WO2020094173A1 - Déphaseur d'arbres à cames hydraulique - Google Patents

Déphaseur d'arbres à cames hydraulique Download PDF

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Publication number
WO2020094173A1
WO2020094173A1 PCT/DE2019/100822 DE2019100822W WO2020094173A1 WO 2020094173 A1 WO2020094173 A1 WO 2020094173A1 DE 2019100822 W DE2019100822 W DE 2019100822W WO 2020094173 A1 WO2020094173 A1 WO 2020094173A1
Authority
WO
WIPO (PCT)
Prior art keywords
pressure medium
rotor
camshaft adjuster
hydraulic camshaft
working chambers
Prior art date
Application number
PCT/DE2019/100822
Other languages
German (de)
English (en)
Inventor
Enno Schmitt
Jürgen Weber
Rainer Ottersbach
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Priority to CN201980073032.5A priority Critical patent/CN113039348A/zh
Priority to US17/292,052 priority patent/US20210396160A1/en
Publication of WO2020094173A1 publication Critical patent/WO2020094173A1/fr

Links

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
    • 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
    • F01L2001/3443—Solenoid driven 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
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a hydraulic camshaft adjuster according to the preamble of claim 1.
  • Hydraulic camshaft adjusters are used in internal combustion engines to adapt a load state of the internal combustion engine and thus to increase the efficiency of the internal combustion engine. Hydraulic camshaft adjusters are known from the prior art, which operate according to the vane cell principle. The basic structure of these camshaft adjusters generally has a stator which can be driven by a crankshaft of an internal combustion engine and a rotor which is connected to the camshaft of the internal combustion engine in a rotationally fixed manner.
  • An annular space is provided between the stator and the rotor, which is subdivided into a plurality of working chambers by projections, which are connected to the stator in a rotationally fixed manner, and which are each divided into two by a wing projecting radially outwards from the rotor Pressure chambers are divided.
  • Hydraulic camshaft adjusters with a central locking are known, in which the rotor can also be locked in a middle position in addition to the respective end positions, in particular to facilitate engine starting.
  • hydraulic camshaft adjusters are known which, as so-called “smart phasers”, have a reservoir for the hydraulic oil.
  • DE 10 2012 201 558 A1 describes a hydraulic camshaft adjuster with a stator, a rotor which is arranged concentrically to the stator and rotatable about a common axis of rotation and is mounted with one or more voids.
  • Lumen accumulator (s) for holding a hydraulic fluid for hydraulically actuating the camshaft adjuster are known, the volume accumulator (s) having an outlet in the direction of the axis of rotation.
  • DE 10 2006 012 733 A1 discloses a hydraulic circuit for a hydraulic camshaft adjuster with a switching valve, in which, in addition to pressurizing the working chambers, an additional force from the alternating torques of the camshaft is used to counter the rotor of the hydraulic camshaft adjuster To twist the stator.
  • EP 1 221 540 A2 discloses a hydraulic camshaft adjuster for adjusting the timing of gas exchange valves of an internal combustion engine, in which the alternating torques of the camshaft and the hydraulic oil pressure in the working chambers are used to turn the rotor relative to the stator.
  • camshaft adjuster known from the prior art is, however, relatively complex owing to the large number of control channels and is associated with correspondingly high production costs.
  • camshaft adjusters have already been largely optimized in terms of production technology, so that the manufacturing costs of the known construction can only be reduced insignificantly.
  • the object of the invention is to propose a hydraulic camshaft adjuster which has no functional disadvantages to the known solutions, but is less complex and can be manufactured more cost-effectively.
  • a hydraulic camshaft adjuster for variable adjustment of the timing of gas exchange valves of an internal combustion engine, with a stator and a rotor which can be rotated relative to the stator, with several hydraulic spaces being removed between the stator and the rotor. are formed, which are separated by radially inwardly projecting webs of the stator, with blades which project radially outwardly and which divide the hydraulic spaces into a first group of working chambers and a second group of working chambers with opposite directions of action, as well as with a pressure medium pump with which a pressure medium can be applied to the working chambers, and with a central valve for controlling the oil pressure of the working chambers.
  • the pressure medium pump is connected directly to the working chambers via a respective pressure medium channel, that the central valve is connected to the working chambers via drainage channels, and that the central valve controls only the pressure medium outflow from the working chambers.
  • a first check valve is arranged in a first pressure medium channel, which connects the pressure medium pump with the first working chamber of the hydraulic camshaft adjuster, and in a second pressure medium channel, which connects the pressure medium pump with the second working chamber of the hydraulic camshaft adjuster connects, a second check valve is arranged.
  • the check valves can regulation in the working chambers are improved and, in particular, it is prevented that there is an undesired outflow of pressure medium from the working chambers.
  • the check valves are arranged or formed in a check valve plate of the hydraulic camshaft adjuster.
  • a non-return valve plate enables the non-return valves to be integrated particularly easily and inexpensively into the pressure medium supply to the working chambers of the hydraulic camshaft adjuster.
  • the check valve plate can be easily and inexpensively manufactured as a stamped part in order to further reduce the costs for the hydraulic camshaft adjuster.
  • the pressure medium channels are formed at least in sections in the check valve plate.
  • a check valve is arranged in the pressure medium channels for each of the first working chambers and for each of the second working chambers.
  • the inflow of pressure medium into each of the first pressure chambers and each of the second pressure chambers can be controlled by a corresponding plurality of check valves, as a result of which the pressure pulsations can be further reduced.
  • the hydraulic camshaft adjuster has a drive wheel with a drive toothing, wherein the pressure medium channels run at least in sections in the drive wheel.
  • the drive wheel can easily be hydraulically connected to the oil supply from the pressure medium pump via appropriate supply holes.
  • the oil supply ducts can be made comparatively short, which improves the adjustment times of the hydraulic camshaft adjuster and the pressure medium requirement is lower overall.
  • the drive wheel is manufactured as a sintered component.
  • the pressure medium channels can be easily and inexpensively formed in the drive wheel, a subsequent mechanical machining being eliminated or at least greatly reduced.
  • the pressure medium channels can be introduced into the drive wheel in a substantially cost-neutral manner, which further reduces the costs for the hydraulic camshaft adjuster.
  • the rotor is designed as a built rotor and has a first rotor component and a second rotor component.
  • the two rotor components are preferably connected to one another via a plurality of pin connections. Since the rotor in the proposed hydraulic camshaft adjuster can be designed without oil supply channels, the geometry of the rotor is comparatively simple and can be manufactured with comparatively little tool expenditure.
  • a diverting sleeve is provided between the rotor and the central valve, which redirects the pressure medium drainage channels at different levels, so that a simple and inexpensive slide valve can be used as the central valve.
  • the rotor components are manufactured as stamped parts.
  • a built rotor can significantly reduce the complexity for the two rotor halves, so that an inexpensive stamped part can be used instead of a comparatively expensive turned or sintered component. This further reduces the manufacturing costs for the hydraulic camshaft adjuster.
  • a sintered rotor can also be used, in the case of a sintered rotor the diverting sleeve between the rotor and the central valve can be omitted.
  • the pressure medium channels run on one of the end faces of the sintered rotor. In this way, the pressure medium channels can be introduced into the sintered blank (green body), which means that subsequent machining is not required.
  • a pressure medium path leads from the working chambers via the central valve, a check valve being arranged in the pressure medium path downstream of the central valve.
  • the pressure medium return can be connected to the pressure medium inlet in a simple manner by means of a check valve downstream of the central valve, as a result of which the oil discharged from the pressure chambers is directed back to the supply side. This can reduce the risk of air being sucked in if there is an insufficient supply.
  • the check valve can also be arranged downstream of the pump inlet of the pressure medium pump.
  • FIG. 1 shows a first section through a hydraulic camshaft adjuster according to the invention
  • Fig. 2 shows a second section through a hydraulic according to the invention
  • Camshaft adjuster 3 shows an exploded view of a hydraulic camshaft adjuster according to the invention
  • Fig. 4 is a hydraulic circuit diagram for a hydraulic according to the invention
  • FIG. 5 shows a further sectional illustration of a hydraulic camshaft adjuster in order to visualize the pressure medium supply into the first working chamber or the pressure medium outflow from the second working chamber when the rotor is adjusted.
  • the hydraulic camshaft adjuster 1 has a stator 2, in which a rotor 3 is arranged, which can be rotated relative to the stator 2.
  • the stator 2 has a plurality of webs 6 running radially inwards.
  • the rotor 3 has a rotor hub 8, from which a plurality of vanes 7 protrude in the radial direction.
  • a plurality of flydraulic spaces 9 are formed between the stator 2 and the rotor 3, which are each divided into a first working chamber 10 and a second working chamber 11 by the blades 7 of the rotor 3.
  • a hydraulic camshaft adjuster 1 with four hydraulic chambers 9 and a rotor 3 with four blades 7 is shown, but embodiments with fewer, in particular with three hydraulic chambers or more, in particular with five hydraulic chambers, are also possible .
  • a chamber drain 12 is formed on the rotor 3, via which the pressure medium, in particular the engine oil of the internal combustion engine, can flow out of the working chambers 10, 11.
  • the hydraulic camshaft adjuster 1 also has a central valve 5, via which the pressure medium outflow from the working chambers 10, 11 can be controlled. Between the rotor 3 and the central valve 5 there is a diverting sleeve 13, which from the working chambers 10, 11 flowing pressure medium redirected accordingly.
  • the central valve 5 can be displaced in the axial direction against the spring force of a spring 16 via an actuator 4, the spring 16 being arranged in a piston 15 of the central valve 5.
  • a bushing 14 is inserted, on which the piston 15 and the guide sleeve 13 are supported.
  • the stator 2 is connected in a rotationally fixed manner via an intermediate plate 32 to a drive wheel 23 of the hydraulic camshaft adjuster, which can be connected to and driven by the crankshaft of an internal combustion engine via a chain or a toothed belt.
  • the drive wheel 23 has a drive toothing 24 on its circumference, with which a chain or a toothed belt can be positively received.
  • a check valve plate 21 is arranged between the drive wheel 23 and the intermediate plate 32, which enables a direct supply of pressure medium to the working chambers 10, 11 from a pressure medium pump 25 and prevents an undesired outflow of pressure medium from the working chambers 10, 11.
  • FIG. 2 shows a further section through a hydraulic camshaft adjuster 1 according to the invention.
  • the rotor 3 is connected in a rotationally fixed manner to the camshaft 17 and the pressure medium is supplied via bores in the drive wheel 23.
  • the oil supply 19 runs through the camshaft 17, at least in sections as a flute shaft, pressure medium channels in the drive wheel 23 directly to the working chambers 10, 11.
  • the pressure medium supply is not controlled by the central valve 5, since this exclusively controls the pressure medium return the working chambers 10, 11 controls.
  • a check valve 18 is provided in the pressure medium return downstream of the central valve 5 and makes it possible to feed the pressure medium flowing back into the pressure medium supply, provided that the pressure in the pressure medium return is above the pressure in the respective channel of the pressure medium supply.
  • FIG. 3 an inventive hydraulic camshaft adjuster 1 is shown in an exploded view.
  • the hydraulic camshaft adjuster 1 comprises a stator 2 and a rotor 3 accommodated in the stator 2 and rotatable relative to the stator about a common axis of rotation.
  • the rotor 3 comprises a first rotor component 34 and a second rotor component 35, the two rotor components 34,
  • a plurality of outflow channels 28, 29 are formed in the rotor 3, which connect the respective working chambers 10, 11 to the central valve 5 in such a way that the pressure medium outflow from the working chambers 10, 11 can be controlled by the central valve 5.
  • a guide sleeve is arranged, which deflects the returning pressure medium in such a way that the pressure medium can be returned from the central valve 5 via a check valve 18 into the area of the pressure medium supply.
  • a plurality of hydraulic chambers 9 are formed between the stator 2 and the rotor 3, which are divided by the vanes 7 of the rotor 3 in a first working chamber 10 and a second working chamber 11 with different directions of action with respect to the adjustment of the hydraulic camshaft adjuster 1.
  • the working chambers 10, 11 are delimited in the axial direction on the side facing away from the stator 2 by an intermediate plate 32.
  • the intermediate plate has a plurality of openings, of which exactly one opening preferably opens into one of the first working chambers 10 or one of the second working chambers 11.
  • the openings can be closed by a non-return valve 30, 31 in a non-return valve plate 21 in order to avoid an undesired outflow of pressure medium from the first working chambers 10 or the second working chambers 11.
  • the check valve plate 21 is clamped between the intermediate plate 32 and a drive wheel 23 of the hydraulic camshaft adjuster 1, the pressure medium supply channels preferably being formed in the drive wheel 23.
  • the pressure medium supply channels can be formed at least in sections in the check valve plate 21.
  • FIG. 4 shows a hydraulic circuit diagram of a hydraulic camshaft adjuster 1 according to the invention.
  • the circuit diagram shown in FIG. 4 shows one of the pairs of working chambers 10, 11. Three or four pairs of working chambers 10, 11 are preferably provided in the hydraulic camshaft adjuster 1.
  • It is a pressure medium pump 25 is connected via a first pressure medium supply channel 26 to a first working chamber 10 of the hydraulic camshaft adjuster 1 and via a second pressure medium supply channel 27 to a second working chamber 11.
  • the first working chamber 10 and the second working chamber are delimited by webs 6 (not shown in FIG. 4) on the stator and are hydraulically separated from one another by a wing 7 of the rotor 7.
  • the two working chambers 10, 11 have different directions of action with respect to the adjustment of the rotor 3.
  • a first check valve 30 is arranged in the first pressure medium supply channel 26 and prevents pressure medium from flowing out of the first working chamber 10 in the direction of the pressure medium pump 25.
  • a second check valve 31 is arranged, which prevents an undesired outflow of pressure medium from the second working chamber 11.
  • FIG. 5 A hydraulic adjustment of the rotor 3 of the hydraulic camshaft adjuster 1 is shown in FIG. 5.
  • the camshaft alternating torque acts in the intended direction of adjustment.
  • the camshaft alternating torque presses the pressure medium from the first working chamber 10 via the rotor 3 via the open outlets 28 of the central valve 5 and the optional check valve 18 for connecting the pressure medium pump 25.
  • the pressure medium is conveyed via the pressure medium supply channel 27 into the second working chamber 11, since this sucks in the pressure medium.
  • the check valve 31 closes and prevents the rotor 3 from rotating against the desired adjustment direction.
  • the second working chamber 11 is pressurized by the pressure medium pump 25 via the pressure medium supply channel 27.
  • the pressure medium from the first working chamber 10 can be nal flow 28, whereby the volume in the first working chamber 10 is reduced and the rotor 3 is rotated in direction A.
  • the check valve 30 in the first pressure medium supply channel 26 is closed and in this way prevents the pressure medium from flowing back in the direction of the pressure medium pump 25.
  • the central valve 5 is in a first switching position in which the first working chamber 10 is depressurized and the drain channel 28 is connected to a pressure medium reservoir.

Landscapes

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

Abstract

L'invention concerne un déphaseur d'arbres à cames (1) pour le déphasage variable des temps de commande de soupapes d'échange de gaz d'un moteur à combustion interne, comprenant un stator (2) et un rotor (3) pouvant tourner par rapport au stator (2), plusieurs chambres hydrauliques (9) étant formées entre le stator (2) et le rotor (3), lesquelles sont séparées par des nervures (6) du stator (2) faisant saillie vers l'intérieur, des aubes (7) faisant saillie radialement vers l'extérieur étant formées sur le rotor (3), lesquelles divisent les chambres hydrauliques (9) en respectivement un premier groupe de chambres hydrauliques (10) et un deuxième groupe de chambres hydrauliques (11) ayant une direction d'action opposée, ainsi que comprenant une pompe à fluide sous pression (25) au moyen de laquelle les chambres hydrauliques (10, 11) peuvent être chargée par un fluide sous pression, et comprenant une soupape centrale (5) pour la commande de la pression d'huile dans les chambres hydrauliques (10, 11). Selon l'invention, la pompe à fluide sous pression (25) est connectée directement aux chambres hydrauliques (10, 11) par respectivement un canal de fluide hydraulique (26, 27), la soupape centrale (5) est connectée aux chambres hydrauliques (10, 11) par des canaux d'écoulement (28, 29), et la soupape centrale (5) commande exclusivement l'écoulement de fluide sous pression des chambres hydrauliques (10, 11).
PCT/DE2019/100822 2018-11-07 2019-09-18 Déphaseur d'arbres à cames hydraulique WO2020094173A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201980073032.5A CN113039348A (zh) 2018-11-07 2019-09-18 液压凸轮轴相位器
US17/292,052 US20210396160A1 (en) 2018-11-07 2019-09-18 Hydraulic camshaft adjuster

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018127733.4 2018-11-07
DE102018127733.4A DE102018127733A1 (de) 2018-11-07 2018-11-07 Hydraulischer Nockenwellenversteller

Publications (1)

Publication Number Publication Date
WO2020094173A1 true WO2020094173A1 (fr) 2020-05-14

Family

ID=68072086

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2019/100822 WO2020094173A1 (fr) 2018-11-07 2019-09-18 Déphaseur d'arbres à cames hydraulique

Country Status (4)

Country Link
US (1) US20210396160A1 (fr)
CN (1) CN113039348A (fr)
DE (1) DE102018127733A1 (fr)
WO (1) WO2020094173A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN117795179A (zh) * 2021-08-27 2024-03-29 舍弗勒技术股份两合公司 凸轮轴相位调节器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1221540A2 (fr) 2001-01-08 2002-07-10 BorgWarner Inc. Commande multi-mode pour dispositif de calage variable d'arbre à cames
US20070028874A1 (en) * 2005-08-02 2007-02-08 Borgwarner Inc. Mapping temperature compensation limits for PWM control of VCT phasers
DE102006012733A1 (de) 2006-03-17 2007-09-20 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102012201558A1 (de) 2012-02-02 2013-08-08 Schaeffler Technologies AG & Co. KG Gestaltung eines Tankanschlusses in einem Nockenwellenversteller mit Volumenspeicher
DE102012211526A1 (de) * 2012-07-03 2014-01-09 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller mit interner Dämpfung
US20160130988A1 (en) * 2013-06-19 2016-05-12 Borgwarner Inc. Variable camshaft timing mechanism with a lock pin engaged by oil pressure
DE102016202960A1 (de) * 2016-02-25 2017-08-31 Schaeffler Technologies AG & Co. KG Nockenwellenversteller für eine Brennkraftmaschine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010019530A1 (de) * 2010-05-06 2011-11-10 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller und U-förmiges Dichtelement zum Abdichten einer radialen Fläche eines Flügels eines Nockenwellenverstellers
DE102010022896B4 (de) * 2010-06-07 2021-11-11 Schaeffler Technologies AG & Co. KG Druckmittelbetätigbare Nockenwellenverstelleinrichtung für eine Brennkraftmaschine
DE102013226445B4 (de) * 2013-12-18 2020-11-26 Schaeffler Technologies AG & Co. KG Nockenwellenzentrierung im geteilten Rotor eines hydraulischen Nockenwellenverstellers und zugehöriges Herstellungsverfahren

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1221540A2 (fr) 2001-01-08 2002-07-10 BorgWarner Inc. Commande multi-mode pour dispositif de calage variable d'arbre à cames
US20070028874A1 (en) * 2005-08-02 2007-02-08 Borgwarner Inc. Mapping temperature compensation limits for PWM control of VCT phasers
DE102006012733A1 (de) 2006-03-17 2007-09-20 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102012201558A1 (de) 2012-02-02 2013-08-08 Schaeffler Technologies AG & Co. KG Gestaltung eines Tankanschlusses in einem Nockenwellenversteller mit Volumenspeicher
DE102012211526A1 (de) * 2012-07-03 2014-01-09 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller mit interner Dämpfung
US20160130988A1 (en) * 2013-06-19 2016-05-12 Borgwarner Inc. Variable camshaft timing mechanism with a lock pin engaged by oil pressure
DE102016202960A1 (de) * 2016-02-25 2017-08-31 Schaeffler Technologies AG & Co. KG Nockenwellenversteller für eine Brennkraftmaschine

Also Published As

Publication number Publication date
US20210396160A1 (en) 2021-12-23
DE102018127733A1 (de) 2020-05-07
CN113039348A (zh) 2021-06-25

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