US20100154732A1 - Camshaft adjuster for an internal combustion engine - Google Patents

Camshaft adjuster for an internal combustion engine Download PDF

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Publication number
US20100154732A1
US20100154732A1 US12/161,118 US16111806A US2010154732A1 US 20100154732 A1 US20100154732 A1 US 20100154732A1 US 16111806 A US16111806 A US 16111806A US 2010154732 A1 US2010154732 A1 US 2010154732A1
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US
United States
Prior art keywords
camshaft adjuster
housing
spring
camshaft
spring element
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.)
Abandoned
Application number
US12/161,118
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English (en)
Inventor
Ali BAYRAKDAR
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Assigned to SCHAEFFLER KG reassignment SCHAEFFLER KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BAYRAKDAR, ALI
Publication of US20100154732A1 publication Critical patent/US20100154732A1/en
Abandoned legal-status Critical Current

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Classifications

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

Definitions

  • the invention relates to a camshaft adjuster for an internal combustion engine, according to the precharacterizing clause of Claim 1 .
  • the invention relates to a camshaft adjuster, by means of which, in order to influence
  • a relative angular position between a camshaft and a drive element which is driven by a crankshaft of the internal combustion engine, for example, via a drawing means can be changed in a targeted manner according to a control device.
  • U.S. Pat. No. 6,311,654 B1 has disclosed a camshaft adjuster in the vane cell design, in which a chain sprocket drives a housing of the camshaft adjuster, in which housing an output element which is configured as a rotor is screwed fixedly in terms of rotation to a camshaft via a central screw.
  • Vanes which are assigned to the rotor are arranged in pressure chambers of the housing in such a way that, depending on the hydraulic loading of the pressure chambers, the rotor and therefore the camshaft can be adjusted in the direction “early” or “late” relative to the housing and the drive gear.
  • the document addresses the problem that a hydraulic pump for loading the pressure chambers is usually driven by a crankshaft, which has the consequence that the flow of the hydraulic medium is reduced, in some circumstances, at a low speed of the internal combustion engine. This can lead to undesirable adjustments of the camshaft adjuster.
  • JP A 9 264 110 proposes to connect a torsion spring between a drive element and an output element.
  • the torsion spring is supported in the housing of the camshaft adjuster at one base point on the chain sprocket, while the other base point of the torsion spring is supported on the rotor.
  • DE 40 32 586 A1 has disclosed a camshaft adjuster which is actuated via a control piston, in which a torsion spring arrangement which serves to transmit approximately a mean torque is arranged parallel to the adjusting chambers between a drive gear and a camshaft.
  • This refinement is based on the finding that, for adjustment in different directions, torques have to be generated in the camshaft adjuster which have opposite directions, the magnitudes of which, however, are different in some circumstances for different directions, with the result that, for example as a result of the drive movement and/or the friction conditions, a mean moment for the torque requirements for different adjusting directions results which is not equal to zero.
  • the document proposes to provide the mean moment by an energy accumulator which is configured as a torsion spring arrangement which is connected parallel to the adjusting chambers between the drive sprocket and the camshaft.
  • the torsion spring arrangement is configured separately from the camshaft adjuster.
  • the invention is based on the object of proposing a camshaft adjuster which is improved with regard to
  • the object is achieved by the features of independent Claim 1 . Further refinements of the solution according to the invention result in accordance with the features of dependent Claims 2 to 14 .
  • the invention is based first of all on the finding that it is disadvantageous in some circumstances to connect a spring element for influencing the moment conditions of the camshaft adjuster between a drive element and the camshaft itself.
  • a connection of this type requires suitable measures for connecting the spring element to the camshaft, which measures can increase the manufacturing expenditure for the camshaft, the mass, the mass moment of inertia and/or the installation space of the camshaft.
  • a spring element of this type cannot already be mounted during manufacture of the camshaft adjuster, but only when the camshaft adjuster is assembled with the camshaft.
  • the invention is based on the finding that, for refinements in accordance with U.S. Pat. No. 6,311,654 B1, the spring element has to be mounted in the housing of the camshaft adjuster. This has the consequence that the spring element has to be secured, for example, for an open housing with exact positioning of the housing parts and at the same time guaranteeing the accessibility of the interior of the housing. Moreover, a torsion spring which is arranged in the housing is the reason for the problems which are addressed in U.S. Pat. No. 6,311,654 B1 with regard to the risk of transfer of the hydraulic medium between individual pressure chambers via a receiving space for the spring element.
  • the spring element acts between the housing and the output element.
  • the spring element can be supported directly on the housing or the output element, or merely indirectly with components which are connected fixedly in terms of rotation to the housing or the output element being connected in between.
  • One particular semi-finished product for which the mechanical properties can be predefined in a simple structural manner, can be used if the supporting element is configured as a pin.
  • the cut-out is provided in the wall of the housing with an extent in the circumferential direction, for example in the shape of a curved groove or a “banana-shaped” groove, with the result that the relative rotation between the housing and the supporting element is made possible in a cut-out or groove of this type.
  • the invention proposes, furthermore, that a seal is provided between the housing and the rotor in the surrounding region of the above-mentioned cut-out.
  • the sealing action can be effected, for example,
  • any desired springs may be suitable as spring elements, such as tension or compression springs, helical springs made from elastic material such as spring steel or, for example, an elastomer element.
  • the spring element is configured with a helical torsion spring, in which the spring element extends in the circumferential direction of the camshaft adjuster, preferably with an angle of extent which is greater than 360°.
  • the spring element can be arranged on one end side of the camshaft adjuster.
  • the spring element is preferably arranged on that end side of the camshaft adjuster which faces the cylinder head, with the result that the spring element is arranged between the housing of the camshaft adjuster and the cylinder head. Accordingly, that end side of the camshaft adjuster which lies opposite and faces away from the cylinder head can be used for other functions, for example for assembly of the camshaft adjuster with the camshaft via a central screw, the supply of hydraulic medium or an end-side adjusting unit.
  • the spring element is arranged radially on the inside of a drive gear of the camshaft adjuster.
  • the drive element of the camshaft adjuster can have a central bore or annular groove, in which the spring element is received.
  • the bore or annular groove can serve as protection and/or for guidance of the spring element, without these functions and the receiving space for the spring element necessarily requiring an increase in the installation space of the camshaft adjuster.
  • the spring element can be protected from contamination or mechanical impairments and limited axially against drifting or deflecting away by a cover, with the result that the spring element is arranged in the axial direction between the housing and the covering.
  • the spring element can be booked into the output element, the supporting element and/or the housing or a component which is connected fixedly in terms of rotation to a component of this type in the region of the base point in a simple manner, for mounting (and dismantling).
  • the spring element has at least one hook-shaped spring base point which can be hooked, for example, into a lug, a journal or a bracket.
  • the invention has discovered that a movement of the spring element with elastic loading of the spring element is required in order to release hook-shaped spring base points of this type.
  • the overall elasticity of the spring element can be unsuitable, in order to predefine a force to a sufficient extent for release of the spring element from the associated component, in order that unintended release of the spring element can be avoided, for example during operation of the internal combustion engine.
  • the invention therefore proposes that the spring element is supported on a stop in the radial direction in the surrounding region of the spring base point. Support of this type acts in the same direction, in which the hooking of the spring base point into the associated component is also released.
  • FIG. 1 shows a camshaft adjuster according to the invention which is assembled with a camshaft, in longitudinal section;
  • FIG. 2 shows an end-side view of the camshaft adjuster, with a viewing angle from the side which faces the cylinder head, without a cover which covers a spring element;
  • FIG. 3 shows an end view according to FIG. 2 , in this case with a cover which covers the spring element, however.
  • FIG. 1 shows a camshaft adjuster 1 in longitudinal section, which camshaft adjuster 1 is assembled with a camshaft 2 .
  • the camshaft adjuster 1 in the exemplary embodiment which is shown in the figures is of the vane cell design which is known per se.
  • the camshaft adjuster 1 has a drive element which is configured as a chain sprocket 3 in the exemplary embodiment which is shown.
  • the chain sprocket 3 is drive-connected fixedly in terms of rotation to a further chain sprocket which is connected to the crankshaft, via a drawing means (not shown), a chain here.
  • the chain sprocket 3 is connected fixedly in terms of rotation to a housing 4 or a part of the housing 4 .
  • a rotor 6 which is connected fixedly in terms of rotation to the camshaft 2 is arranged in the housing 4 such that it can be rotated relatively about the longitudinal axis 5 - 5 of the camshaft adjuster 1 .
  • There are pressure chambers 7 in the housing 6 in which pressure chambers 7 vanes which are connected fixedly to the rotor 6 can be pivoted according to the loading with the hydraulic medium, which is associated with the rotation of the rotor 6 relative to the housing 4 .
  • the pressure chambers 7 are loaded with pressure via end-side feed channels of the camshaft adjuster 1 .
  • the fixed connection between the rotor 6 and the camshaft 2 is effected for the exemplary embodiment which is shown by means of a central screw 8 which is screwed on the end side into a central bore, having a thread, of the camshaft 2 .
  • the rotor 6 is captured and clamped between an end face 9 of the camshaft and a head 10 of the central screw 8 , optionally with further components 18 being connected in between.
  • the central screw 8 has an end-side blind bore 11 on that side which faces away from the camshaft 2 , in which end-side blind bore 11 hydraulic elements are received for suitable loading of the camshaft adjuster 1 with the hydraulic medium.
  • the hydraulic medium is fed from the blind bore 11 to the pressure chambers 7 via suitable, in particular radial channels.
  • the housing 4 is formed with an approximately U-shaped half section which has an approximately axially oriented base limb 12 and parallel, radially oriented side limbs 13 , 14 .
  • the side limbs 13 , 14 reach around the rotor 6 in a radially inward manner.
  • Radially inner end faces 15 , 16 of the side limbs 13 , 14 form a gap, a contact face or a sealing face with a circumferential face 17 of the camshaft 2 and the component 18 which is connected fixedly in terms of rotation to the rotor 6 .
  • the side limbs 13 , 14 are formed with two substantially circularly annular discs 23 , 24 .
  • the disc 24 for the side limb 14 has a hollow-cylindrical protrusion 22 with a bore 38 which extends in the direction of the cylinder head and bears the chain sprocket 13 radially on the outside
  • the disc 24 , the protrusion 22 and the chain sprocket 3 are of single-piece configuration for the exemplary embodiment which is shown.
  • the base limb 12 is formed by a hollow-cylindrical outer casing of the housing 4 , which has radially inwardly oriented projections for delimiting the pressure chambers 7 in the circumferential direction.
  • the housing 4 therefore has discs 23 , 24 , which are configured separately from one another but are sealed with respect to one another, and the outer casing.
  • a seal 19 is arranged between the side limbs 13 , 14 and the rotor 6 which can be pivoted relative to the latter, which seal 19 prevents lubricant from passing from one pressure chamber into an adjacent pressure chamber and/or from migrating radially inwards or outside the camshaft adjuster 1 .
  • the seal 19 can be configured as a narrow gap or contact face between the side limbs 13 , 14 and the facing end faces of the rotor 6 .
  • the arrangement of a labyrinth seal, an additional sealing element such as a sealing ring or the like is likewise possible.
  • the rotor 6 has a bore 20 which is oriented parallel with respect to the longitudinal axis 5 - 5 and can be configured as a through bore or blind bore.
  • the spacing of the longitudinal axis of the bore 20 from the longitudinal axis 5 - 5 is greater than the diameter of the camshaft 2 in the region of the camshaft adjuster, but smaller than the diameter for an inner delimitation of the pressure chamber 7 .
  • a supporting element which is configured as a cylindrical pin 21 is inserted into the bore 20 with an accurate fit, in particular with a press fit.
  • the pin 21 extends in a contactless manner, in particular with formation of a play 26 , through a cut-out 25 of the disc 24 on that side which faces away from the cylinder head, and protrudes from the disc 24 with an end region 27 on that side which faces the cylinder head.
  • the end region 27 is arranged in the bore 38 in a manner which lies radially on the inside of the protrusion 22 .
  • the cut-out 25 is configured as a groove 28 which extends in the circumferential direction.
  • the spring element 29 has hook-shaped spring base points 30 , 31 which are connected elastically to one another via a helical torsion spring 32 which extends with a plurality of turns in the circumferential direction.
  • the hook-shaped spring base point 30 which is bent in a hook-shaped manner approximately over a circumferential angle of 180° and has a diameter which is slightly greater than the external diameter of the end region 27 engages around the end region 27 , while the hook-shaped spring base point 31 is bent in a hook-shaped manner approximately over a circumferential angle of 90° and is hooked into the projection 33 of the protrusion 22 , which projection 33 is oriented radially inwards.
  • the spring element 29 is formed from an elastic material, in particular a resilient metal.
  • a spring wire of the torsion spring 32 has a substantially rectangular cross section.
  • a stop 34 is arranged in a manner which is offset approximately by 60° in the circumferential direction about the longitudinal axis 5 - 5 with respect to the projection 33 , at a radius which corresponds approximately to the internal radius of the projection 33 , on the outer side of which the torsion spring 32 is supported.
  • the hook-shaped spring base point 30 of the spring element 29 is hooked into the end region 27 of the pin 21 for substantially finished mounting of the camshaft adjuster 1 itself and finished assembly of the housing 4 .
  • the associated region of the torsion spring 32 is positioned on the stop 34 .
  • the hook-shaped spring base point 31 is deformed elastically radially inwards, with loading of that region of the torsion spring 32 which extends in the circumferential direction between the projection 33 and the stop 34 .
  • the hook-shaped spring base point 31 is then hooked or clipped into the projection 33 .
  • Further support of further part regions of the torsion spring is possible, for example in the region of a further pin 35 which is configured in accordance with the pin 21 , extends through a corresponding cut-out 36 and on which the torsion spring 32 is supported on the radially outer side.
  • the torsion spring 32 is preferably configured with a radial play between individual turns, in order to avoid friction which impedes the pivoting between the rotor 6 and the housing 4 .
  • a cover 37 is introduced radially on the inside into the protrusion 22 .
  • the cover is configured as a circularly annular disc-shaped metal plate, the inner bore of the metal plate having a radius which is slightly greater than the radius of the outer side of the pins 35 , 21 .
  • the cover 37 is bent over in the direction of the cylinder head radially on the outside.
  • the cover 37 is deformed radially inwards by its insertion into the protrusion 22 and, for the operating position which is shown in FIG. 1 , bears with radial pressure against the inner bore 38 of the protrusion 22 in a manner which is positioned fixedly in the latter with a frictional fit.
  • the protrusion 22 can have a suitable groove for an additional form-fitting connection.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
US12/161,118 2006-01-21 2006-12-06 Camshaft adjuster for an internal combustion engine Abandoned US20100154732A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102006002993.3 2006-01-21
DE102006002993A DE102006002993A1 (de) 2006-01-21 2006-01-21 Nockenwellenversteller für eine Brennkraftmaschine
PCT/EP2006/069360 WO2007082600A1 (en) 2006-01-21 2006-12-06 Camshaft adjuster for an internal combustion engine

Publications (1)

Publication Number Publication Date
US20100154732A1 true US20100154732A1 (en) 2010-06-24

Family

ID=37983405

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/161,118 Abandoned US20100154732A1 (en) 2006-01-21 2006-12-06 Camshaft adjuster for an internal combustion engine

Country Status (9)

Country Link
US (1) US20100154732A1 (de)
EP (1) EP1979582B1 (de)
JP (1) JP2009523943A (de)
KR (1) KR101304714B1 (de)
CN (1) CN101360890B (de)
AT (1) ATE479827T1 (de)
DE (2) DE102006002993A1 (de)
PL (1) PL1979582T3 (de)
WO (1) WO2007082600A1 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100258069A1 (en) * 2009-04-09 2010-10-14 Denso Corporation Valve timing control apparatus
US20120216766A1 (en) * 2009-10-26 2012-08-30 Yuji Noguchi Valve closing/opening timing control device
DE102012214033A1 (de) 2011-08-08 2013-02-14 Denso Corporation Ventilzeitsteuerung
US20130324269A1 (en) * 2011-02-08 2013-12-05 SCHAEFFLER TECHOLOGIES AG & Co. KG Camshaft phaser having a spring
US8851033B2 (en) 2012-04-20 2014-10-07 Schaeffler Technologies AG & Co. KG Spring suspension of a hydraulic camshaft adjuster
US8925507B2 (en) 2011-12-12 2015-01-06 Schaeffler Technologies Gmbh & Co. Kg Camshaft adjuster
US9334763B1 (en) 2014-11-21 2016-05-10 Schaeffler Technologies AG & Co. KG Support pin for spring guidance in a camshaft phaser
US9429050B2 (en) 2012-07-31 2016-08-30 Schaeffler Technologies Gmbh & Co. Kg Camshaft phaser
US9441508B2 (en) 2012-09-26 2016-09-13 Schaeffler Technologies Gmbh & Co. Kg Camshaft adjuster
US9957849B2 (en) 2013-04-15 2018-05-01 Schaeffler Technologies AG & Co. KG Camshaft adjuster
US9970334B2 (en) 2013-09-24 2018-05-15 Schaeffler Technologies AG & Co. KG Camshaft adjuster
US11466597B2 (en) 2017-07-25 2022-10-11 Schaeffler Technologies AG & Co. KG Electromechanical camshaft adjuster

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DE102008001078A1 (de) * 2008-04-09 2009-10-15 Robert Bosch Gmbh Vorrichtung zum Verändern der Nockenwellenphasenlage
DE102008048386B4 (de) * 2008-09-22 2016-12-01 Hilite Germany Gmbh Flügelzellennockenwellenversteller
DE102008051142B4 (de) * 2008-10-09 2021-02-11 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102008056796A1 (de) * 2008-11-11 2010-05-12 Schaeffler Kg Rotationskolbenversteller mit Drehfeder
EP2282021B1 (de) * 2009-08-06 2012-05-09 Delphi Technologies, Inc. Nockenwellenversteller mit harmonischem Antrieb und Vorspannfeder
DE102009039385A1 (de) * 2009-08-29 2011-03-03 Schaeffler Technologies Gmbh & Co. Kg Steuerventil
DE102010005602A1 (de) * 2010-01-25 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Nockenwellenversteller
DE102010006415A1 (de) 2010-02-01 2011-08-04 Schaeffler Technologies GmbH & Co. KG, 91074 Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102010009394A1 (de) * 2010-02-26 2011-09-01 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zur varibalen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP5182326B2 (ja) 2010-06-09 2013-04-17 トヨタ自動車株式会社 流量制御弁
DE102010060620B4 (de) * 2010-11-17 2014-02-13 Hilite Germany Gmbh Schwenkmotorversteller
DE102011003556B4 (de) * 2011-02-03 2022-03-24 Schaeffler Technologies AG & Co. KG Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102011081971A1 (de) 2011-09-01 2013-03-07 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012200683B4 (de) 2012-01-18 2017-01-26 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012201550B4 (de) * 2012-02-02 2015-05-21 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit einem Rückschlagventil
DE102012202520B4 (de) 2012-02-20 2016-03-24 Schaeffler Technologies AG & Co. KG Zentralventil für einen Nockenwellenversteller
DE102012213402B4 (de) 2012-07-31 2017-06-01 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102012214760A1 (de) 2012-08-20 2014-02-20 Schaeffler Technologies AG & Co. KG Zentralschraube zur Befestigung eines Nockenwellenverstellers mit einer Nockenwelle mit einem Klemmelement
DE102012214764B4 (de) * 2012-08-20 2018-04-26 Schaeffler Technologies AG & Co. KG Befestigungsanordnung zur Verbindung eines Nockenwellenverstellers mit einem Nockenwellenende einer Nockenwelle
DE102012218403A1 (de) 2012-10-10 2014-04-10 Schaeffler Technologies Gmbh & Co. Kg Hydraulischer Nockenwellenversteller mit Federdeckel sowie Federdeckel mit integrierter Federaufnahme und variabler Federvorspannkraft
DE102013200767B4 (de) 2013-01-18 2016-04-07 Schaeffler Technologies AG & Co. KG Nockenwellenversteller und Federkassette für einen Nockenwellenversteller
DE102013207383B4 (de) 2013-04-24 2022-03-24 Schaeffler Technologies AG & Co. KG Nockenwellenverstelleinrichtung
DE102013212943B4 (de) * 2013-07-03 2017-01-26 Schaeffler Technologies AG & Co. KG Anbindung eines Verstellaktuators an ein Zentralventilsystem für einen trockenen Riementrieb
DE102013217145A1 (de) 2013-08-28 2015-03-05 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102013218031B4 (de) 2013-09-10 2020-09-17 Schaeffler Technologies AG & Co. KG Nockenwellenversteller und Federdeckel
US9470117B2 (en) 2014-05-30 2016-10-18 Schaeffler Technologies AG & Co. KG Trapped support pin for spiral spring retention in a camshaft phaser
DE202015008578U1 (de) 2015-01-08 2016-03-22 Schaeffler Technologies AG & Co. KG Montagehilfe für einen Nockenwellenversteller sowie Verfahren zur Montage des Nockenwellenverstellers an einem nockenwellenfesten Abschnitt
DE102015200140B4 (de) 2015-01-08 2021-07-01 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Montagehilfe sowie Verfahren zur Montage des Nockenwellenverstellers an einem nockenwellenfesten Abschnitt
WO2018220789A1 (ja) * 2017-06-01 2018-12-06 三菱電機株式会社 バルブタイミング調整装置
DE102019106338B4 (de) * 2019-03-13 2020-09-24 Schaeffler Technologies AG & Co. KG Wellgetriebe
CN112797862B (zh) * 2020-12-28 2022-09-27 中国化学工程第十三建设有限公司 联轴器安装对正装置

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PL1979582T3 (pl) 2011-04-29
EP1979582B1 (de) 2010-09-01
DE102006002993A1 (de) 2007-08-09
JP2009523943A (ja) 2009-06-25
KR101304714B1 (ko) 2013-09-06
EP1979582A1 (de) 2008-10-15
WO2007082600A1 (en) 2007-07-26
CN101360890B (zh) 2011-11-23
DE602006016649D1 (de) 2010-10-14
ATE479827T1 (de) 2010-09-15
KR20080087122A (ko) 2008-09-30

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