EP1073830A1 - Nockenwellenversteller für brennkraftmaschinen - Google Patents
Nockenwellenversteller für brennkraftmaschinenInfo
- Publication number
- EP1073830A1 EP1073830A1 EP99916918A EP99916918A EP1073830A1 EP 1073830 A1 EP1073830 A1 EP 1073830A1 EP 99916918 A EP99916918 A EP 99916918A EP 99916918 A EP99916918 A EP 99916918A EP 1073830 A1 EP1073830 A1 EP 1073830A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- camshaft
- inner body
- camshaft adjuster
- outer body
- internal combustion
- 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.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 14
- 238000004519 manufacturing process Methods 0.000 description 7
- 238000010276 construction Methods 0.000 description 3
- 230000000903 blocking effect Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000000149 penetrating effect Effects 0.000 description 2
- BGPVFRJUHWVFKM-UHFFFAOYSA-N N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] Chemical compound N1=C2C=CC=CC2=[N+]([O-])C1(CC1)CCC21N=C1C=CC=CC1=[N+]2[O-] BGPVFRJUHWVFKM-UHFFFAOYSA-N 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 239000000565 sealant Substances 0.000 description 1
- 230000007704 transition Effects 0.000 description 1
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
- 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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T74/00—Machine element or mechanism
- Y10T74/21—Elements
- Y10T74/2101—Cams
- Y10T74/2102—Adjustable
Definitions
- the invention relates to a camshaft adjuster for internal combustion engines according to the preamble of claim 1.
- Camshaft adjusters are as piston adjusters with axially displaceable pistons (DE 40 29 849 C2, DE 196 11 365 AI and DE 197 26 300 AI, Figure 1) as well as wing adjusters with wings that can be acted upon and pivoted in the circumferential direction (DE 197 26 300 AI, Figures 7 to 10) known.
- the camshaft adjuster is fixed in the front extension of the camshaft via a central clamping screw.
- the inner body of the camshaft adjuster which is non-rotatable relative to the camshaft and whose outer body is rotatable relative to the inner body and via which the drive connection to the crankshaft runs, is guided on the tensioning screw, regardless of a centering of the inner body relative to the camshaft that is independent of this.
- the invention is intended to design a camshaft adjuster of the type mentioned at the outset in such a way that the best possible centering of the camshaft adjuster is achieved, which at the same time creates the conditions for particularly simple and inexpensive production.
- the tensioning screw forms the element of the camshaft adjuster centering with respect to the camshaft, so that the latter does not have any additional elements in terms of its inner and outer body and also its lateral end elements in the form of covers centering support needed. This eliminates the need for axial undercuts or protrusions on the inner and outer body, which complicate production.
- the configuration according to the invention with centering of the entire camshaft adjuster, including the connection of the control device formed by the multi-way valve to the actuator, via the tensioning screw provides particularly favorable conditions for largely tolerance-free centering without excessive demands on production, with the best conditions for one best possible and vibration-free concentricity and with the lowest possible required gap dimensions in the transition between control spool and actuator.
- the inner and outer bodies can be designed to be flat on the end face, that is to say to form disc-shaped elements which are covered over the surface by means of ring covers, so that the covers only have to be clamped axially. It proves to be expedient if the cover connects radially on the inside to the centering collar of the cam shaft, so that there is sufficient radial overlap with the inside and outside body, which makes it possible to use simple sealants, if such are to be provided, the through the invention achieved exact centering with little play also has a favorable effect with regard to the reduction of leakages.
- FIG. 1 in a sectional view along line II in FIG. 2, a longitudinal section through a camshaft adjuster according to the invention, shown partially schematically, the camshaft adjuster being an extension of the camshaft of the placed internal combustion engine is arranged and is received by a chain box, also indicated only in its contours, provided on the front side to the internal combustion engine,
- Fig. 2 shows a section along line II-II in Figure 1, in a simplified representation
- FIG. 3 shows a largely corresponding, enlarged representation of the central region of the camshaft adjuster according to FIG. 1, which comprises the control slide.
- the camshaft adjuster according to FIGS. 1 to 3 is denoted overall by 1 and is shown in association with a camshaft 2 of an internal combustion engine 3, which is only indicated here in its outlines and on the end face associated with the illustrated end of the camshaft 2, a chain box 4 is provided , which is essentially only shown in its outline.
- the actuator 5 assigned to the camshaft adjuster 1 is provided, which is formed by an actuating magnet and which is screwed from the outside onto the front side of the chain case 4 opposite the 3r ⁇ nnkraftmaschine 3, as in ⁇ indicated.
- the steep drive 5 formed by an actuating magnet interacts with the armature 7 of a control slide 8, which is integrated in a central screw as a clamping screw S, via which the camshaft adjuster 1 is flanged on the end face to the camshaft 2, the clamping screw 9 being connected to the control Slider 8 of the camshaft adjuster 1 and the actuator 5 is coaxial with the camshaft 2.
- the outer body 111 has, over its circumference, radially inwardly projecting piston vanes 13, to which counter-vanes 14 are assigned on the part of the inner body 110, two counter-vanes 14 each delimiting an annular sector 15 in which a piston vane 13 of the outer body 111 lies, the outer body 111 with its associated piston wings 13 it forms a wing rotor that is adjustable relative to the inner body 110 over an angular range that is limited by the counter wing 14 of a ring sector 15 " .
- the xolbenfiügi 13 and counter wing 14 each delimit two working chambers 16, 17 which can be acted upon hydraulically, specifically in a controlled manner by means of the control slide 8. It can be seen from FIGS. 1 and 3 that the centering of the clamping screw 9 with respect to the camshaft 2 takes place via a centering collar 119 of the camshaft 2, which is supported directly against the circumference of the clamping screw 9.
- This centering between the clamping screw 9 and the camshaft 2 in the region of the end region adjacent to the camshaft 2 makes it possible to design the inner body 110 and the outer body 111 as flat disks, so that they have end faces lying in planes perpendicular to the axis of the camshaft 2 and also by plane covers 134, 135 designed as ring covers can be covered.
- the centering collar 119 cooperating with the circumference of the tensioning screw 9 thus enables the tensioning screw 9 to be aligned directly with the camshaft 2, so that, with simple manufacture, manufacturing which is easy to control with regard to the fit play is possible the camshaft adjuster 1 results.
- Pressure medium is supplied to the respective working chamber 16 or 17 in a manner not shown in more detail via a bearing point of the camshaft 2 in the housing of the internal combustion engine and radial bores 20 in the camshaft 2.
- an axial channel 21, 22 leads via camshaft 2 and inner body 110 to an annular space 23 in the inner body 110, which overlaps radial holes 24 in the clamping screw 9.
- the ring collar 26 remote from the camshaft 2 delimits with another ring collar 28 which is offset from the side remote from the camshaft 2, a further annular space 29, which is connected via a radial connection bore and an axial bore 30 to the receptacle 31, which via a Bottom-side limitation of the receptacle 31 penetrating bore 32 and a radial connecting channel 33 penetrating the centering collar 119 of the camshaft 2 into the chain case 4.
- the ring sectors containing the working chambers 16 and 17 are axially closed by the ring covers 134 and 135, which flatly cover parts of the end faces of the inner body 110 and the outer body 111 and which via axial clamping screws 38 against the flat end faces of the inner body 110 and the outer body 111 are kept tight.
- a locking element 39 in the form of a radial bolt is provided in the area of a piston vane 13 of the outer body 111, which points in the direction of the inner body 110 is spring-loaded and to which a latching opening 40 is assigned in the inner body 110.
- the latching opening 40 overlaps a radial channel 41 which opens out onto the chamber 16 and which starts from an annular groove 42 provided in the inner circumference of the inner body 110.
- This annular groove 42 overlaps with radial bores 43 in the axial wall of the tensioning screw 9, which forms the guide of the control slide 8 and delimits the receptacle 31 for the control slide 8.
- radial channels 44 are provided in the inner body 110, which open out on annular grooves 45, which overlap with radial bores 46 in the wall of the clamping screw 9.
- the necessary adjustment is carried out via the adjusting magnet 5 as a continuously controlling element, for example as a proportional magnet, i.e. by supplying or discharging pressure medium to one or the other chamber 16 or 17 .
- the control slide 8 returns to the starting position shown, in which the chamber 16 is connected to the return line via the annular space 29, so that the chamber 16 is emptied and at the same time the blocking element 39 forming bolts can be moved by the spring force in its blocking position.
- the chamber that is not pressurized is open to the return. 11
- a very short construction in the axial direction of the camshaft 2 camshaft adjuster is ben 1 gege ⁇ , wherein the inner body is braced 110 via the clamping screw 9 axially against the camshaft 2, and at the same time centered, the clamping screw 9 in turn also the centering for forms the inner body 110.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19817319 | 1998-04-18 | ||
DE19817319A DE19817319C2 (de) | 1998-04-18 | 1998-04-18 | Nockenwellenversteller für Brennkraftmaschinen |
PCT/EP1999/002495 WO1999054599A1 (de) | 1998-04-18 | 1999-04-14 | Nockenwellenversteller für brennkraftmaschinen |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1073830A1 true EP1073830A1 (de) | 2001-02-07 |
EP1073830B1 EP1073830B1 (de) | 2002-09-25 |
Family
ID=7865014
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99916918A Expired - Lifetime EP1073830B1 (de) | 1998-04-18 | 1999-04-14 | Nockenwellenversteller für brennkraftmaschinen |
Country Status (4)
Country | Link |
---|---|
US (1) | US6363896B1 (de) |
EP (1) | EP1073830B1 (de) |
DE (2) | DE19817319C2 (de) |
WO (1) | WO1999054599A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112007002915B4 (de) * | 2006-12-04 | 2020-10-29 | Daimler Ag | Verstelleinrichtung zur Phaseneinstellung einer Nockenwelle |
Families Citing this family (69)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19944535C1 (de) | 1999-09-17 | 2001-01-04 | Daimler Chrysler Ag | Nockenwellenversteller für Brennkraftmaschinen |
DE19958541A1 (de) * | 1999-12-04 | 2001-06-07 | Schaeffler Waelzlager Ohg | Vorrichtung zur Drehwinkelverstellung einer Nockenwelle |
US6481402B1 (en) * | 2001-07-11 | 2002-11-19 | Borgwarner Inc. | Variable camshaft timing system with pin-style lock between relatively oscillatable components |
DE10134320A1 (de) * | 2001-07-14 | 2003-01-23 | Ina Schaeffler Kg | Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle |
US20030033998A1 (en) * | 2001-08-14 | 2003-02-20 | Marty Gardner | Hybrid multi-position cam indexer having controls located in rotor |
DE10211467A1 (de) | 2002-03-15 | 2003-09-25 | Daimler Chrysler Ag | Nockenwellerversteller |
DE10211468A1 (de) * | 2002-03-15 | 2003-09-25 | Daimler Chrysler Ag | Nockenwellenversteller für eine Brennkraftmaschine |
US6745735B2 (en) * | 2002-04-19 | 2004-06-08 | Borgwarner Inc. | Air venting mechanism for variable camshaft timing devices |
US7556000B2 (en) * | 2002-05-21 | 2009-07-07 | Delphi Technologies, Inc. | Camshaft phaser having designated contact vane |
DE10233044A1 (de) * | 2002-07-20 | 2004-02-05 | Daimlerchrysler Ag | Vorrichtung zur relativen Drehwinkeländerung einer Welle zu einem Antriebsrad |
DE10303991A1 (de) * | 2003-02-01 | 2004-08-05 | Hydraulik-Ring Gmbh | Einrichtung zur Verstellung einer Nockenwelle einer Brennkraftmaschine eines Kraftfahrzeuges |
DE10322394A1 (de) * | 2003-05-12 | 2004-12-02 | Hydraulik-Ring Gmbh | Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen |
US6871621B2 (en) * | 2003-05-12 | 2005-03-29 | Hydraulik-Ring Gmbh | Camshaft adjuster for internal combustion engines of motor vehicles |
DE10326886A1 (de) | 2003-06-14 | 2004-12-30 | Daimlerchrysler Ag | Nockenwellensteller für eine Brennkraftmaschine |
US20050056249A1 (en) * | 2003-07-24 | 2005-03-17 | Matthias Heinze | Camshaft adjustment control device |
DE102004035035B4 (de) | 2003-07-24 | 2022-04-14 | Daimler Ag | Nockenwellenversteller für Brennkraftmaschinen |
DE10346443A1 (de) | 2003-10-07 | 2005-05-04 | Daimler Chrysler Ag | Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine |
DE10346448B4 (de) | 2003-10-07 | 2017-03-30 | Daimler Ag | Nockenwellenversteller für eine Brennkraftmaschine |
DE10346447B4 (de) * | 2003-10-07 | 2007-06-21 | Daimlerchrysler Ag | Verfahren zur Befestigung eines Nockenwellenverstellers an einer Nockenwelle einer Brennkraftmaschine |
US7255077B2 (en) * | 2003-11-17 | 2007-08-14 | Borgwarner Inc. | CTA phaser with proportional oil pressure for actuation at engine condition with low cam torsionals |
EP1596040B1 (de) * | 2004-05-14 | 2010-10-13 | Schaeffler KG | Nockenwellenversteller |
DE102004025215A1 (de) * | 2004-05-22 | 2005-12-08 | Ina-Schaeffler Kg | Nockenwellenversteller |
DE102004041430A1 (de) | 2004-08-27 | 2006-03-09 | Daimlerchrysler Ag | Nockenwellenversteller |
DE102004057634B4 (de) * | 2004-11-30 | 2011-07-07 | hofer mechatronik GmbH, 72644 | Verfahren für eine Startphase einer Brennkraftmaschine |
DE102004057633B4 (de) * | 2004-11-30 | 2014-05-15 | Hofer Mechatronik Gmbh | Rückschlagventil für einen Nockenwellenversteller |
DE102005011441B4 (de) * | 2005-03-12 | 2011-02-17 | Hofer Mechatronik Gmbh | Nockenwellenversteller für Brennkraftmaschinen |
DE102005034275B4 (de) * | 2005-07-22 | 2018-02-15 | Daimler Ag | Nockenwellenstellventilvorrichtung |
DE102005034276A1 (de) | 2005-07-22 | 2007-01-25 | Daimlerchrysler Ag | Nockenwellenstellvorrichtung |
DE102005039460A1 (de) * | 2005-08-20 | 2007-02-22 | Daimlerchrysler Ag | Stellvorrichtung für eine Brennkraftmaschine, insbesondere Nockenwellenstellvorrichtung |
DE102005048732A1 (de) | 2005-10-12 | 2007-04-19 | Schaeffler Kg | Hydraulisches Wegeventil |
DE102006005342A1 (de) * | 2006-02-07 | 2007-08-09 | Daimlerchrysler Ag | Verstelleinrichtung |
DE102007004197A1 (de) | 2007-01-27 | 2008-07-31 | Schaeffler Kg | System zur Verstellung des Stellwinkels eines Nockenwellenverstellers |
DE102007020525A1 (de) | 2007-05-02 | 2008-11-06 | Schaeffler Kg | Nockenwellenversteller für eine Brennkraftmaschine mit integriertem Ventilschieber |
DE102007020526A1 (de) | 2007-05-02 | 2008-11-06 | Schaeffler Kg | Nockenwellenversteller für eine Brennkraftmaschine mit verbesserter Ausführung der Druckräume |
DE102007020527A1 (de) | 2007-05-02 | 2008-11-06 | Schaeffler Kg | Nockenwellenversteller |
DE102007058491A1 (de) | 2007-12-05 | 2009-06-10 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102008030057B4 (de) | 2008-06-27 | 2018-01-25 | Hilite Germany Gmbh | Nockenwellenverstelleinrichtung |
DE202008018657U1 (de) | 2008-08-21 | 2017-11-20 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
DE102008039038B4 (de) | 2008-08-21 | 2021-01-28 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
US20100084019A1 (en) * | 2008-10-08 | 2010-04-08 | Schaeffler Kg | Central spool valve |
DE102008051386A1 (de) * | 2008-10-11 | 2010-04-15 | Daimler Ag | Phasenverstellvorrichtung |
DE102010015716A1 (de) | 2009-04-24 | 2010-10-28 | Schaeffler Technologies Gmbh & Co. Kg | Integriertes Innennockenwellenschieberventil |
DE102009029389A1 (de) | 2009-09-11 | 2011-03-24 | Robert Bosch Gmbh | Nockenwellenversteller |
DE102009051519A1 (de) * | 2009-10-31 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenverstellanordnung |
EP2510200B1 (de) | 2009-12-11 | 2015-05-06 | Schaeffler Technologies AG & Co. KG | Schrittrotor für nockenwellenversteller |
DE102010044637A1 (de) * | 2010-09-07 | 2012-03-08 | Hydraulik-Ring Gmbh | Zentralventil |
JP5585832B2 (ja) * | 2010-09-10 | 2014-09-10 | アイシン精機株式会社 | 弁開閉時期制御装置 |
US8397687B2 (en) * | 2010-10-26 | 2013-03-19 | Delphi Technologies, Inc. | Axially compact camshaft phaser |
DE102010063703A1 (de) * | 2010-12-21 | 2012-06-21 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenversteller |
CN102367751B (zh) * | 2011-09-20 | 2013-07-24 | 宁波诺依克电子有限公司 | Vvt发动机控制阀及其控制方法 |
WO2013063757A1 (zh) * | 2011-11-01 | 2013-05-10 | Lio Pang-Chian | 驱动装置及可变行程时序压力控制系统 |
DE102012201573A1 (de) | 2012-02-02 | 2013-08-08 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
DE102012202520B4 (de) * | 2012-02-20 | 2016-03-24 | Schaeffler Technologies AG & Co. KG | Zentralventil für einen Nockenwellenversteller |
WO2013128295A2 (en) | 2012-02-28 | 2013-09-06 | Schaeffler Technologies AG & Co. KG | Electric phasing of a concentric camshaft |
DE102012204617A1 (de) | 2012-03-22 | 2013-09-26 | Schaeffler Technologies AG & Co. KG | Steuerventil eines Nockenwellenverstellers |
DE102012210178B4 (de) | 2012-06-18 | 2016-05-19 | Schaeffler Technologies AG & Co. KG | Steuerventil eines Nockenwellenverstellers |
KR101364505B1 (ko) | 2012-07-05 | 2014-02-18 | 덴소코리아오토모티브 주식회사 | 밸브 타이밍 조절장치 |
DE102013100890B4 (de) | 2013-01-29 | 2018-05-17 | Hilite Germany Gmbh | Schwenkmotorversteller mit einer als Zentralventil ausgeführten Zentralschraube |
DE102014216119A1 (de) | 2013-08-22 | 2015-02-26 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren und Vorrichtung zum Wickeln einer Rückstellfeder mit einem zweiteiligen Rotor für einen Nockenversteller |
JP6295720B2 (ja) | 2014-02-27 | 2018-03-20 | アイシン精機株式会社 | 弁開閉時期制御装置 |
DE102014204566B4 (de) * | 2014-03-12 | 2021-05-12 | Schaeffler Technologies AG & Co. KG | Zentralventil für einen Nockenwellenversteller mit Mittenverriegelung |
US10072537B2 (en) | 2015-07-23 | 2018-09-11 | Husco Automotive Holdings Llc | Mechanical cam phasing system and methods |
JP6834382B2 (ja) | 2016-11-14 | 2021-02-24 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP6834381B2 (ja) | 2016-11-14 | 2021-02-24 | アイシン精機株式会社 | 弁開閉時期制御装置 |
JP6769253B2 (ja) | 2016-11-14 | 2020-10-14 | アイシン精機株式会社 | 弁開閉時期制御装置 |
US10557383B2 (en) | 2017-01-20 | 2020-02-11 | Husco Automotive Holdings Llc | Cam phasing systems and methods |
US10900387B2 (en) | 2018-12-07 | 2021-01-26 | Husco Automotive Holdings Llc | Mechanical cam phasing systems and methods |
US11946394B2 (en) * | 2019-07-25 | 2024-04-02 | ECO Holding 1 GmbH | Method for producing a cam phaser and cam phaser |
DE102021128258A1 (de) | 2021-10-29 | 2023-05-04 | Schaeffler Technologies AG & Co. KG | Steuerventil |
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US4091776A (en) * | 1974-04-04 | 1978-05-30 | Rockwell International Corporation | Fluid actuated timing mechanism |
US5058539A (en) | 1989-09-20 | 1991-10-22 | Atsugi Unisia Corporation | Valve timing adjusting system for internal combustion engine |
DE3937644A1 (de) * | 1989-11-11 | 1991-05-16 | Bayerische Motoren Werke Ag | Vorrichtung zur hydraulischen drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle fuer brennkraftmaschinen |
US5088456A (en) * | 1990-01-30 | 1992-02-18 | Atsugi-Unisia Corporation | Valve timing control system to adjust phase relationship between maximum, intermediate, and minimum advance position |
DE4116169A1 (de) * | 1991-05-17 | 1992-11-19 | Bosch Gmbh Robert | Vorrichtung zur verstellung der drehwinkelzuordnung einer nockenwelle zu ihrem antriebselement |
DE4237193A1 (de) * | 1992-11-04 | 1994-05-05 | Bosch Gmbh Robert | Verfahren zur Ansteuerung einer Einrichtung zum relativen Verdrehen einer Welle und Einrichtung zum relativen Verdrehen der Welle einer Brennkraftmaschine |
DE19611365C2 (de) * | 1996-03-22 | 1999-09-23 | Daimler Chrysler Ag | Vorrichtung zur relativen Winkelverstellung einer Nockenwelle |
US5870983A (en) * | 1996-06-21 | 1999-02-16 | Denso Corporation | Valve timing regulation apparatus for engine |
-
1998
- 1998-04-18 DE DE19817319A patent/DE19817319C2/de not_active Expired - Lifetime
-
1999
- 1999-04-14 DE DE59902848T patent/DE59902848D1/de not_active Expired - Lifetime
- 1999-04-14 US US09/673,772 patent/US6363896B1/en not_active Expired - Lifetime
- 1999-04-14 EP EP99916918A patent/EP1073830B1/de not_active Expired - Lifetime
- 1999-04-14 WO PCT/EP1999/002495 patent/WO1999054599A1/de active IP Right Grant
Non-Patent Citations (1)
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112007002915B4 (de) * | 2006-12-04 | 2020-10-29 | Daimler Ag | Verstelleinrichtung zur Phaseneinstellung einer Nockenwelle |
Also Published As
Publication number | Publication date |
---|---|
EP1073830B1 (de) | 2002-09-25 |
DE59902848D1 (de) | 2002-10-31 |
WO1999054599A1 (de) | 1999-10-28 |
DE19817319C2 (de) | 2001-12-06 |
US6363896B1 (en) | 2002-04-02 |
DE19817319A1 (de) | 1999-10-28 |
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