EP1794420B1 - Nockenwellenversteller für eine verbrennungskraftmaschine - Google Patents

Nockenwellenversteller für eine verbrennungskraftmaschine Download PDF

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Publication number
EP1794420B1
EP1794420B1 EP05773962A EP05773962A EP1794420B1 EP 1794420 B1 EP1794420 B1 EP 1794420B1 EP 05773962 A EP05773962 A EP 05773962A EP 05773962 A EP05773962 A EP 05773962A EP 1794420 B1 EP1794420 B1 EP 1794420B1
Authority
EP
European Patent Office
Prior art keywords
stator
rotor
blades
camshaft adjuster
blade
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.)
Not-in-force
Application number
EP05773962A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1794420A1 (de
Inventor
Josef Bachmann
Rolf Schwarze
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GKN Sinter Metals Holding GmbH
Original Assignee
GKN Sinter Metals Holding GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GKN Sinter Metals Holding GmbH filed Critical GKN Sinter Metals Holding GmbH
Publication of EP1794420A1 publication Critical patent/EP1794420A1/de
Application granted granted Critical
Publication of EP1794420B1 publication Critical patent/EP1794420B1/de
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • F01L1/352—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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34479—Sealing of phaser devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the invention relates to a camshaft adjuster for internal combustion engines.
  • Camshaft adjusters of the aforementioned type serve to enable the most optimal or variable valve control. They offer the possibility of adjusting the phase angle of the valve control infinitely and in a controlled manner.
  • a camshaft adjuster is non-rotatably and non-positively connected to the respective camshaft.
  • a rotational movement is transmitted to the camshaft and thereby preset a respective desired setting of the camshaft relative to the crankshaft of the internal combustion engine.
  • camshaft adjusters are hydraulically driven.
  • the oil pressure required for adjusting the camshaft is obtained from the lubricating oil pressure circuit associated with the respective internal combustion engine.
  • the camshaft is not yet in the desired relative position to the crankshaft, especially in the exhaust-gas-critical engine starting phase.
  • camshaft phasers which steplessly change the angular position of the camshaft, is represented by systems that are based on the swing motor principle.
  • the above systems are supplied via the oil pump from the lubricating oil circuit of the engine with pressurized oil, during which so-called "hot run” these systems must also work at oil temperatures of 150 ° C and pressures of ⁇ 0.5 bar at idle speed of the engine. Thermal influences, which can occur due to the maximum temperatures of 150 ° C reached during engine operation, must be taken into account when designing the component size and tolerances.
  • a drive wheel has a cavity formed by a peripheral wall and two side walls, in which at least one hydraulic working space is formed by at least two boundary walls.
  • a wing extending into the hydraulic working space divides the hydraulic working space into two hydraulic pressure chambers. Gap between a head of a pressure medium distributor and a breakthrough of a side wall of the drive wheel and / or between the lateral surface and an opening of the other side wall of the drive wheel are sealed by wear-resistant sealant against pressure medium leaks.
  • the DE 198 08 619 A1 describes a locking device for a vane-type adjusting device.
  • a vane-adjusting device in which between a swivel impeller and a drive wheel enlarged formed radial gaps are provided, while the sealing elements are designed as pivotable in both directions of rotation of the swivel impeller pendulum sealing strips, with the pressure force of the hydraulic pressure medium against the respective mating surface on the drive wheel or the swing impeller are pivotable.
  • a drive unit is pivotally mounted on a driven unit via a plurality of radial bearing points, wherein at least the surfaces of the individual radial bearing segments of the drive unit and the opposite radial bearing segments of the output unit and optionally also the axial contact surfaces between the drive unit and the output unit are formed with a friction-reducing coating.
  • Probesematic in such camshaft adjusters is that to avoid greater internal leakage in the pressure chambers tight tolerances must be met, which can be met only costly, especially if such components are made by sintering. In a sintering production, these tolerances are therefore only by a corresponding complex mechanical processing, or on significantly reduced quantities reachable. Furthermore, in most camshaft adjusters locking or return springs must be installed to ensure the function in the so-called 'hot idle'.
  • the invention has for its object to provide a camshaft adjuster for internal combustion engines, which prevents internal radial leaks and is inexpensive to manufacture.
  • a camshaft adjuster for an internal combustion engine having a stator which has distributed over its circumference radially inwardly projecting Statorhoffl having at least one arranged in the stator Statoreriellagerasche which is open to the inside and in which a Statorhofflplanetenrad is mounted, said a rotor is mounted in the stator having rotor blades with at least one outwardly open rotor blade bearing pocket in which a Rotorhofflplanetenrad is mounted, wherein the Statorerielplanetengan engage in a arranged on the outer circumference of the rotor between each rotor blade gear segment and the rotor blade planet gears in one on the inner circumference engage the stator between each arranged a stator blade toothed segment.
  • the geometry of the toothing must be designed so that the toothing data of the planet wheels, which are mounted in the rotor blade and in the stator wing, are the same.
  • the production costs are reduced, since only a tool is needed in the sintering technology of the rotor blade planetary gears and Statorplanetenzier.
  • the adjustment of the inner rotor takes place in that pressure is applied to a pressure chamber, wherein in response to the applied pressure chamber, the pressure against the inner rotor blade and this accordingly rotates.
  • the Statorhofflplanetenrad which engages with the toothed segment of the inner rotor is pressurized, whereby the tooth tips of the Statorhofflplanetenrades are pressed against the wall of Statoreriellagerasche and presses the tooth flanks of the Statorhofflplanetsrades against the tooth flanks of the toothed segment of the inner rotor by this pressurization become.
  • the stator has at least two stator blades and the rotor has at least two rotor blades. In a further advantageous embodiment, it is provided that the stator has three stator blades and the rotor has three rotor blades. In a likewise advantageous embodiment, it is provided that the stator has four stator blades and the rotor has four rotor blades.
  • Known camshaft adjusters usually have four stator vanes and four rotor vanes, whereby the possible angle of rotation of the camshaft are structurally limited.
  • stator, the inner rotor and / or the planet wheels are made of sintered metal. These parts can be sintered with larger tolerances without the radial tightness is worsened. Furthermore, the sensitivity to contaminated oil is low.
  • Another advantage of the relatively large manufacturing tolerances is the possibility to use other materials such as sintered aluminum or plastic. It is advantageous if the rotor, stator and the planet gears have at least approximately the same coefficients of thermal expansion so that these components can be paired with each other. It is possible, for example, to use a rotor and stator made of sintered steel and the planet wheels made of a plastic (thermosetting plastic) with approximately the same thermal coefficient. In particular, this results in a reduction of the noise due to the combination of sintered steel / plastic.
  • Fig. 1 shows a camshaft adjuster 1 for an internal combustion engine, not shown, with a stator 2, which has distributed over its circumference radially inwardly projecting stator 3.
  • the stator vanes 3 each have a Statorhoffllagerasche 4, which is open to the inside and in which a Statorhofflplanetenrad 5 is mounted.
  • a rotor 6 is mounted, the rotor blade 7 has.
  • Each rotor blade 7 has an outwardly open rotor blade bearing pocket 8 in which a rotor blade planet 9 is mounted.
  • stator blades 3 protrude radially inwards into the intermediate space between two rotor blades 7.
  • Statorhofflplanetenrad 5 engages in a arranged on the outer circumference of the rotor 6 between each rotor blade 7 toothed segment 10 a.
  • the rotor blade planetary gear 9 arranged in the rotor blade 7 engages in a toothing segment 11 arranged on the inner circumference of the stator 2 between in each case one stator wing 3.
  • the adjustment of the rotor 6 takes place in that 12 pressure is given by the pressure hole in the pressure chamber 13 or for the alternative direction of rotation that pressure in the pressure chamber 15 is given.
  • the Statorerielplanetenrad 5 which is engaged with the toothed segment 10 of the rotor 6, pressurized, by this pressurization, the tooth tips of the Statorerielplanetenrades 5 are pressed against the wall of the Statoreriellagerasche 4 and the tooth flanks of the Statorhofflplanetenrades 5 are pressed against the tooth flanks of the toothed segment 10 of the rotor 6.
  • the contact pressure of the tooth heads and tooth flanks results in large sealing surfaces which separate the pressure chambers 13, 15 radially absolutely tightly from the respective pressure-less chamber 13, 15, so that a radial sealing of the camshaft adjuster 1 is made possible.
  • Fig. 2 shows a detail "X" Fig. 1 with the partially indicated camshaft adjuster 1, which consists of a stator 2 and a rotor 6 mounted therein, wherein a state is shown in which the pressure chamber 15 with pressure, for example by means of a hydraulic fluid, is applied.
  • Pressure is introduced into the pressure chamber 15 via the pressure bore 14, wherein the pressurized space occupied by the hydraulic fluid is drawn in black. It turns out that in addition to the pressure chamber 15, which is formed from the space between the stator 3 and the rotor blade 7 also other areas are pressurized.
  • Fig. 3 shows a camshaft adjuster 1 for an internal combustion engine, not shown, with a stator 2, which has distributed over its circumference radially inwardly projecting stator 3.
  • the stator vanes 3 each have a Statorhoffllagerasche 4, which is open to the inside and in which a Statorhofflplanetenrad 5 is mounted.
  • a rotor 6 is mounted, the rotor blade 7 has.
  • Each rotor blade 7 has an outwardly open rotor blade bearing pocket 8 in which a rotor blade planet 9 is mounted.
  • the stator blades 3 protrude radially inwards into the intermediate space between two rotor blades 7. The same applies to the rotor blades 7, which each protrude into the intermediate space.
  • the rotor 6 is formed approximately star-shaped.
  • Stator pursuelplanetenrad 5 engages in a arranged on the outer circumference of the rotor 6 between each rotor blade 7 toothed segment 10 a.
  • the rotor blade planetary gear 9 arranged in the rotor blade 7 engages in a toothing segment 11 arranged on the inner circumference of the stator 2 between in each case one stator wing 3. Internal radial leaks that occur between the contact points of the stator 2 and the inner rotor 6 in the form of gap losses are prevented by the use of the toothed segments and the planetary gears engaging in them.
  • the adjustment of the rotor 6 takes place in that 12 pressure is given by the pressure hole in the pressure chamber 13 or for the alternative direction of rotation that pressure in the pressure chamber 15 is given.
  • the pressure against the rotor blade 7, Dependent on from the applied pressure chamber 13, 15, the pressure against the rotor blade 7, whereby this is rotated accordingly.
  • the Statorhofflplanetenrad 5 which is engaged with the toothed segment 10 of the rotor 6, pressurized, by this pressurization, the tooth tips of the Statorerielplanetenrades 5 are pressed against the wall of the Statoreriellagerasche 4 and the tooth flanks of the Statorhofflplanetenrades 5 are pressed against the tooth flanks of the toothed segment 10 of the rotor 6.

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)
EP05773962A 2004-09-29 2005-08-10 Nockenwellenversteller für eine verbrennungskraftmaschine Not-in-force EP1794420B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004047817A DE102004047817B3 (de) 2004-09-29 2004-09-29 Nockenwellenversteller für eine Verbrennungskraftmaschine
PCT/EP2005/008669 WO2006034752A1 (de) 2004-09-29 2005-08-10 Nockenwellenversteller für eine verbrennungskraftmaschine

Publications (2)

Publication Number Publication Date
EP1794420A1 EP1794420A1 (de) 2007-06-13
EP1794420B1 true EP1794420B1 (de) 2009-07-01

Family

ID=35197982

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05773962A Not-in-force EP1794420B1 (de) 2004-09-29 2005-08-10 Nockenwellenversteller für eine verbrennungskraftmaschine

Country Status (11)

Country Link
US (1) US7584731B2 (zh)
EP (1) EP1794420B1 (zh)
JP (1) JP4845888B2 (zh)
KR (1) KR101185387B1 (zh)
CN (1) CN100504041C (zh)
AT (1) ATE435360T1 (zh)
BR (1) BRPI0515941A (zh)
DE (2) DE102004047817B3 (zh)
ES (1) ES2328381T3 (zh)
MX (1) MX2007003419A (zh)
WO (1) WO2006034752A1 (zh)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006019607B4 (de) * 2006-04-25 2008-01-31 Hydraulik-Ring Gmbh Nockenwellenversteller
DE102008028640A1 (de) * 2008-06-18 2009-12-24 Gkn Sinter Metals Holding Gmbh Hydraulischer Nockenwellenversteller
JP6221694B2 (ja) * 2013-11-29 2017-11-01 アイシン精機株式会社 弁開閉時期制御装置
JP5987868B2 (ja) * 2014-07-22 2016-09-07 株式会社デンソー バルブタイミング調整装置
WO2018077404A1 (en) * 2016-10-26 2018-05-03 HELLA GmbH & Co. KGaA Apparatus for camshaft timing adjustment

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0583303U (ja) * 1992-04-14 1993-11-12 トーヨーエイテック株式会社 内燃機関の弁開閉時期制御装置
JPH05296011A (ja) * 1992-04-14 1993-11-09 Toyo A Tec Kk 内燃機関の弁開閉時期制御装置
JPH1113431A (ja) * 1997-06-24 1999-01-19 Aisin Seiki Co Ltd 弁開閉時期制御装置
DE19808619A1 (de) * 1998-02-28 1999-09-02 Schaeffler Waelzlager Ohg Verriegelungseinrichtung für eine Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere für eine Flügelzellen-Verstelleinrichtung
CN1292845A (zh) * 1998-05-12 2001-04-25 特罗科申特里克国际有限公司 用于轴相位调整的调整装置
JP2000045727A (ja) * 1998-08-04 2000-02-15 Mitsubishi Electric Corp 油圧式バルブタイミング調節装置およびその組立方法
JP2000161028A (ja) * 1998-11-26 2000-06-13 Denso Corp バルブタイミング調整装置
JP2000204915A (ja) * 1999-01-12 2000-07-25 Toyota Motor Corp 内燃機関の可変動弁装置
JP2000297614A (ja) * 1999-04-12 2000-10-24 Toyota Motor Corp 内燃機関のバルブタイミング制御装置
DE19922792A1 (de) * 1999-05-18 2000-11-23 Gkn Sinter Metals Holding Gmbh Verzahnungsrotorsatz
DE19962981A1 (de) * 1999-12-24 2001-07-05 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine insbesondere hydraulische Nockenwellen-Verstelleinrichtung in Rotationskolbenbauart
DE10010170A1 (de) * 2000-03-05 2001-09-06 Gkn Sinter Metals Gmbh Inverser Verzahnungsrotorsatz
DE10020120A1 (de) * 2000-04-22 2001-10-25 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere hydraulische Nockenwellen-Verstelleinrichtung in Rotationskolbenbauart
DE10054796A1 (de) * 2000-11-04 2002-06-13 Ina Schaeffler Kg Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
DE10062981A1 (de) 2000-12-16 2002-06-20 Mitsubishi Polyester Film Gmbh Heißsterilisierbare, biaxial orientierte Polyesterfolie mit guter Metallhaftung, Verfahren zu ihrer Herstellung und ihre Verwendung
DE10109837A1 (de) * 2001-03-01 2002-09-05 Ina Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
JP2002332812A (ja) * 2001-05-08 2002-11-22 Unisia Jecs Corp 内燃機関のバルブタイミング制御装置
JP3996895B2 (ja) * 2003-12-26 2007-10-24 株式会社日立製作所 内燃機関のバルブタイミング変更装置

Also Published As

Publication number Publication date
JP2008514853A (ja) 2008-05-08
MX2007003419A (es) 2007-05-23
CN101027463A (zh) 2007-08-29
KR20070057199A (ko) 2007-06-04
KR101185387B1 (ko) 2012-09-25
DE502005007631D1 (de) 2009-08-13
US20070169733A1 (en) 2007-07-26
JP4845888B2 (ja) 2011-12-28
CN100504041C (zh) 2009-06-24
WO2006034752A1 (de) 2006-04-06
BRPI0515941A (pt) 2008-08-12
US7584731B2 (en) 2009-09-08
ES2328381T3 (es) 2009-11-12
ATE435360T1 (de) 2009-07-15
EP1794420A1 (de) 2007-06-13
DE102004047817B3 (de) 2005-12-08

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