WO2003078804A1 - Nockenwellenversteller für eine brennkraftmaschine - Google Patents
Nockenwellenversteller für eine brennkraftmaschine Download PDFInfo
- Publication number
- WO2003078804A1 WO2003078804A1 PCT/EP2003/001772 EP0301772W WO03078804A1 WO 2003078804 A1 WO2003078804 A1 WO 2003078804A1 EP 0301772 W EP0301772 W EP 0301772W WO 03078804 A1 WO03078804 A1 WO 03078804A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- guide sleeve
- camshaft
- control piston
- camshaft adjuster
- adjuster according
- Prior art date
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
-
- 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
- F01L1/34403—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft
- F01L1/34406—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 helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
-
- 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
Definitions
- the invention relates to a camshaft adjuster according to the preamble of claim 1.
- An actuating unit for angular adjustment of a camshaft can be controlled via the control piston, the actuating unit having an inner body formed by an impeller in a rotationally fixed manner with the camshaft and an outer body rotatably mounted to the camshaft and formed by a sprocket wheel, via which a drive connection from the crankshaft to the camshaft runs.
- the control piston is slidably guided in a receptacle of a central clamping screw in the axial direction of the central clamping screw.
- the inner body is axially clamped against the camshaft via the central clamping screw.
- the invention is based in particular on the object of providing a generic camshaft adjuster for an internal combustion engine with reduced tolerances and at the same time reduced production costs. It is solved according to the invention by the features of claim 1. Further refinements result from the subclaims.
- the invention relates to a camshaft adjuster for an internal combustion engine with a hydraulic control piston, with which an actuating unit for angular adjustment of a camshaft can be controlled.
- control piston be guided in a separate guide sleeve.
- the guide sleeve can be designed specifically for its function and faults caused by other functions can be avoided.
- Control edges can be introduced to the guide sleeve in a structurally simple, inexpensive and particularly precise manner, as a result of which tolerances can be reduced overall and costs can be saved.
- Functional decoupling can be achieved and modularization and unification can be achieved with the functional decoupling, e.g. can be used for at least several similar guide sleeves for different internal combustion engines.
- the guide sleeve is arranged in the camshaft, simple oil guidance can be achieved and, in particular, existing oil guides can be used essentially unchanged. Furthermore, the arrangement of the guide sleeve in the camshaft enables an advantageous precise position assignment of the control piston to the camshaft.
- the guide sleeve can, however, also be arranged in an impeller, a central tensioning screw or another component which appears useful to the person skilled in the art.
- the guide sleeve be inserted, as a result of which it can be designed and assembled particularly simply and inexpensively.
- the guide sleeve could also be screwed on.
- the guide sleeve can also be held in a component receiving the guide sleeve by various non-positive, positive and / or material connections that appear to be useful to the person skilled in the art, for example by a welded connection, adhesive connection, press connection, screw connection, etc.
- the guide sleeve pressed in or is the guide sleeve held by a press connection the guide sleeve can be attached inexpensively, and in particular the attachment can advantageously be integrated into existing assembly processes of internal combustion engines.
- the press connection is particularly advantageously produced by a heat-related shrinking process.
- At least one channel is introduced at least one interface between the guide sleeve and a component receiving the guide sleeve in the longitudinal and / or in the circumferential direction of the guide sleeve, additional channels which are difficult to manufacture can be avoided in other functional components, such as in particular in the camshaft, and costs can be saved, and in particular if the channel is formed by a recess made in the guide sleeve.
- a distribution of pressure and / or control means is realized via the channel.
- control piston be held captively in the guide sleeve by means of a securing element.
- the guide sleeve and the control piston can advantageously be preassembled as a unit, checked for their function, transported and assembled.
- a spring acting on the control piston is arranged in the guide sleeve, whereby a simple control of the control piston via an actuator generating tensile or compressive forces alone can be realized.
- Fig. 1 shows a section of an internal combustion engine 20 of a motor vehicle, not shown, with a camshaft adjuster according to the invention.
- the camshaft adjuster has a hydraulic control piston 10 with which an actuating unit for angular adjustment of a camshaft 16 can be controlled.
- the control piston 10 is guided in a separate guide sleeve 11, which has control edges formed by four radial bores 12, 13, 14, 15, the radial bores 12, 15 being arranged offset in the circumferential direction from the radial bores 13, 14.
- the guide sleeve 11 is inserted or pressed into a concentric recess 21, which extends from one end of the camshaft 16 in the axial direction. Before the guide sleeve 11 is inserted into the recess 21, the camshaft 16 is heated, the camshaft 16 and thus the recess 21 expanding. The guide sleeve 11 is inserted into the recess 21 in the heated state, namely until it strikes the bottom of the recess 21 with its end face facing the camshaft 16. When the cam shaft 16 narrows the recess 21, and the guide sleeve 11 is pressed into the recess 21.
- the camshaft 16 is mounted in a cylinder head 23 of the internal combustion engine 20 via a main bearing 22 and is fixed in the axial direction to the control piston 10 via a cover 24 screwed onto the cylinder head 23.
- pressure medium is supplied via a radial bore 25 and via an axial bore 26 in the camshaft 16 and via interfaces 17, 55 between the guide sleeve 11 and the camshaft 16, namely via an axially extending channel, not shown, and via an annular groove 47, radial bores 27, 28 are fed to the guide sleeve 11, via which the pressure medium is guided into an annular space formed by an annular groove 29 of the control piston 10 and by the guide sleeve 11.
- the channel, not shown, and the annular groove 47 are formed by recesses made in the guide sleeve 11.
- control piston 10 On a side of the control piston 10 facing the camshaft 16 there is a helical compression spring 19 acting on the control piston 10, which is supported with its end facing away from the control piston 10 on a bottom of the guide sleeve 11 closed to the side of the camshaft 16 and with its end facing the control piston 10 End acts on the control piston 10.
- an actuating magnet 30 formed by a pressure magnet is arranged in a housing 36 which is fixedly mounted to the cylinder head 23 and by means of which the control piston 10 can be adjusted against the spring force of the helical compression spring 19.
- piston 10 on an end of the control spring facing away from the helical compression spring 19 piston 10 a contact point, not shown, between the plunger of the pressure magnet and the control piston, which transmits the actuating forces of the pressure magnet to the control piston in a known manner.
- the control piston 10 is secured in the guide sleeve 11 via a locking ring 18 in the direction facing away from the helical compression spring 19.
- the actuating unit which can be controlled with the actuating magnet 30 via the control piston 10 has a sleeve-shaped housing 31 which encloses the camshaft 16 at its end.
- the cover 32, the housing 31 and the sprocket 33 are clamped over tensioning screws 34 extending in the axial direction and form a unit rotatably mounted on the camshaft 16.
- the cover 32, the housing 31 and the sprocket 33 enclose an annular space in which an impeller 35 is arranged.
- the impeller 35 is pressed non-rotatably onto the camshaft 16 and has vanes, not shown, which extend outward in the radial direction.
- the vanes of the impeller 35 form pressure chambers with vanes, not shown, which are molded onto the housing 31 and extend radially inwards. If the actuating magnet 30 is deactivated, the control piston 10 is displaced by the helical compression spring 19 into its first end position facing away from the camshaft 16.
- the annular groove 29 of the control piston 10 is located radially within the radial bores 12, 15.
- the annular groove 29 of the control piston 10 comes to lie radially within the radial bores 13, 14.
- Via the radial bores 13, 14, via an interface 56 between the guide sleeve 11 and the camshaft 16, specifically via an annular groove 53 made on the outer circumference of the guide sleeve 11, via radial bores 39, 40 in the camshaft 16 and via radial bores 51, 52 in the inner ring of the impeller 35 further pressure chambers are pressurized.
- annular groove 41 of the control piston 10 comes to rest radially inside the radial bores 12, 15, via which the first pressure spaces are relieved of pressure and via channels 42, 43 in the control piston 10, so that the sprocket 33 rotates relative to the camshaft 16 into its second rotational position ,
- the actuating magnet 30 is deactivated and the control piston 10 by the spring force of the helical compression spring 19 in the
- the camshaft 16 is shifted away from it, namely until the annular groove 29 of the control piston 10 comes to rest radially within the radial bores 12, 15, the radial bores 37, the radial bores 37, the radial bores 12, 15 and the annular groove 48 introduced into the guide sleeve 11.
- 38 in the camshaft 16 and via the radial bores 49, 50 in the inner ring of the impeller 35 pressurized the first pressure chambers.
- annular groove 44 of the control piston 10 comes to rest radially inside the radial bores 13, 14, via which the further pressure spaces are relieved of pressure and via channels 45, 46 in the control piston 10, so that the sprocket 33 rotates relative to the camshaft 16 into its first rotational position ,
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
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE50302961T DE50302961D1 (de) | 2002-03-15 | 2003-02-21 | Nockenwellenversteller für eine brennkraftmaschine |
JP2003576783A JP2005530078A (ja) | 2002-03-15 | 2003-02-21 | 内燃機関用カムシャフト調節器 |
EP03744333A EP1485581B1 (de) | 2002-03-15 | 2003-02-21 | Nockenwellenversteller für eine brennkraftmaschine |
US10/940,943 US20050051123A1 (en) | 2002-03-15 | 2004-09-14 | Camshaft adjuster for an internal combustion engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10211468.4 | 2002-03-15 | ||
DE10211468A DE10211468A1 (de) | 2002-03-15 | 2002-03-15 | Nockenwellenversteller für eine Brennkraftmaschine |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/940,943 Continuation-In-Part US20050051123A1 (en) | 2002-03-15 | 2004-09-14 | Camshaft adjuster for an internal combustion engine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003078804A1 true WO2003078804A1 (de) | 2003-09-25 |
Family
ID=27771341
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2003/001772 WO2003078804A1 (de) | 2002-03-15 | 2003-02-21 | Nockenwellenversteller für eine brennkraftmaschine |
Country Status (5)
Country | Link |
---|---|
US (1) | US20050051123A1 (de) |
EP (1) | EP1485581B1 (de) |
JP (1) | JP2005530078A (de) |
DE (2) | DE10211468A1 (de) |
WO (1) | WO2003078804A1 (de) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006018081A1 (de) * | 2004-08-10 | 2006-02-23 | Schaeffler Kg | Nockenwellentrieb mit einem nockenwellenversteller |
WO2008028902A1 (de) * | 2006-09-07 | 2008-03-13 | Mahle International Gmbh | Verstellbare nockenwelle |
WO2008132004A1 (de) * | 2007-04-27 | 2008-11-06 | Schaeffler Kg | Nockenwellenverstellsystem |
WO2009071457A2 (de) * | 2007-12-05 | 2009-06-11 | Schaeffler Kg | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkraftmaschine |
EP2322769A1 (de) * | 2009-11-13 | 2011-05-18 | Hydraulik-Ring GmbH | Nockenwelleneinsatz |
US8505507B2 (en) | 2010-06-09 | 2013-08-13 | Toyota Jidosha Kabushiki Kaisha | Flow rate control valve |
WO2014183751A1 (de) * | 2013-05-17 | 2014-11-20 | Schaeffler Technologies Gmbh & Co. Kg | Zentralventil mit einem steuerkolben zur steuerung der ölversorgung für einen nockenwellenversteller |
Families Citing this family (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10346448B4 (de) | 2003-10-07 | 2017-03-30 | Daimler Ag | Nockenwellenversteller für eine Brennkraftmaschine |
DE102004005795A1 (de) * | 2004-02-06 | 2005-08-25 | Daimlerchrysler Ag | Vorrichtung zur Winkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine |
EP1596040B1 (de) * | 2004-05-14 | 2010-10-13 | Schaeffler KG | Nockenwellenversteller |
US7475660B2 (en) * | 2004-06-02 | 2009-01-13 | Ina-Schaeffler Kg | Camshaft adjuster |
DE102004058767A1 (de) * | 2004-12-07 | 2006-06-22 | Schaeffler Kg | Steuerventil |
DE102005026247A1 (de) * | 2005-06-08 | 2006-12-14 | Schaeffler Kg | Nockenwellentrieb für eine Brennkraftmaschine eines Kraftfahrzeugs |
DE102005053187A1 (de) * | 2005-11-08 | 2007-05-10 | Daimlerchrysler Ag | Stellvorrichtung für eine Brennkraftmaschine |
DE102009022869A1 (de) * | 2009-05-27 | 2010-12-09 | Hydraulik-Ring Gmbh | Flügelzellennockenwellenverstellersystem |
DE102009039385A1 (de) * | 2009-08-29 | 2011-03-03 | Schaeffler Technologies Gmbh & Co. Kg | Steuerventil |
DE102009039384A1 (de) | 2009-08-29 | 2011-03-03 | Schaeffler Technologies Gmbh & Co. Kg | Steuerventil |
DE102009050779B4 (de) * | 2009-10-27 | 2016-05-04 | Hilite Germany Gmbh | Schwenkmotornockenwellenversteller mit einer Reibscheibe und Montageverfahren |
DE102009051519A1 (de) * | 2009-10-31 | 2011-05-05 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenverstellanordnung |
DE102010045358A1 (de) | 2010-04-10 | 2011-10-13 | Hydraulik-Ring Gmbh | Schwenkmotornockenwellenversteller mit einem Hydraulikventil |
DE102010019005B4 (de) | 2010-05-03 | 2017-03-23 | Hilite Germany Gmbh | Schwenkmotorversteller |
DE102010061337B4 (de) | 2010-12-20 | 2015-07-09 | Hilite Germany Gmbh | Hydraulikventil für einen Schwenkmotorversteller |
DE102011003556B4 (de) | 2011-02-03 | 2022-03-24 | Schaeffler Technologies AG & Co. KG | Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4007181A1 (de) * | 1990-03-07 | 1991-09-12 | Audi Ag | Antriebsvorrichtung fuer eine nockenwelle |
US5107804A (en) * | 1989-10-16 | 1992-04-28 | Borg-Warner Automotive Transmission & Engine Components Corporation | Variable camshaft timing for internal combustion engine |
DE19817319A1 (de) * | 1998-04-18 | 1999-10-28 | Daimler Chrysler Ag | Nockenwellenversteller für Brennkraftmaschinen |
EP1052378A2 (de) * | 1999-05-14 | 2000-11-15 | Honda Giken Kogyo Kabushiki Kaisha | Steuerungseinrichtung für eine Brennkraftmaschine |
EP1136656A2 (de) * | 2000-02-14 | 2001-09-26 | BorgWarner Inc. | Nockenwellenzeitsteuerungseinrichtung mit Drehflügel und Sperrsystem |
DE10029261A1 (de) * | 2000-06-14 | 2001-12-20 | Deutz Ag | Nockenwellenverschwenkeinrichtung |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4116152A1 (de) * | 1991-05-17 | 1992-11-19 | Bosch Gmbh Robert | Einrichtung zur verstellung der drehwinkelzuordnung einer nockenwelle zu ihrem antriebselement |
-
2002
- 2002-03-15 DE DE10211468A patent/DE10211468A1/de not_active Withdrawn
-
2003
- 2003-02-21 EP EP03744333A patent/EP1485581B1/de not_active Expired - Fee Related
- 2003-02-21 DE DE50302961T patent/DE50302961D1/de not_active Expired - Lifetime
- 2003-02-21 JP JP2003576783A patent/JP2005530078A/ja not_active Abandoned
- 2003-02-21 WO PCT/EP2003/001772 patent/WO2003078804A1/de active IP Right Grant
-
2004
- 2004-09-14 US US10/940,943 patent/US20050051123A1/en not_active Abandoned
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5107804A (en) * | 1989-10-16 | 1992-04-28 | Borg-Warner Automotive Transmission & Engine Components Corporation | Variable camshaft timing for internal combustion engine |
DE4007181A1 (de) * | 1990-03-07 | 1991-09-12 | Audi Ag | Antriebsvorrichtung fuer eine nockenwelle |
DE19817319A1 (de) * | 1998-04-18 | 1999-10-28 | Daimler Chrysler Ag | Nockenwellenversteller für Brennkraftmaschinen |
EP1052378A2 (de) * | 1999-05-14 | 2000-11-15 | Honda Giken Kogyo Kabushiki Kaisha | Steuerungseinrichtung für eine Brennkraftmaschine |
EP1136656A2 (de) * | 2000-02-14 | 2001-09-26 | BorgWarner Inc. | Nockenwellenzeitsteuerungseinrichtung mit Drehflügel und Sperrsystem |
DE10029261A1 (de) * | 2000-06-14 | 2001-12-20 | Deutz Ag | Nockenwellenverschwenkeinrichtung |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006018081A1 (de) * | 2004-08-10 | 2006-02-23 | Schaeffler Kg | Nockenwellentrieb mit einem nockenwellenversteller |
WO2008028902A1 (de) * | 2006-09-07 | 2008-03-13 | Mahle International Gmbh | Verstellbare nockenwelle |
US8453615B2 (en) | 2006-09-07 | 2013-06-04 | Mahle International Gmbh | Adjustable camshaft |
WO2008132004A1 (de) * | 2007-04-27 | 2008-11-06 | Schaeffler Kg | Nockenwellenverstellsystem |
WO2009071457A2 (de) * | 2007-12-05 | 2009-06-11 | Schaeffler Kg | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkraftmaschine |
WO2009071457A3 (de) * | 2007-12-05 | 2009-08-20 | Schaeffler Kg | Vorrichtung zur variablen einstellung der steuerzeiten von gaswechselventilen einer brennkraftmaschine |
US8522733B2 (en) | 2007-12-05 | 2013-09-03 | Schaeffler Technologies AG & Co. KG | Device for variably adjusting control times of gas exchange valves of an internal combustion engine |
EP2322769A1 (de) * | 2009-11-13 | 2011-05-18 | Hydraulik-Ring GmbH | Nockenwelleneinsatz |
US8505507B2 (en) | 2010-06-09 | 2013-08-13 | Toyota Jidosha Kabushiki Kaisha | Flow rate control valve |
WO2014183751A1 (de) * | 2013-05-17 | 2014-11-20 | Schaeffler Technologies Gmbh & Co. Kg | Zentralventil mit einem steuerkolben zur steuerung der ölversorgung für einen nockenwellenversteller |
Also Published As
Publication number | Publication date |
---|---|
US20050051123A1 (en) | 2005-03-10 |
DE10211468A1 (de) | 2003-09-25 |
EP1485581A1 (de) | 2004-12-15 |
JP2005530078A (ja) | 2005-10-06 |
EP1485581B1 (de) | 2006-04-12 |
DE50302961D1 (de) | 2006-05-24 |
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