EP3219942B1 - Déphaseur d'arbre à cames - Google Patents

Déphaseur d'arbre à cames Download PDF

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Publication number
EP3219942B1
EP3219942B1 EP17159488.0A EP17159488A EP3219942B1 EP 3219942 B1 EP3219942 B1 EP 3219942B1 EP 17159488 A EP17159488 A EP 17159488A EP 3219942 B1 EP3219942 B1 EP 3219942B1
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EP
European Patent Office
Prior art keywords
adapter
camshaft
adjuster
rotor
stator
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.)
Active
Application number
EP17159488.0A
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German (de)
English (en)
Other versions
EP3219942A1 (fr
Inventor
Steve NANCE
John Snyder
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.)
Eco Holding 1 GmbH
Original Assignee
Eco Holding 1 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 Eco Holding 1 GmbH filed Critical Eco Holding 1 GmbH
Publication of EP3219942A1 publication Critical patent/EP3219942A1/fr
Application granted granted Critical
Publication of EP3219942B1 publication Critical patent/EP3219942B1/fr
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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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • 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
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • 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
    • 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
    • F01L2250/00—Camshaft drives characterised by their transmission means
    • F01L2250/02—Camshaft drives characterised by their transmission means the camshaft being driven by chains
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets

Definitions

  • the invention relates to a camshaft adjuster according to the preamble of patent claim 1.
  • Camshaft phasors for internal combustion engines are well known.
  • the camshaft adjuster has a non-rotatably connected to the camshaft hydraulic valve, which is provided for the hydraulic actuation of a Schwenkverstellers the camshaft adjuster.
  • the pivoting adjuster is indirectly connected to a crankshaft of the internal combustion engine, so that a relative angular position between the crankshaft and the camshaft is variable by the action of the pivoting adjuster.
  • the published patent DE 10 2010 018 202 A1 shows a camshaft adjuster, which has a camshaft adapter for the axial connection of the camshaft adjuster to a camshaft.
  • the camshaft adapter is positively connected to the camshaft and clamped to a rotor of the camshaft adjuster.
  • phaser comprising a camshaft adapter is shown in FIG WO 2015/122359 A1 disclosed.
  • An object of the present invention is a camshaft adjuster to provide which is safe to use and inexpensive to manufacture.
  • the camshaft adjuster comprises a pivoting adjuster and a hydraulic valve acting hydraulically on the pivoting adjuster.
  • the hydraulic valve is rotatably connected to a camshaft for rotating the camshaft.
  • the swivel adjuster has a stator and a rotor formed coaxially with the stator, wherein the rotor is rotatable relative to the stator.
  • the hydraulic valve is formed at least partially projecting into the Schwenkversteller.
  • an adapter is provided for relative axial positioning of the rotor and the stator. According to the adapter for loose mounting in the swivel adjuster is formed and a firm connection of the adapter with the swivel adjuster is brought about after assembly of the camshaft on the hydraulic valve.
  • the adapter is only fixed and sealed when the camshaft adjuster is mounted on the camshaft in the phaser.
  • the loose adapter does not require a press connection process or a cohesive connection process, for example gluing, for connection to the rotor. Due to the reduced assembly operations, there is a cheaper installation compared with the prior art.
  • Another advantage is a reduction of machining operations of the adapter, since an outer diameter of the adapter does not have to be formed exactly.
  • the production of the outer diameter is usually carried out by means of a turning operation. This machining operation is usually necessary in particular when pressing the adapter or when gluing the adapter to the rotor, so that one for the production of the corresponding Connection exactly trained adapter can be provided.
  • a next advantage of the loose connection with the Schwenkversteller is seen in a relatively free design of the camshaft adjuster.
  • the camshaft adjuster can be easily assigned by replacing the adapter different camshafts. This reduces an essential development and assembly process for providing the camshaft adjuster for a camshaft.
  • Another advantage is to produce the rotor in a simple design and thus cost, since it may be in the form of, for example, two circular, flat discs.
  • a radial distance is formed between adapter and rotor, which is preferably formed at all times. An over-determination on the outside of the adapter is thereby excluded.
  • the hydraulic valve is designed as a helical central valve.
  • the advantage is that with the aid of the helical central valve, a centering of the rotor, the stator and the adapter is formed.
  • the components of the camshaft adjuster can be clamped axially one behind the other via the helical central valve and the adapter allows the relative axial positioning of stator and rotor. Furthermore, tightness between the rotor and the adapter is achieved when tightening the helical center valve.
  • the advantage of arranging the adapter between the camshaft and the rotor can be seen in the fact that in the connection of the camshaft with the hydraulic valve, the adapter can easily adjust the necessary axial position by the positioning of the camshaft.
  • a sliding bearing is formed between the pivoting adjuster and the adapter, wherein the radial distance between the sliding bearing and the adapter is provided. Bearing surfaces are only provided between the sliding bearing and the rotor or the drive wheel. An overdetermination of the adapter is not possible.
  • the sliding bearing is designed as a radial slide bearing in the form of a floating radial bearing.
  • the adapter has an annular collar at its end facing the rotor, a fixation of the adapter is brought about during assembly on a camshaft.
  • the adapter has over its circumference at least one recess which completely penetrates the adapter in the radial direction.
  • a tank connection of the hydraulic valve can be provided for removal via the adapter.
  • the recess is groove-shaped.
  • An inventive camshaft adjuster 1 for an internal combustion engine, not shown, for adjusting timing, in other words of opening and closing times of gas exchange valves of the internal combustion engine is in a first embodiment according to Fig. 1 educated.
  • the camshaft adjuster 1 allows during the operation of the internal combustion engine to bring about a change in the timing.
  • a relative angular position of a camshaft of the internal combustion engine, not shown is continuously varied with respect to a crankshaft of the internal combustion engine, not shown, wherein the camshaft is rotated relative to the crankshaft.
  • the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine can perform its optimum performance at the respective speed.
  • the camshaft adjuster 1 comprises a swivel adjuster 2 and a hydraulic valve 3.
  • the swivel adjuster 2 essentially comprises a rotor 4 and a stator 5 comprising the rotor 4.
  • the hydraulic valve 3 is designed to receive the rotor 4 as a helical central valve, which may also be referred to as a central screw. In other words, that the hydraulic valve 3 is at least partially included in a central adjuster opening 6 of the Schwenkverstellers 2 of this.
  • the hydraulic valve 3 has a housing 7, which is designed to flow through.
  • a housing 7 For hydraulic supply of the Schwenkverstellers 2 more connections A, B, P, T1, T2 are provided on the housing 7.
  • a piston 9 axially movable along a first longitudinal axis 8 of the hydraulic valve 3 is received in a central opening 10 of the housing 7.
  • the housing 7 is designed predominantly tubular shape.
  • the stator 5 of the Schwenkverstellers 2 is rotatably connected to a drive wheel 11 of the camshaft.
  • a stator base body 13 On inner sides 12 of a stator base body 13, radially inwardly extending webs 14 are formed at regular intervals, such that between each two adjacent webs 14, a gap 15 is formed.
  • the intermediate space 15 projecting a wing 16 of a rotor hub 17 of the rotor 4 is arranged.
  • the rotor hub 17 has a number of wings 16.
  • each gap 15 is divided into two pressure chambers.
  • a pressure medium generally a hydraulic fluid, introduced controlled by means of the hydraulic valve 3.
  • Each working port A, B is associated with a pressure chamber.
  • the pressure medium in the one pressure chamber or in the other pressure chamber is pressurized, while the other pressure chamber or a pressure chamber is relieved.
  • the discharge takes place via the first tank connection T1 or the second tank connection T2, whereby the hydraulic fluid can flow off via these tank connections T1, T2.
  • the piston 9 has a cylindrical shape and has throughflow openings, a first throughflow opening 18, a second throughflow opening 19 and a third throughflow opening 20.
  • Each flow-through opening 18, 19, 20 is carried out starting completely from a central channel 21 of the piston 9, so that via the central channel 21, the hydraulic fluid on the Throughflow openings 18, 19, 20 can flow into the working and tank connections A, B, T1, T2. So that a backflow of the hydraulic fluid into the central channel 21 is prevented when the pressure chambers are emptied, the throughflow openings 19, 20 assigned to the working ports A, B have check valves 22.
  • the piston 9 is positioned by means of an electromagnetic actuator 23 so that a corresponding admission of the pressure chambers can take place.
  • An actuator punch 24 is designed to engage on a plunger 25 having the central channel 21, so that with the aid of the actuator 23 the plunger 9 is positioned in the central opening 10.
  • an adapter 26 the housing 7 is carried at least partially radially comprising. Before mounting the camshaft with the housing 7, the adapter 26 is axially and radially movable. Between the housing 7 and the adapter 26, a tight fit tolerance is formed after assembly of the valve 3.
  • the swivel adjuster 2 comprises, in addition to the rotor 4 and the stator 5, a securing washer 27, which is designed for the axial securing of the rotor 4.
  • the locking washer 27 is rotatably connected to the stator 5 by means of fastening means 28.
  • the locking washer 27 serves to receive a locking pin 29 of a locking device 30 of the pivoting adjuster 2, wherein the locking device 30 further comprises a restoring element 31 in the form of a spiral spring and a cover element 32, which is designed for hydraulic actuation of the locking device 30.
  • the locking pin 29 is positioned in a receiving opening 33 of the drive wheel 11.
  • the adapter 26 is formed in a cylindrical shape and has at its end facing the rotor 4 34 an annular collar 35 which serves an axial stop of the rotor 4 and the drive wheel 11 and fixes the adapter 26 during assembly on a camshaft.
  • the sliding bearing 36 is designed in particular for radial support in the form of a floating sliding bearing 36. It serves on the one hand the bearing of the rotor 4 and on the other hand the bearing of the drive wheel 11, so that bearing surfaces are provided only between the sliding bearing 36 and the rotor 4 and the drive wheel 11. As Fig. 1 can be removed, a distance is formed between the sliding bearing 36 and the adapter 26. Thus, both components, the rotor 4 and the drive wheel 11 are stored inexpensively by means of a single sliding bearing 36. An over-determination on the outside of the adapter 26 is excluded by the radial distance between adapter 26 and plain bearing 36.
  • the adapter 26 has a groove-shaped recess 40.
  • the groove-shaped recess 40 can serve for a drainage of the hydraulic fluid via the first tank connection T1.
  • the drive wheel 11 has a positioning element 37, which is designed in the form of a spiral spring.
  • the positioning member 37 is secured by means of a pin 38 on the drive wheel 11.
  • the drive wheel 11 is rotatably connected to the stator 5 via the fastening means 28.
  • the rotor 4 is urged in a circumferential direction.
  • Fig. 3 shows the Schwenkversteller 2 in a perspective view in the assembly.
  • Fig. 4 is shown Schwenkversteller 2 of the camshaft adjuster 1 of a second embodiment. Between an adapter 26 facing formed inner surface 39 of the drive wheel 11 and the adapter 26 is too provided a radial distance each time. Bearing surfaces are provided only between the rotor 4 and the stator 5. On a separate annular plain bearing can be omitted. This reduces the assembly effort and additional costs can be further reduced due to the removal of the plain bearing. An over-determination on the outside of the adapter 26 is excluded by the radial distance between the adapter 26 and the drive wheel 11.

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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. Déphaseur d'arbre à cames, comprenant un déphaseur pivotant (2) et une soupape hydraulique (3) sollicitant hydrauliquement le déphaseur pivotant (2), et dans lequel la soupape hydraulique (3) peut être assemblée de façon calée en rotation à un arbre à cames pour faire tourner l'arbre à cames, et dans lequel le déphaseur pivotant (2) présente un stator (5) et un rotor (4) réalisé de façon coaxiale au stator (5), dans lequel le rotor (4) peut tourner par rapport au stator (5), et dans lequel le stator (5) est assemblé de façon calée en rotation à une roue d'entraînement (11) de l'arbre à cames, et dans lequel la soupape hydraulique (3) est réalisée de façon à pénétrer au moins partiellement dans le déphaseur pivotant (2), et dans lequel il est prévu un adaptateur (26) pour le positionnement axial relatif du rotor (4) et du stator (5), et dans lequel l'adaptateur (26) présente un bourrelet annulaire (35) à son extrémité (34) réalisée en position tournée vers le rotor (4), et dans lequel l'adaptateur (26) est réalisé pour le montage libre dans le déphaseur pivotant (2) et un assemblage fixe de l'adaptateur (26) avec le déphaseur pivotant (2) est réalisé après le montage de l'arbre à cames sur la soupape hydraulique (3), dans lequel le rotor (4) et/ou la roue d'entraînement (11) sont disposés en direction radiale sur le bourrelet annulaire (35) de l'adaptateur (26), dans lequel une distance radiale est ménagée entre le bourrelet (35) et la roue d'entraînement (11).
  2. Déphaseur d'arbre à cames selon la revendication 1, caractérisé en ce qu'une distance radiale est ménagée entre l'adaptateur (26) et le rotor (4).
  3. Déphaseur d'arbre à cames selon une revendication 1 ou 2, caractérisé en ce que la soupape hydraulique (3) est formée par une soupape centrale hélicoïdale.
  4. Adaptateur d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que l'adaptateur (26) est disposé entre l'arbre à cames et le rotor (4).
  5. Déphaseur d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce qu'un appui lisse radial (36) est réalisé entre le déphaseur pivotant (2) et l'adaptateur (26), dans lequel la distance radiale est prévue entre l'appui lisse (36) et l'adaptateur (26).
  6. Déphaseur d'arbre à cames selon la revendication 5, caractérisé en ce que l'appui lisse (36) est formé par un palier radial flottant.
  7. Déphaseur d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que l'adaptateur (26) présente au moins un évidement (40) traversant entièrement l'adaptateur (26) en direction radiale sur sa périphérie.
  8. Déphaseur d'arbre à cames selon la revendication 7, caractérisé en ce que l'évidement (40) est réalisé en forme de rainure.
EP17159488.0A 2016-03-14 2017-03-07 Déphaseur d'arbre à cames Active EP3219942B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201662307753P 2016-03-14 2016-03-14
US15/406,922 US10240493B2 (en) 2016-03-14 2017-01-16 Cam phaser

Publications (2)

Publication Number Publication Date
EP3219942A1 EP3219942A1 (fr) 2017-09-20
EP3219942B1 true EP3219942B1 (fr) 2019-09-11

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP17159488.0A Active EP3219942B1 (fr) 2016-03-14 2017-03-07 Déphaseur d'arbre à cames

Country Status (3)

Country Link
US (2) US10240493B2 (fr)
EP (1) EP3219942B1 (fr)
DE (1) DE102017104677A1 (fr)

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Publication number Priority date Publication date Assignee Title
WO2018019633A1 (fr) * 2016-07-27 2018-02-01 ECO Holding 1 GmbH Piston pour unité hydraulique d'un dispositif de réglage à pivotement et dispositif de réglage à pivotement pour un arbre à cames
US10947870B2 (en) * 2018-05-25 2021-03-16 Schaeffler Technologies AG & Co. KG Coupling for a camshaft phaser arrangement for a concentric camshaft assembly
US11118486B2 (en) * 2019-01-23 2021-09-14 Schaeffler Technologies AG & Co. KG Rotor timing feature for camshaft phaser
CN111485969B (zh) * 2019-01-28 2024-09-06 舍弗勒投资(中国)有限公司 凸轮轴相位调节器
US10883616B2 (en) * 2019-02-06 2021-01-05 ECO Holding 1 GmbH Control valve for cam phaser and method for mounting the control valve
US11092045B1 (en) * 2020-03-22 2021-08-17 ECO Holding 1 GmbH Control valve for cam phaser and method for mounting the control valve
US11326703B2 (en) * 2020-10-02 2022-05-10 ECO Holding 1 GmbH Oil control valve for a cam phaser of an internal combustion engine and a cam phaser comprising an oil control valve

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DE102006057492A1 (de) 2006-12-06 2008-06-12 Braun Gmbh Adapter, Verfahren zur Datenübertragung zwischen einer Zahnbürste und einem Endgerät sowie elektrische Zahnbürste
DE102008057492A1 (de) * 2008-11-15 2010-05-20 Daimler Ag Nockenwellenverstellvorrichtung
DE102010018202A1 (de) 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenverstellsystem für eine Brennkraftmaschine
JP5321926B2 (ja) 2011-02-18 2013-10-23 アイシン精機株式会社 弁開閉時期制御装置
JP6217438B2 (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
JP6369253B2 (ja) * 2014-09-16 2018-08-08 アイシン精機株式会社 弁開閉時期制御装置
JP6237574B2 (ja) * 2014-10-31 2017-11-29 アイシン精機株式会社 弁開閉時期制御装置
CN107614840B (zh) * 2015-06-02 2019-12-20 日立汽车系统株式会社 内燃机的气门正时控制装置

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Also Published As

Publication number Publication date
DE102017104677A1 (de) 2017-09-14
US20190170029A1 (en) 2019-06-06
US20170260884A1 (en) 2017-09-14
US10240493B2 (en) 2019-03-26
US10605128B2 (en) 2020-03-31
EP3219942A1 (fr) 2017-09-20

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