WO2006045389A1 - Lebensdauergeschmierter nockenwellentrieb für eine brennkraftmaschine - Google Patents
Lebensdauergeschmierter nockenwellentrieb für eine brennkraftmaschine Download PDFInfo
- Publication number
- WO2006045389A1 WO2006045389A1 PCT/EP2005/010392 EP2005010392W WO2006045389A1 WO 2006045389 A1 WO2006045389 A1 WO 2006045389A1 EP 2005010392 W EP2005010392 W EP 2005010392W WO 2006045389 A1 WO2006045389 A1 WO 2006045389A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- camshaft
- housing
- cylinder head
- camshaft adjuster
- sealing
- Prior art date
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 11
- 238000007789 sealing Methods 0.000 claims abstract description 67
- 238000005461 lubrication Methods 0.000 claims abstract description 19
- 230000005540 biological transmission Effects 0.000 claims description 7
- 230000005923 long-lasting effect Effects 0.000 abstract 1
- 239000010687 lubricating oil Substances 0.000 abstract 1
- 239000000314 lubricant Substances 0.000 description 12
- 230000033001 locomotion Effects 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 230000006735 deficit Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000011109 contamination Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 239000010705 motor oil Substances 0.000 description 2
- 238000000465 moulding Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- RGWOFTGZWJGPHG-NKWVEPMBSA-N (2r)-3-hydroxy-2-[(1r)-2-oxo-1-(6-oxo-3h-purin-9-yl)ethoxy]propanal Chemical compound N1C=NC(=O)C2=C1N([C@@H](C=O)O[C@H](CO)C=O)C=N2 RGWOFTGZWJGPHG-NKWVEPMBSA-N 0.000 description 1
- 241001295925 Gegenes Species 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 239000004519 grease Substances 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
- 230000001050 lubricating effect Effects 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000007246 mechanism Effects 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 229910052761 rare earth metal Inorganic materials 0.000 description 1
- 150000002910 rare earth metals Chemical class 0.000 description 1
- 230000000284 resting effect 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
- F01L1/02—Valve drive
- F01L1/024—Belt drive
-
- 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
-
- 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
- F01L1/352—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 bevel or epicyclic 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
- F01L2810/00—Arrangements solving specific problems in relation with valve gears
- F01L2810/02—Lubrication
Definitions
- the invention relates to a camshaft drive for an internal combustion engine with a camshaft adjuster.
- DE 689 04 842 T2 discloses a camshaft drive for adjusting and fixing the relative rotational angle position of a cam lobe relative to a crankshaft of an internal combustion engine by means of a camshaft adjuster.
- the camshaft adjuster comprises a housing which carries a pulley on its mantle surface.
- the housing of the camshaft adjuster is hermetically and airtightly closed by a front cover on the front side opposite a camshaft.
- the camshaft adjuster is supplied via an engine oil pump from an oil sump with a fluid, which serves as a working fluid and assumes lubricating properties. 5
- a camshaft adjuster which has a trained as a three-shaft gear adjusting with a Doppelexzen ⁇ ter.
- the camshaft drive has a toothed chain as traction means.
- the camshaft adjuster is integrated in a cylinder head.
- An actuator is also integrated in the cylinder head with a seal. Relative to each other moving contact surfaces of components of the camshaft adjuster and bearings are lubricated via existing in the cylinder head lubricant.
- the camshaft adjuster according to DE 100 38 354 C2 which includes a swash plate gear is driven via a toothed chain ange ⁇ and integrated into a cylinder head, so that lubrication takes place in the cylinder head lubricant.
- the object of the invention is to propose a camshaft drive for which lubrication of the camshaft adjuster is made possible in a simple manner and for long operating periods.
- the camshaft adjuster has a lifetime lubrication.
- lifetime lubrication is introduced, for example, with a production of the camshaft adjuster once in the camshaft adjuster and need not be renewed within predetermined maintenance intervals, but provides sufficient lubrication for a predetermined lifetime of the camshaft adjuster or the internal combustion engine.
- Lifetime lubrication is a suitable lubricant chosen for this purpose, in particular a grease or an oil.
- the camshaft adjuster has an environment sealed housing in which the lifetime lubrication is arranged.
- sealing means any seal which is sufficient to prevent the lubricant from escaping from the mold. prevent housing.
- the appropriate measures for sealing the housing must be adapted to the viscosity of the lubricant.
- An essential advantage of the invention is that with the sealed housing and the lifetime lubrication the need for a connection of the Ge housing with other Schmierstoffniktechnik ⁇ deleted. Rather, the INOX shaft adjuster represents a separate and autonomous component in terms of lubrication. This has advantages for assembly and disassembly of the camshaft adjuster, since any connections to further lubricant circuits do not have to be taken into account. A further advantage is that, in the case of a collapse, a change or a contamination of a lubricant circuit, this in the case of embodiment 5 according to the invention has no repercussions on a function of the camshaft adjuster.
- the camshaft adjuster does not necessarily have to be arranged in a cylinder head of the internal combustion engine, but can be arranged outside the same. This results in extended constructive possibilities.
- a camshaft adjuster can now be used in conjunction with a linear drive.
- O has the housing on at least one side open interior.
- a seal is made with a sealing cover, which seals the housing to the outside. closes.
- a sealing cover is in particular a pressed-in or clipped-in sealing cover.
- the sealing cover here can only fulfill a sealing function at one or more sealing points, so that it can be performed with low wall thickness or bend soft.
- such a sealing cover can fulfill further functions, for example, serve to support components of the camshaft adjuster.
- any known components come into consideration.
- these are an O-ring, a labyrinth seal, a gap seal and / or a radial shaft seal.
- sealing measures can be ensured both between resting components such as the housing and a sealing cover as well as between relatively moving components, a sufficient sealing function.
- the selection of a suitable sealing measure takes place according to the occurring relative speeds, the viscosity of a lubricant and the sealing point. For example, fugal forces may be lower for sealing points in the surrounding area of rotating components due to centrifugal forces exerted on the lubricant than for sealing points between components that are not moved relative to one another.
- a camshaft with sealing emerges from a cylinder head with an end region.
- the camshaft adjuster can be formed separately from the cylinder head.
- the housing of the camshaft adjuster is sealed on the side facing the cylinder head relative to the cylinder head, the end region of the camshaft or a component rotating with the camshaft. This ensures that no lubricant can escape from the housing of the camshaft adjuster in the direction of the cylinder head and no foreign bodies can enter the housing.
- the housing of the Nockenwel- lenverstellers against this component is sealed.
- the camshaft adjuster is also sealed on the side facing the cylinder head for disassembly of the camshaft.
- the camshaft is sealed regardless of the assembly of the camshaft adjuster relative to the cylinder head to the outside.
- the housing of the camshaft adjuster is sealed with respect to an actuating shaft of a servomotor (or with respect to a component rotating with the actuating shaft).
- the housing possibly with sealing lids, the adjusting shaft and the camshaft, forms an interior which is sealed to the outside and in which the gearbox of the camshaft adjuster with lifetime lubrication is arranged.
- FIG. 1 shows a camshaft drive in half section through a housing sealed off via a sealing cover
- FIG. 2 shows a front view of the camshaft drive according to FIG. 1 in a spatial representation
- Figure 3 is a rear view of the camshaft drive according to FIG. 1 in a three-dimensional view. Detailed description of the invention
- a camshaft adjuster 13 is used for adjusting the angular position between a drive element 11 driven by a traction means, for example a chain or a belt, and a camshaft 12 in accordance with a control device, which in particular takes into account a thoroughlyanforde ⁇ tion of the driver, emission requirements, Kraftstofferspamisan petitione n and engine, operating and ambient ngsparametern a suitable control signal for adjusting the camshaft adjuster 13 determined.
- camshaft drive 10 is any camshaft adjuster is used, which operates on the basis of a superposition gear or Dreiwelleng ⁇ - drive.
- the transmission of the drive motion of the drive element 1 1 to the camshaft 12 depends on the movement of an actuating shaft 14, which is in driving connection with an actuator.
- the transmission is a double eccentric transmission.
- the control shaft 14 enters into a central bore of a double eccentric shaft 15 for the purpose of forming a drive connection, possibly with the interposition of an elastic coupling element 41.
- the double eccentric shaft 15 In the end region of the double eccentric shaft 15 projecting beyond the end of the adjusting shaft 14, the latter has two axially offset eccentric circumferential surfaces 16, 17 which each carry a roller bearing 18, 19.
- the two extremities (areas maximum distance of the circumferential surfaces 16, 17 from a longitudinal axis X-X of the camshaft adjuster) of the peripheral surfaces 16, 17 are offset in the circumferential direction by 180 ° from each other.
- the roller bearings 18, 19 carry intermediate gears 20, 21 on their outer lateral surfaces.
- the intermediate gears 20, 21 have a plurality of bores 22, 23 distributed in the circumferential direction F.
- a respective common web 24 passes through the bores 22, 23, which passes through parallel to the longitudinal axis XX of the No camshaft adjuster 13 extends.
- the web 24 is supported in its end regions and on the outside by the intermediate wheels 20, 21 in respective annular support elements 25, 26.
- the double eccentric shaft 15 passes through the inner bore of the support element 25 with radial clearance.
- the Ab support member 26 is radially inwardly rotatably ver ⁇ with the camshaft 12 connected.
- the support element 26 is braced with the cam shaft 12 via a clamping screw 27, which is screwed into an end face of the camshaft 12.
- a housing 28 of the camshaft adjuster 13 has a hollow cylindrical wall 29, which carries the drive element 11, in particular a belt pulley, radially on the outside and forms a ring gear 30 radially inwardly.
- the intermediate wheels 20, 21 mesh with the ring gear 30.
- the limb of the peripheral surface 16 is represented for the intermediate wheel 20 the intermediate wheel 20 engages with the ring gear 30 here.
- the extremity for the circumferential surface 17 lies in the half-plane (not shown) in FIG. 1, so that the toothing of the intermediate wheel 21 is not in mesh with the internal toothing of the ring gear 30 in the illustrated region.
- the holes 22, 23 have over the diameters of the webs such an excess that caused by the extremity relative movements between the Zwi ⁇ 's wheels 20, 21 and the web 24 are possible.
- the support elements 25, 26 are guided relative to the housing 28 via suitable sliding bearings and ab ⁇ supported on the shoulder for the ring gear 30 inwardly and supported in the direction of the axis XX to the outside in each case via suitable securing elements 34. If the actuating shaft 14 is driven by the actuator at an angular velocity which deviates from the angular velocity of the camshaft 12, the extreme movement and thus the contact point between intermediate wheels 20, 21 will move in the circumferential direction with respect to the ring gear 30. This is a change the angle between the drive element 11 and the camshaft 12 is accompanied.
- the contact surfaces that move relative to one another and roll against each other, as well as the roller bearings 18, 19, 31, are provided with lifetime lubrication.
- An outlet of such a lifetime lubrication from the Ge housing 28 is prevented by using sealing caps 36, 37 which close the two openings of the wall 29.
- the sealing covers 36, 37 rotate with the housing 28.
- the sealing cover 36 is clipped into a suitable groove of the housing 28.
- Radially inwardly between the sealing cover 36 and the actuating shaft 14, a sealing element 38 is interposed.
- sealing element 39 is interposed between the sealing cover 37 and the housing 28, a sealing element 39 is interposed. Radially inside the sealing cover 37 has a collar on which radially inwardly a sealing element 40 is supported, which occurs radially outboard with the cylinder head 33 in operative connection.
- the sealing covers 36, 37 can be non-positively inserted or clipped into the adjacent components.
- the elastic caps 36, 37 are pressed against the adjacent components by elasticities of the sealing caps 36, 37 themselves or additional elastic elements, as a result of which a sealing effect is produced.
- sealing cover of the adjacent components can be positively received, for example in a groove.
- a sealing element such as a sealing ring or a radial shaft sealing ring may be interposed.
- gap seal or labyrinth seal can be used which is adapted to the particular operating requirements, such as rotational speeds, centrifugal forces and a viscosity of the service life lubrication and the temperatures occurring.
- the sealing cover 36 preferably bears against the wall 29 in the radially outer end region.
- a support in relation to the support element 25 is possible, in which case an additional seal must be provided between the support element 25 and the wall 29.
- the sealing cover 36 is supported relative to the actuating shaft 14.
- a support of the sealing cover 36 relative to the double eccentric shaft 15 takes place. In this case, it must be ensured that the connection between the control shaft 14 and the double lever shaft 15 is sealed.
- the sealing cover 37 is supported axially on the outside of the wall 29 from. Alternatively, it is possible for the sealing cover 37 to be supported relative to the support element 26, in which case a seal is provided between the abutment element 26 and the abutment element 26. Support member 26 and wall 29 is provided. Radial inside is a support of the sealing cover 37 relative to the cylinder head 33 or the camshaft 12th
- the sealing cover 36, 37 are preferably designed inherently rigid, for example as a sheet metal part. Alternatively, the sealing cover can be formed at least partially bendable, in particular as a sealing bellows or the like.
- the sealing cover 36, 37 can be completely eliminated for a further embodiment of the invention, provided that a seal between the housing 28, support member 25, web 24, Doppelexzenterwelle 15 and actuator shaft 14 and housing 28, Abstweil ⁇ element 26, web 24 and camshaft 12 is.
- a rubber-elastic molding element 41 is interposed between the adjusting shaft 14 and the double eccentric shaft 15.
- a sealing of a sealing cover 36 relative to the rubber-elastic molding element 41 or against the control shaft can be done. Under certain circumstances, it is sufficient in this case to provide a gap seal, since the lifetime lubrication is thrown radially outward due to the centrifugal force.
- the camshaft actuator used according to the invention may be a camshaft actuator of any design.
- an actuating unit an embodiment with a BLDC motor with rare earth magnet and stationary stator, preferably with bipolar control, can be used.
- Other other motors such as, for example, a brushed direct current motor, are also conceivable.
- camshaft adjuster units are used, in which the engine rotates with the transmission.
- a rubber-elastic molded element 41 As Kuppln ngselement between the control shaft 14 and the electric motor can be integrated into the control shaft 14, a rubber-elastic molded element 41, although other options, such as a feather key or a splined shaft profile can be used.
- other transmissions such as single internal eccentric gear units, wobble gears, wave gears, planetary gears and other highly translating gears, can also be used in a manner known per se for belt-driven internal combustion engines.
- the lifetime lubrication is preferably formed aus ⁇ as life fat filling.
- Other lifetime lubrication such as engine oil (as in chain driven engines) is also acceptable, in which case increased sealing requirements must be met.
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 (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/577,605 US7703427B2 (en) | 2004-10-22 | 2005-09-27 | Lifelong-lubricated camshaft drive for an internal combustion engine |
CN2005800363466A CN101048575B (zh) | 2004-10-22 | 2005-09-27 | 终身润滑的内燃机凸轮轴传动装置 |
DE502005009918T DE502005009918D1 (de) | 2004-10-22 | 2005-09-27 | Lebensdauergeschmierter nockenwellentrieb für eine brennkraftmaschine |
EP05787247A EP1802850B1 (de) | 2004-10-22 | 2005-09-27 | Lebensdauergeschmierter nockenwellentrieb für eine brennkraftmaschine |
JP2007537140A JP2008517207A (ja) | 2004-10-22 | 2005-09-27 | 内燃機関用のカム軸駆動装置 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004051423.2 | 2004-10-22 | ||
DE102004051423A DE102004051423A1 (de) | 2004-10-22 | 2004-10-22 | Nockenwellentrieb für eine Brennkraftmaschine |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2006045389A1 true WO2006045389A1 (de) | 2006-05-04 |
Family
ID=35427525
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2005/010392 WO2006045389A1 (de) | 2004-10-22 | 2005-09-27 | Lebensdauergeschmierter nockenwellentrieb für eine brennkraftmaschine |
Country Status (7)
Country | Link |
---|---|
US (1) | US7703427B2 (de) |
EP (1) | EP1802850B1 (de) |
JP (1) | JP2008517207A (de) |
KR (1) | KR20070068392A (de) |
CN (1) | CN101048575B (de) |
DE (2) | DE102004051423A1 (de) |
WO (1) | WO2006045389A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013216184A1 (de) | 2013-08-14 | 2015-02-19 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenversteller |
DE102013216182A1 (de) | 2013-08-14 | 2015-02-19 | Schaeffler Technologies Gmbh & Co. Kg | Verstelleinrichtung, insbesondere für Brennkraftmaschinen |
DE102013218513A1 (de) | 2013-09-16 | 2015-03-19 | Schaeffler Technologies Gmbh & Co. Kg | Kupplung |
US10330148B2 (en) | 2014-02-26 | 2019-06-25 | Airbus Helicopters Deutschland GmbH | Bearing arrangement with a first bearing layer and a second bearing layer |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006007584A1 (de) * | 2006-02-18 | 2007-08-30 | Schaeffler Kg | Nockenwellenversteller mit einem Überlagerungsgetriebe |
DE102008014609A1 (de) * | 2008-03-17 | 2009-09-24 | Continental Automotive Gmbh | Aktuator für Schaltelement einer Verbrennungskraftmaschine |
DE102011004588A1 (de) * | 2011-02-23 | 2012-08-23 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellensteller |
DE102016207612A1 (de) | 2016-05-03 | 2017-11-09 | Schaeffler Technologies AG & Co. KG | Wellgetriebe |
WO2018165455A1 (en) | 2017-03-09 | 2018-09-13 | Johnson Controls Technology Company | Back to back bearing sealing systems |
DE102017105455A1 (de) * | 2017-03-15 | 2018-09-20 | Schaeffler Technologies AG & Co. KG | Stellmotor für eine elektrische Nockenwellenverstellung |
DE102017114053B3 (de) | 2017-06-26 | 2018-09-20 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
DE102018100405A1 (de) | 2018-01-10 | 2019-07-11 | Schaeffler Technologies AG & Co. KG | Elektrischer Nockenwellenversteller zur variablen Ventilsteuerung in einer Brennkraftmaschine |
DE102018132427A1 (de) | 2018-12-17 | 2020-06-18 | Schaeffler Technologies AG & Co. KG | Elektrischer Nockenwellenversteller mit trockenlaufendem Zugmittelgetriebe |
JP7225836B2 (ja) * | 2019-01-24 | 2023-02-21 | トヨタ自動車株式会社 | 内燃機関 |
CN111940197B (zh) * | 2020-06-28 | 2022-09-06 | 惠州市富美真空镀膜有限公司 | 喷涂加工生产线 |
DE102020121213A1 (de) | 2020-08-12 | 2022-02-17 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
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EP0356162A1 (de) * | 1988-08-18 | 1990-02-28 | Atsugi Unisia Corporation | Zeitsteuervorrichtung |
EP0488156A1 (de) * | 1990-11-26 | 1992-06-03 | Unisia Jecs Corporation | Einlass-, Auslassventilsteuervorrichtung für Brennkraftmaschinen |
DE4218081A1 (de) * | 1992-06-01 | 1993-12-02 | Schaeffler Waelzlager Kg | Verstellbarer, geteilter Kolben |
US5680837A (en) * | 1996-09-17 | 1997-10-28 | General Motors Corporation | Planetary cam phaser with worm electric actuator |
US20020017257A1 (en) * | 2000-08-05 | 2002-02-14 | Detlef Axmacher | Control unit for adjusting the angle of rotation of a camshaft |
DE10248355A1 (de) * | 2002-10-17 | 2004-04-29 | Ina-Schaeffler Kg | Nockenwellenversteller mit elektrischem Antrieb |
US6799544B1 (en) * | 2003-05-29 | 2004-10-05 | Delphi Technologies, Inc. | Method and apparatus for actuating a cam phaser |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS59175616U (ja) * | 1983-05-12 | 1984-11-24 | トヨタ自動車株式会社 | 内燃機関のバルブタイミング制御装置 |
DE4036209C1 (en) | 1990-11-14 | 1992-05-07 | Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De | IC engine accessories drive system - incorporates planetary gears and freewheel mechanism |
US5172660A (en) * | 1992-02-24 | 1992-12-22 | Eaton Corporation | Camshaft phase change device |
DE19546934C2 (de) * | 1995-12-15 | 2001-05-31 | Schaeffler Waelzlager Ohg | Druckmittelabdichtung für eine Nockenwellenverstellvorrichtung |
DE10101669A1 (de) | 2001-01-16 | 2002-08-29 | Zahnradfabrik Friedrichshafen | Elektrischer Einzelradantrieb |
DE10211607A1 (de) * | 2002-03-12 | 2003-10-09 | Porsche Ag | Antrieb für Ventiltriebsteuerungen von Fahrzeugen, vorzugsweise von Nockenwellenverstellern |
JP2004132515A (ja) * | 2002-10-15 | 2004-04-30 | Nsk Ltd | ボールネジ機構及びアクチュエータ |
-
2004
- 2004-10-22 DE DE102004051423A patent/DE102004051423A1/de not_active Withdrawn
-
2005
- 2005-09-27 DE DE502005009918T patent/DE502005009918D1/de active Active
- 2005-09-27 CN CN2005800363466A patent/CN101048575B/zh active Active
- 2005-09-27 US US11/577,605 patent/US7703427B2/en active Active
- 2005-09-27 WO PCT/EP2005/010392 patent/WO2006045389A1/de active Application Filing
- 2005-09-27 KR KR1020077008982A patent/KR20070068392A/ko not_active Application Discontinuation
- 2005-09-27 EP EP05787247A patent/EP1802850B1/de active Active
- 2005-09-27 JP JP2007537140A patent/JP2008517207A/ja active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0356162A1 (de) * | 1988-08-18 | 1990-02-28 | Atsugi Unisia Corporation | Zeitsteuervorrichtung |
EP0488156A1 (de) * | 1990-11-26 | 1992-06-03 | Unisia Jecs Corporation | Einlass-, Auslassventilsteuervorrichtung für Brennkraftmaschinen |
DE4218081A1 (de) * | 1992-06-01 | 1993-12-02 | Schaeffler Waelzlager Kg | Verstellbarer, geteilter Kolben |
US5680837A (en) * | 1996-09-17 | 1997-10-28 | General Motors Corporation | Planetary cam phaser with worm electric actuator |
US20020017257A1 (en) * | 2000-08-05 | 2002-02-14 | Detlef Axmacher | Control unit for adjusting the angle of rotation of a camshaft |
DE10248355A1 (de) * | 2002-10-17 | 2004-04-29 | Ina-Schaeffler Kg | Nockenwellenversteller mit elektrischem Antrieb |
US6799544B1 (en) * | 2003-05-29 | 2004-10-05 | Delphi Technologies, Inc. | Method and apparatus for actuating a cam phaser |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013216184A1 (de) | 2013-08-14 | 2015-02-19 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenversteller |
DE102013216182A1 (de) | 2013-08-14 | 2015-02-19 | Schaeffler Technologies Gmbh & Co. Kg | Verstelleinrichtung, insbesondere für Brennkraftmaschinen |
WO2015021971A1 (de) | 2013-08-14 | 2015-02-19 | Schaeffler Technologies Gmbh & Co. Kg | Verstelleinrichtung, insbesondere für brennkraftmaschinen |
WO2015021984A1 (de) | 2013-08-14 | 2015-02-19 | Schaeffler Technologies Gmbh & Co. Kg | Nockenwellenversteller |
US9840942B2 (en) | 2013-08-14 | 2017-12-12 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster |
DE102013216184B4 (de) * | 2013-08-14 | 2020-11-26 | Schaeffler Technologies AG & Co. KG | Nockenwellenversteller |
DE102013218513A1 (de) | 2013-09-16 | 2015-03-19 | Schaeffler Technologies Gmbh & Co. Kg | Kupplung |
US10330148B2 (en) | 2014-02-26 | 2019-06-25 | Airbus Helicopters Deutschland GmbH | Bearing arrangement with a first bearing layer and a second bearing layer |
Also Published As
Publication number | Publication date |
---|---|
EP1802850A1 (de) | 2007-07-04 |
US20080047513A1 (en) | 2008-02-28 |
DE102004051423A1 (de) | 2006-05-04 |
US7703427B2 (en) | 2010-04-27 |
JP2008517207A (ja) | 2008-05-22 |
KR20070068392A (ko) | 2007-06-29 |
CN101048575A (zh) | 2007-10-03 |
CN101048575B (zh) | 2013-01-23 |
EP1802850B1 (de) | 2010-07-14 |
DE502005009918D1 (de) | 2010-08-26 |
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