EP2539552B1 - Dispositif de réglage variable des temps d'ouverture et de fermeture de soupapes d'échange des gaz d'un moteur à combustion interne - Google Patents

Dispositif de réglage variable des temps d'ouverture et de fermeture de soupapes d'échange des gaz d'un moteur à combustion interne Download PDF

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Publication number
EP2539552B1
EP2539552B1 EP11701503.2A EP11701503A EP2539552B1 EP 2539552 B1 EP2539552 B1 EP 2539552B1 EP 11701503 A EP11701503 A EP 11701503A EP 2539552 B1 EP2539552 B1 EP 2539552B1
Authority
EP
European Patent Office
Prior art keywords
drive
spring
internal combustion
protuberance
combustion engine
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
EP11701503.2A
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German (de)
English (en)
Other versions
EP2539552A1 (fr
Inventor
Jürgen Weber
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2539552A1 publication Critical patent/EP2539552A1/fr
Application granted granted Critical
Publication of EP2539552B1 publication Critical patent/EP2539552B1/fr
Not-in-force 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
    • 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
    • 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
    • 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 a device for the variable adjustment of the timing of gas exchange valves of an internal combustion engine with a drive element, an output element and at least one side cover, wherein the drive element can be brought into drive connection with a crankshaft of the internal combustion engine, wherein the output element can be brought into drive connection with a camshaft of the internal combustion engine and is arranged pivotably to the drive element, wherein the side cover is arranged on an axial side surface of the output element or the drive element and rotatably connected to the drive element or the driven element, wherein on the side facing away from the input and the driven element side of the side cover, a spring element is arranged and wherein the side cover has a disc-shaped portion from which protrude a plurality of fastening elements in the axial direction, which angeo on the side facing away from the drive element of the side cover rdnet are.
  • devices for variable adjustment of the timing of gas exchange valves are used to adjust the phase relation between a crankshaft and a camshaft in a defined angular range, between a maximum early and a maximum late position variable.
  • the device is integrated in a drive train via which torque is transmitted from the crankshaft to the camshaft.
  • This powertrain can be used, for example, as belt, chain or gear drive to be realized.
  • the device is non-rotatably connected to a camshaft and, for example, have one or more pressure chambers, by means of which the phase relation between the crankshaft and the camshaft can be selectively changed by pressure medium.
  • Such a device is for example from the DE 10 2008 017 688 A1 known.
  • the device has a drive element, an output element and two side covers, wherein the drive element is in driving connection with a crankshaft and the output element is non-rotatably attached to a camshaft.
  • the output element is arranged in a defined angular interval pivotally to the drive element.
  • the drive element, the output element and the side cover define a plurality of pressure chambers, which form a hydraulic actuator by means of which the phase angle between the output element and the drive element can be variably adjusted.
  • the side covers are arranged on the axial side surfaces of the output element and the drive element and rotatably connected by screws with the drive element. The screws pass through the first side cover and the drive element and engage in each case a clamping nut, which are manufactured separately from the side cover and inextricably linked thereto.
  • fastening element are integrally formed with the side cover.
  • the fasteners are designed as cylindrical collars, which are provided with an internal thread and protrude in the axial direction of the side cover.
  • the present invention has for its object to propose a device with increased life and reliability.
  • the disc-shaped portion on the spring element facing side surface has at least one bulge, which faces at least one spring coil of the spring element in the axial direction of the device.
  • the device has a drive element and an output element, wherein the drive element is driven by a crankshaft of the internal combustion engine and the output element drives a camshaft of the internal combustion engine.
  • the drive element can be in drive connection with the crankshaft, for example, by means of a traction mechanism or gear drive.
  • the output member may be rotatably connected to the camshaft, for example.
  • an actuator for example a hydraulic actuator with at least two counteracting pressure chambers, provided by means of which the output element can be pivoted in a defined angular range relative to the drive element.
  • a phase relation between the output element and the drive element is variably adjustable.
  • a side cover On an axial side surface of the drive element and / or the output element, a side cover is provided which is rotatably connected to one of these components.
  • the side cover on a disc-shaped portion, optionally with a central opening, which seals, for example, the pressure chambers in the axial direction.
  • fasteners protrude in the axial direction. These may be, for example, screw heads of screws or clamping nuts into which the screws engage.
  • the connection between the side cover and the output element or the drive element can be produced.
  • clamping nuts these can be firmly connected to the disc-shaped section before assembly of the side cover or be present as a separate component.
  • the fastening elements are formed integrally with the disk-shaped section, for example as cylindrical collars, which are provided with an internal thread.
  • the disk-shaped portion is preceded by a spring element which, for example, as a helical spring, in particular as a spiral spring, is formed, and on the one hand acts on the output element and on the other hand on the drive element.
  • a spring element By means of the spring element, the output element is acted upon relative to the drive element with a torque which can be used, for example, to compensate for friction losses or to achieve a base position with insufficient pressure medium.
  • the disc-shaped section on the side facing the spring element at least one bulge, which faces at least one spring coil of the spring element in the axial direction of the device.
  • the bulge serves as a stop for the spring element. If the spring element is excited to axial vibrations, then it is true this on the spacer, whereby the vibration amplitudes are reduced. Thus, the vibration loads acting on the spring element decrease. Furthermore, the vibrations are damped. In addition, the rigidity of the disk-shaped portion is increased by the bulges.
  • the extent of the bulge in the radial direction of the disc-shaped portion is formed such that each spring coil of the spring element of the bulge facing in the axial direction and thus each spring coil undergoes the desired damping.
  • the bulge limits an axial movement of the spring coil such that it can not dip into a region radially within the fastening elements. Thus, it is prevented that the spring coil between the fasteners jammed and so off the function of the spring element or the spring element is damaged.
  • the bulge is formed integrally with the disc-shaped portion.
  • the disc-shaped section on the side facing away from the spring element has a recess in the region of the bulge.
  • the bulge is thus formed groove-shaped on the disc-shaped portion.
  • the device has pressure chambers which are separated by vanes and projections, that the depression is arranged in the region of the pressure chambers, vanes and projections and that components of the group of vanes and projections are pivotable relative to the depression, wherein the recess is arranged outside the pivoting range of the pivotable components.
  • a short circuit between two adjacent pressure chambers is effectively prevented via the recess.
  • a plurality of groove-shaped bulges are provided, communicate the wells on the one hand with a pressure medium line and on the other hand in each case with a pressure chamber.
  • the wells can be used to supply pressure to the pressure chambers.
  • the recess may also be formed as a backdrop of a Verrieglungsmechanismus in which engages a locking element to produce a releasable mechanical locking between the drive element and the output element.
  • an insert may be provided in the recess to avoid hydraulic short circuits between the pressure chambers.
  • the insert may be formed as a sliding element.
  • the bulge is massive, i. as excess material on the spring element facing side of the disc-shaped portion is formed. This can be formed integrally with the disk-shaped portion, or manufactured separately for this and force, positively or materially secured thereto.
  • the bulge projects beyond the fastening elements in the axial direction at least in places or flush with them.
  • the first side cover can, for example, by means of non-cutting forming process, for example a deep drawing process, by means of a sintering process, a metal or plastic injection molding process, by casting, forging or stamping package.
  • the bulges can be provided with friction-reducing layers or corrosion protection layers or covered with a jacket of a sliding or protective material.
  • FIG. 1 schematically an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction drive 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, wherein a first and a second device 11 for the variable adjustment of the timing of gas exchange valves 9, 10 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more intake gas exchange valves 9 or one or more exhaust gas exchange valves 10.
  • FIGS. 2 and 3 show a device 11 according to the invention in the longitudinal or cross section.
  • the device 11 has a drive element 13, an output element 14 and two side covers 15, 16, which are arranged on axial side surfaces of the drive member 13 and secured by screws 12 thereto.
  • the output element 14 is designed in the form of an impeller and has a substantially cylindrically designed hub member 17, extending from the outer cylindrical surface area wings 18 in the radial direction outwards.
  • projections 20 extend radially inwards.
  • the projections 20 are formed integrally with the peripheral wall 19.
  • the drive element 13 is mounted by means of radially inner circumferential walls of the projections 20 relative to the output element 14 rotatably mounted on this.
  • the drive element 13 is provided with a sprocket 21, via which by means of a chain drive, not shown, torque can be transmitted from the crankshaft 2 to the drive member 13.
  • the output member 14 is rotatably connected in the assembled state with the camshaft, not shown in these figures, rotatably connected.
  • a pressure chamber 22 is formed between each two circumferentially adjacent projections 20.
  • Each of the pressure chambers 22 is circumferentially bounded by adjacent projections 20, axially of the side covers 15, 16, radially inwardly of the hub member 17, and radially outward of the peripheral wall 19.
  • In each of the pressure chambers 22 protrudes a wing 18, wherein the wings 18 rest against both the side covers 15, 16, and on the peripheral wall 19.
  • Each wing 18 thus divides the respective pressure chamber 22 into two oppositely acting pressure chambers.
  • phase position of the drive element 13 to the output element 14 and thus the phase angle of the camshaft 6, 7 to the crankshaft 2 can be varied.
  • phase position can be kept constant.
  • FIGS. 4 and 5 show a plan view of the device 11 along the arrow IV FIG. 2 , where in FIG. 5 a spring cover 34 is not shown.
  • the side cover 15 has a disk-shaped portion 23 and four fastening elements 24 and consists of a steel sheet.
  • the fastening elements 24 are designed in the form of clamping nuts, which are fastened in a form-fitting manner in openings 33 of the disk-shaped section 23.
  • the clamping nuts 24 protrude in the axial direction from the side surface of the disk-shaped section 23 facing away from the drive element 13.
  • the clamping nuts 24 are each provided with an internal thread into which the screws 12 engage such that the rotationally fixed connection between the side covers 15, 16 and the drive element 13 is made.
  • two of the four screws 12 project out of the respective clamping nut 24 in the axial direction.
  • the length of the other screws 12 is chosen such that they do not protrude from the clamping nuts 24 in the assembled state.
  • a biased spring element 25 ( Figures 2 and 4) is provided in the form of a coil spring.
  • the coil spring is encompassed by a spring cover 34 and has a plurality of concentric spring coils 26 of different diameters.
  • an end of the outermost spring coil 26 engages on the area protruding from the clamping nut 24 region of the first screw 12a ( FIG. 3 ).
  • the outermost spring winding 26 is radially supported by the region of the second screw 12b protruding from the clamping nut 24.
  • One end of the innermost spring coil 26 engages a protruding from the output member 14 Pin 27 on.
  • the innermost spring coil 26 is supported radially inwardly on two further pins 27 projecting from the driven element 14.
  • the biased spring element 25 is connected to both the drive member 13 and the output member 14 such that a torque between these components is mediated. This can serve, for example, to adjust the output element 14 in the case of insufficient supply of pressure medium to the device 11 in a base position or to adjust different adjustment speeds in the direction of earlier or later control times of the gas exchange valves 9, 10.
  • the spring element 25 is excited to axial and radial vibrations, whereby individual spring coils 26 can dip into the region between the fastening elements 24.
  • the dipping spring coil 26 is clamped between the fasteners 24, whereby the function of the device 11 is limited.
  • increased wear on the spring element 25 occurs, and there is a risk that the spring element 25 breaks due to the increased load.
  • five recesses 28 are provided on the disk-shaped portion 23, which extend in the direction of the spring element 25.
  • the bulges 28 are formed by means of a chipless forming process, so that on the first side cover 15 recesses 29 are formed on the output member 14 side facing.
  • Three first recesses 29 a are arranged in the region of pressure chambers 22 outside a pivoting range of the corresponding blade 18.
  • a second recess 29b is arranged in a pivoting region of a wing 18, wherein the extension of the recess 29b in the circumferential direction is chosen smaller than the corresponding extent of the wing 18.
  • a third recess 29c is arranged in the region of one of the projections 20, wherein the extension of Recess 29c is selected smaller in the circumferential direction, as the corresponding extension of the projection 20. In this way, a hydraulic short circuit avoided between two adjacent pressure chambers.
  • a loading member 30 is inserted into the second recess 29b to further reduce the leakage between the pressure chambers and to improve the sliding contact between the first side cover 15 and the output member 14.
  • the bulges 28 are formed and arranged such that each spring coil 26 faces each bulge 28 in the axial direction.
  • the bulges 28 prevent the spring coils 26 from entering the region between the clamping nuts 24.
  • the vibration amplitude is reduced and dampens the vibration.
  • damage to the spring member 25 is prevented and reduces the stress caused by the vibrations.
  • the axial side surfaces of the bulges 28 may be provided with a friction-reducing layer, for example a Teflon layer, or a wear-resistant layer.
  • the output element 14 has a receptacle 31, in which an unillustrated, axially displaceable locking pin is received.
  • the disc-shaped portion 23 has a slotted portion 32, into which the locking pin can engage in a certain phase position of the output element 14 relative to the drive element 13 in order to form a releasable, mechanical coupling between these two components.
  • the slide 32 also projects out of the disk-shaped portion 23 and can serve as an axial stop for the spring element 25 in addition to the bulges 28.

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

Claims (8)

  1. Dispositif (11) d'ajustement variable des temps de commande de soupapes d'échange de gaz (9, 10) d'un moteur à combustion interne (1), comprenant
    - un élément d'entraînement (13), un élément de prise de force (14) et au moins un couvercle latéral (15),
    - l'élément d'entraînement (13) pouvant être amené en liaison d'entraînement avec un vilebrequin (2) du moteur à combustion interne (1),
    - l'élément de prise de force (14) pouvant être amené en liaison d'entraînement avec un arbre à cames (6, 7) du moteur à combustion interne (1) et étant disposé de manière à pivoter par rapport à l'élément d'entraînement (13),
    - le couvercle latéral (15) étant disposé sur une face latérale axiale de l'élément de prise de force (14) ou de l'élément d'entraînement (13) et étant connecté de manière solidaire en rotation à l'élément d'entraînement (13) ou à l'élément de prise de force (14),
    - un élément de ressort (25) étant disposé sur le côté du couvercle latéral opposé à l'élément d'entraînement et à l'élément de prise de force (13, 14), et
    - le couvercle latéral (15) présentant une portion en forme de disque (23) depuis laquelle font saillie, dans la direction axiale, plusieurs éléments de fixation (24) qui sont disposés sur le côté du couvercle latéral (15) opposé à l'élément d'entraînement (13), caractérisé en ce que
    - la portion en forme de disque (23) présente, sur la face latérale tournée vers l'élément de ressort (25), au moins un renflement (28) en regard d'au moins un enroulement de ressort (26) de l'élément de ressort (25) dans la direction axiale du dispositif (11).
  2. Dispositif (11) selon la revendication 1, caractérisé en ce que le renflement (28) limite un mouvement axial de l'enroulement de ressort (26) de telle sorte que celui-ci ne puisse pas plonger dans une région radialement à l'intérieur des éléments de fixation (24).
  3. Dispositif (11) selon la revendication 1, caractérisé en ce que le renflement (28) est réalisé d'une seule pièce avec la portion en forme de disque (23).
  4. Dispositif (11) selon la revendication 1, caractérisé en ce que l'étendue du renflement (28) dans la direction radiale de la portion en forme de disque (23) est réalisée de telle sorte que chaque enroulement de ressort (26) de l'élément de ressort (25) soit en regard du renflement (28) dans la direction axiale.
  5. Dispositif (11) selon la revendication 1, caractérisé en ce que la portion en forme de disque (23) présente, sur le côté opposé à l'élément de ressort (25), un renfoncement (29) dans la région du renflement (28).
  6. Dispositif (11) selon la revendication 5, caractérisé en ce que le dispositif (11) présente des chambres de pression qui sont séparées par des ailes (18) et des saillies (20), en ce que le renfoncement est disposé dans la région des chambres de pression, des ailes (18) et des saillies (20) et en ce que des composants constitués du groupe des ailes (18) et des saillies (20) peuvent pivoter par rapport au renfoncement (29), le renfoncement (29) étant disposé à l'extérieur de la région de pivotement des composants pivotants.
  7. Dispositif (11) selon la revendication 1, caractérisé en ce que le renflement (28) est réalisé sous forme d'un excès de matière au niveau du côté de la portion en forme de disque (23) tourné vers l'élément de ressort (25).
  8. Dispositif (11) selon la revendication 1, caractérisé en ce que le renflement (28) fait saillie au moins en partie dans la direction axiale au-delà des éléments de fixation (24) ou se termine en affleurement avec ceux-ci.
EP11701503.2A 2010-02-26 2011-01-25 Dispositif de réglage variable des temps d'ouverture et de fermeture de soupapes d'échange des gaz d'un moteur à combustion interne Not-in-force EP2539552B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010009394A DE102010009394A1 (de) 2010-02-26 2010-02-26 Vorrichtung zur varibalen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2011/050972 WO2011104055A1 (fr) 2010-02-26 2011-01-25 Dispositif de réglage variable des temps d'ouverture et de fermeture de soupapes d'échange des gaz d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2539552A1 EP2539552A1 (fr) 2013-01-02
EP2539552B1 true EP2539552B1 (fr) 2013-12-18

Family

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Application Number Title Priority Date Filing Date
EP11701503.2A Not-in-force EP2539552B1 (fr) 2010-02-26 2011-01-25 Dispositif de réglage variable des temps d'ouverture et de fermeture de soupapes d'échange des gaz d'un moteur à combustion interne

Country Status (6)

Country Link
US (1) US8671900B2 (fr)
EP (1) EP2539552B1 (fr)
KR (1) KR20130008014A (fr)
CN (1) CN102791965B (fr)
DE (1) DE102010009394A1 (fr)
WO (1) WO2011104055A1 (fr)

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DE102010005602A1 (de) * 2010-01-25 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Nockenwellenversteller
DE102010008005A1 (de) * 2010-02-15 2011-08-18 Schaeffler Technologies GmbH & Co. KG, 91074 Stator-Deckel-Einheit und Nockenwellenversteller
DE102011081971A1 (de) 2011-09-01 2013-03-07 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102011086236B4 (de) 2011-11-14 2017-03-09 Schaeffler Technologies AG & Co. KG Verbindung zwischen einem Stirnrad und einer Zahnwelle einer Nockenwellenverstelleinheit
DE102012217393A1 (de) * 2012-09-26 2014-03-27 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102013204659A1 (de) * 2013-03-18 2014-09-18 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
JP6217763B2 (ja) * 2014-02-14 2017-10-25 アイシン精機株式会社 弁開閉時期制御装置
CN105650241A (zh) * 2015-12-10 2016-06-08 刘元生 发动机可调正时齿轮
CN217002003U (zh) * 2019-10-21 2022-07-19 三菱电机株式会社 气门正时调节装置
US11560816B1 (en) 2021-07-16 2023-01-24 Schaeffler Technologies AG & Co. KG Spring retainer retention tab for bias spring

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US5095857A (en) * 1990-07-17 1992-03-17 Eaton Corporation Self actuator for cam phasers
DE19708661B4 (de) 1997-03-04 2005-06-16 Ina-Schaeffler Kg Vorrichtung zur Variierung der Ventilsteuerzeiten einer Brennkraftmaschine, insbesondere Nockenwellen-Verstelleinrichtung nach dem Flügelzellenprinzip
DE10007200A1 (de) 2000-02-17 2001-08-23 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE10215879A1 (de) * 2002-04-11 2003-10-23 Ina Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Einrichtung zur hydraulischen Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
US6619248B1 (en) * 2002-04-17 2003-09-16 Ina-Schaeffler Kg Device for altering the control timing of gas exchange valves of an internal combustion engine, especially an apparatus for hydraulic rotational angle adjustment of a camshaft relative to a crankshaft
DE102005024241B4 (de) 2005-05-23 2017-08-17 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102006002993A1 (de) * 2006-01-21 2007-08-09 Schaeffler Kg Nockenwellenversteller für eine Brennkraftmaschine
DE102006036052B4 (de) * 2006-08-02 2018-03-08 Schaeffler Technologies AG & Co. KG Dichtblech für einen Nockenwellenversteller und Nockenwellenversteller mit einem Dichtblech
CN201110201Y (zh) * 2007-09-17 2008-09-03 靳宇男 界面配气发动机
DE102008017688A1 (de) 2008-04-08 2009-10-15 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine

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CN102791965A (zh) 2012-11-21
WO2011104055A1 (fr) 2011-09-01
CN102791965B (zh) 2014-10-29
EP2539552A1 (fr) 2013-01-02
US20120318222A1 (en) 2012-12-20
DE102010009394A1 (de) 2011-09-01
US8671900B2 (en) 2014-03-18
KR20130008014A (ko) 2013-01-21

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