur la circonférence extérieure (70) de la structure de fixation (10) ou sur la circonférence intérieure du rotor (7).
  8. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que la structure de fixation (10 ; 100) présente, dans une partie faisant saillie à partir de l'espace annulaire (16), un épaulement circulaire autour de l'axe de rotation (R), lequel épaulement peut être serré axialement en direction du rotor (7) pour relier le rotor (7) et l'arbre à cames (1) de manière fixe en termes de couple, et l'une des nervures d'étanchéité (51, 52, 53) ou une nervure d'étanchéité supplémentaire de la bague d'étanchéité (50) fait radialement saillie dans un espace circulaire autour de l'axe de rotation (R) entre le rotor (7) et l'épaulement de la structure de fixation (10 ; 100), de telle sorte que l'épaulement, lorsque le rotor (7) et l'arbre à cames (1) sont reliés, pousse axialement contre le rotor (7) par l'intermédiaire de la nervure d'étanchéité (51) et la nervure d'étanchéité (51) rend l'espace annulaire (16) étanche.
  9. Déphaseur selon l'une des revendications précédentes, caractérisé en ce qu'au moins une des nervures d'étanchéité (51, 52, 53) s'amincit, de préférence de manière conique, en direction d'une surface circonférentielle extérieure de la structure de fixation (10 ; 100) ou d'une surface circonférentielle intérieure du rotor (7).
  10. Déphaseur selon l'une des revendications précédentes, caractérisé en ce qu'au moins les nervures d'étanchéité (51, 52, 53) sont des nervures en matière élastomère moulées par injection formées conjointement dans un procédé de moulage par injection, dans lequel la bague d'étanchéité (50) comporte facultativement une douille de support (300) en métal ou en matière plastique, laquelle douille de support est moulée par injection avec une ou plusieurs des nervures d'étanchéité, de préférence avec chaque nervure d'étanchéité.
  11. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que la bague d'étanchéité (50) comporte un dispositif de filtrage (300) en tant que composant intégré afin de nettoyer le fluide sous pression.
  12. Déphaseur selon la revendication précédente, caractérisé en ce que le dispositif de filtrage (300) forme au moins l'une des nervures de liaison, ou le matériau élastiquement souple de la bague d'étanchéité (50) forme une structure de support pour le dispositif de filtrage (300) fixement relié à la structure de support de manière non amovible.
  13. Déphaseur selon l'une des deux revendications précédentes, caractérisé en ce que les nervures d'étanchéité (51, 52, 53), de préférence également les nervures de liaison (56, 57), sont des nervures en matière plastique moulées par injection formées par un moulage par injection, et le dispositif de filtrage (300) est fixement relié par un moulage par injection à la matière plastique avec au moins une des nervures moulées par injection.
  14. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que la bague d'étanchéité (50) présente au moins un canal (60) de préférence ouvert sur une surface circonférentielle de la bague d'étanchéité (50) et s'étendant axialement pour le guidage du fluide sous pression.
  15. Déphaseur selon l'une des revendications précédentes, caractérisé en ce que le rotor (7) présente, dans une direction radiale, une dilatation thermique supérieure à la structure de fixation (10 ; 100), de telle sorte que la largeur radiale de l'espace annulaire (16) augmente lorsque la température augmente, et en ce que la bague d'étanchéité (50) compense au moins partiellement, par déformation élastique, une variation résultante de la largeur radiale de l'espace annulaire (16).
EP13177506.6A 2012-07-24 2013-07-22 Régulateur de phase d'arbre à cames avec douille d'étanchéité Not-in-force EP2690261B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012213002.0A DE102012213002A1 (de) 2012-07-24 2012-07-24 Nockenwellen-Phasensteller mit Dichtungshülse

Publications (3)

Publication Number Publication Date
EP2690261A2 EP2690261A2 (fr) 2014-01-29
EP2690261A3 EP2690261A3 (fr) 2014-03-12
EP2690261B1 true EP2690261B1 (fr) 2016-09-07

Family

ID=48808232

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13177506.6A Not-in-force EP2690261B1 (fr) 2012-07-24 2013-07-22 Régulateur de phase d'arbre à cames avec douille d'étanchéité

Country Status (4)

Country Link
EP (1) EP2690261B1 (fr)
CN (1) CN103573319B (fr)
DE (1) DE102012213002A1 (fr)
HU (1) HUE029773T2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112513431A (zh) * 2018-09-25 2021-03-16 舍弗勒技术股份两合公司 凸轮轴相位器用插入件及凸轮轴相位器

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2743466B1 (fr) * 2012-12-11 2015-03-18 Hilite Germany GmbH Déphaseur à moteur rotatif
DE102013203139A1 (de) * 2013-02-26 2014-08-28 Schaeffler Technologies Gmbh & Co. Kg Zentralventilkäfig mit am Innenumfang umlaufender Nut und hydraulischer Nockenwellenversteller
JP6225750B2 (ja) * 2014-02-27 2017-11-08 アイシン精機株式会社 弁開閉時期制御装置
JP6295720B2 (ja) 2014-02-27 2018-03-20 アイシン精機株式会社 弁開閉時期制御装置
DE102014226304A1 (de) 2014-12-17 2016-06-23 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
DE102014226316A1 (de) * 2014-12-17 2016-06-23 Robert Bosch Gmbh Kolben-Kraftstoffpumpe für eine Brennkraftmaschine
JP6578896B2 (ja) * 2015-11-09 2019-09-25 アイシン精機株式会社 弁開閉時期制御装置
JP6721334B2 (ja) * 2015-12-28 2020-07-15 株式会社ミクニ バルブタイミング変更装置
DE102016204779B4 (de) * 2016-03-23 2023-12-07 Schaeffler Technologies AG & Co. KG Nockenwellenverstellsystem für eine Verbrennungskraftmaschine eines Kraftfahrzeuges
DE102016214914A1 (de) 2016-08-10 2018-02-15 Schwäbische Hüttenwerke Automotive GmbH Partikelabscheidesystem
DE102017104348B3 (de) * 2017-03-02 2018-05-30 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller
DE102017111900A1 (de) 2017-05-31 2018-03-15 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung
CN109281724B (zh) * 2017-07-21 2022-07-26 舍弗勒技术股份两合公司 凸轮轴调节器和内燃机
DE102017122425A1 (de) * 2017-09-27 2019-03-28 ECO Holding 1 GmbH Bausatz mit einem Nockenwellenversteller
DE102017011004A1 (de) * 2017-11-28 2019-05-29 Schwäbische Hüttenwerke Automotive GmbH Nockenwellenphasensteller mit ringartigem Rückschlagventil
JP6497430B2 (ja) * 2017-11-30 2019-04-10 アイシン精機株式会社 弁開閉時期制御装置
DE102018115343A1 (de) 2018-06-26 2020-01-02 Schaeffler Technologies AG & Co. KG Steuerventil mit Dichtkontur auf einem hülsenförmigen Hydraulikleitelement; sowie Bausatz mit Steuerventil und Nockenwellenversteller
CN109590932B (zh) * 2018-12-19 2024-04-05 海力达汽车科技有限公司 相位调节器同心度充气调节夹具及装置
DE102019100949B4 (de) * 2019-01-15 2020-09-03 ECO Holding 1 GmbH Hülse für einen Schwenkmotorversteller einer Nockenwelle und Schwenkmotorversteller für eine Nockenwelle
WO2023019599A1 (fr) * 2021-08-20 2023-02-23 舍弗勒技术股份两合公司 Régulateur de phase d'arbre à cames

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
DE102005027617A1 (de) * 2004-07-29 2006-03-23 Ina-Schaeffler Kg Ringfilter
DE102005034275B4 (de) * 2005-07-22 2018-02-15 Daimler Ag Nockenwellenstellventilvorrichtung
DE102008006179A1 (de) * 2008-01-26 2009-07-30 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen in Brennkraftmaschinen
DE102008030057B4 (de) 2008-06-27 2018-01-25 Hilite Germany Gmbh Nockenwellenverstelleinrichtung
DE102008057491A1 (de) * 2008-11-15 2010-05-20 Daimler Ag Nockenwellenverstellvorrichtung
DE102010007463A1 (de) * 2010-02-10 2011-09-29 Hydraulik-Ring Gmbh Cartridgeventil
DE102010002713B4 (de) 2010-03-09 2013-12-05 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit Steuerventil für die hydraulische Verstellung der Phasenlage einer Nockenwelle
US8397687B2 (en) * 2010-10-26 2013-03-19 Delphi Technologies, Inc. Axially compact camshaft phaser
DE102011004539A1 (de) 2011-02-22 2012-08-23 Schwäbische Hüttenwerke Automotive GmbH Nockenwellen-Phasensteller mit verbesserter Verriegelungseinrichtung
DE102011084059B4 (de) 2011-10-05 2016-12-08 Schwäbische Hüttenwerke Automotive GmbH Steuerventil mit integriertem Filter und Nockenwellen-Phasensteller mit dem Steuerventil

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112513431A (zh) * 2018-09-25 2021-03-16 舍弗勒技术股份两合公司 凸轮轴相位器用插入件及凸轮轴相位器
CN112513431B (zh) * 2018-09-25 2022-11-15 舍弗勒技术股份两合公司 凸轮轴相位器用插入件及凸轮轴相位器
US11542843B2 (en) 2018-09-25 2023-01-03 Schaeffler Technologies AG & Co. KG Insertion piece for camshaft phaser and camshaft phaser

Also Published As

Publication number Publication date
EP2690261A2 (fr) 2014-01-29
HUE029773T2 (hu) 2017-04-28
CN103573319A (zh) 2014-02-12
DE102012213002A1 (de) 2014-01-30
EP2690261A3 (fr) 2014-03-12
CN103573319B (zh) 2016-09-14

Similar Documents

Publication Publication Date Title
EP2690261B1 (fr) Régulateur de phase d'arbre à cames avec douille d'étanchéité
EP2578818B1 (fr) Soupape de commande avec filtre intégré et régulateur de phase d'arbres à came avec la soupape de commande
EP2245278B1 (fr) Soupape de commande pour un mécanisme de distribution à programme variable
EP1945917B1 (fr) Soupape de commande pour un dispositif de reglage variable des instants d'actionnement de soupapes de remplacement de gaz dans un moteur a combustion interne
EP2463486B1 (fr) Dispositif de réglage de la position de l'angle de rotation d'un arbre à came
EP1596040B1 (fr) Déphaseur d'arbre à cames
DE102010026853B4 (de) Steuerventil zur Steuerung von Druckmittelströmen eines Nockenwellenverstellers
EP2365193B1 (fr) Régulateur de phases d'arbres à cames doté d'une soupape de commande pour le réglage hydraulique de la position de phase d'un arbre à cames
EP1896699B1 (fr) Soupape de commande pour un dispositif de reglage variable des temps de commande de soupapes d'echange des gaz d'un moteur a combustion interne
EP2021588B1 (fr) Soupape de commande pour un dispositif de réglage d'arbre à cames
EP2452052B1 (fr) Soupape centrale d'un déphaseur d'arbre à cames d'un moteur à combustion interne
EP2470756B1 (fr) Vanne de commande
EP3489474A1 (fr) Régulateur de phase d'arbre à cames pourvu de clapet anti-retour de type anneau
EP2267282B1 (fr) Régulateur de phase d'arbres à came doté d'un couvercle de boîtier multifonctionnel
DE102009024026A1 (de) Steuerventil zum Steuern von Druckmittelströmen mit integriertem Rückschlagventil
EP2470757A1 (fr) Soupape de commande
WO2011104058A1 (fr) Valve proportionnelle, en particulier pour un dispositif de réglage d'arbre à cames
DE202010006605U1 (de) Zentralventil
DE102012203114A1 (de) Einlegeteil für Nockenwellenversteller mit Mittenverriegelung
EP3903006A1 (fr) Pompe rotative à compensation axiale, garniture d'étanchéité de sortie pour une pompe et ensemble pompe prémonté
EP3903005A1 (fr) Pompe rotative avec compensation axiale, garniture d'étanchéité de sortie pour une pompe ainsi qu'unité de pompe préassemblée
DE102010013777A1 (de) Zentralventil
DE102014222590A1 (de) Nockenwellenversteller mit Steuerhülse
DE102009043777A1 (de) Zentralventil eines Nockenwellenverstellers einer Brennkraftmaschine

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

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

AX Request for extension of the european patent

Extension state: BA ME

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F01L 1/344 20060101AFI20140131BHEP

17P Request for examination filed

Effective date: 20140417

RBV Designated contracting states (corrected)

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

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20160105

INTG Intention to grant announced

Effective date: 20160216

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013004337

Country of ref document: DE

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 827073

Country of ref document: AT

Kind code of ref document: T

Effective date: 20161015

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20160907

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

Ref country code: HR

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

Effective date: 20160907

Ref country code: LT

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

Effective date: 20160907

Ref country code: NO

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

Effective date: 20161207

Ref country code: FI

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

Effective date: 20160907

Ref country code: RS

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

Effective date: 20160907

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

Ref country code: LV

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

Effective date: 20160907

Ref country code: SE

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

Effective date: 20160907

Ref country code: ES

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

Effective date: 20160907

Ref country code: NL

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

Effective date: 20160907

Ref country code: GR

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

Effective date: 20161208

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

Ref country code: EE

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

Effective date: 20160907

Ref country code: RO

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

Effective date: 20160907

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E029773

Country of ref document: HU

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

Ref country code: SK

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

Effective date: 20160907

Ref country code: CZ

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

Effective date: 20160907

Ref country code: IS

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

Effective date: 20170107

Ref country code: SM

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

Effective date: 20160907

Ref country code: BG

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

Effective date: 20161207

Ref country code: PT

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

Effective date: 20170109

Ref country code: PL

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

Effective date: 20160907

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013004337

Country of ref document: DE

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

Ref country code: IT

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

Effective date: 20160907

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

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

Ref country code: DK

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

Effective date: 20160907

26N No opposition filed

Effective date: 20170608

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

Ref country code: SI

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

Effective date: 20160907

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: IE

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

Effective date: 20170722

Ref country code: CH

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

Effective date: 20170731

Ref country code: LI

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

Effective date: 20170731

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20170731

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

Ref country code: LU

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

Effective date: 20170722

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

Ref country code: BE

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

Effective date: 20170731

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

Ref country code: MT

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

Effective date: 20160907

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

Ref country code: AL

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

Effective date: 20160907

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

Ref country code: MC

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

Effective date: 20160907

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 827073

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180722

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

Ref country code: CY

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

Effective date: 20160907

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

Ref country code: DE

Payment date: 20190719

Year of fee payment: 7

Ref country code: FR

Payment date: 20190719

Year of fee payment: 7

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

Ref country code: MK

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

Effective date: 20160907

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

Ref country code: HU

Payment date: 20190716

Year of fee payment: 7

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

Ref country code: AT

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

Effective date: 20180722

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

Ref country code: GB

Payment date: 20190719

Year of fee payment: 7

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

Ref country code: TR

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

Effective date: 20160907

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502013004337

Country of ref document: DE

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

Effective date: 20200722

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

Ref country code: FR

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

Effective date: 20200731

Ref country code: GB

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

Effective date: 20200722

Ref country code: HU

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

Effective date: 20200723

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

Ref country code: DE

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

Effective date: 20210202