EP1605141B1 - Flügelzellen-Nockenwellenversteller - Google Patents

Flügelzellen-Nockenwellenversteller Download PDF

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Publication number
EP1605141B1
EP1605141B1 EP05010197.1A EP05010197A EP1605141B1 EP 1605141 B1 EP1605141 B1 EP 1605141B1 EP 05010197 A EP05010197 A EP 05010197A EP 1605141 B1 EP1605141 B1 EP 1605141B1
Authority
EP
European Patent Office
Prior art keywords
groove
vane
circular arc
camshaft adjuster
type camshaft
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.)
Active
Application number
EP05010197.1A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1605141A3 (de
EP1605141A2 (de
Inventor
Mike Kohrs
Hermann Golbach
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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Publication date
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Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP1605141A2 publication Critical patent/EP1605141A2/de
Publication of EP1605141A3 publication Critical patent/EP1605141A3/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D47/00—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D47/00—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts
    • B23D47/04—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts of devices for feeding, positioning, clamping, or rotating work
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D47/00—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts
    • B23D47/08—Sawing machines or sawing devices working with circular saw blades, characterised only by constructional features of particular parts of devices for bringing the circular saw blade to the workpiece or removing same therefrom
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23D—PLANING; SLOTTING; SHEARING; BROACHING; SAWING; FILING; SCRAPING; LIKE OPERATIONS FOR WORKING METAL BY REMOVING MATERIAL, NOT OTHERWISE PROVIDED FOR
    • B23D61/00—Tools for sawing machines or sawing devices; Clamping devices for these tools
    • B23D61/02—Circular saw blades
    • 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 vane-type camshaft adjuster with a stator, a rotor connectable to a camshaft having a plurality of radially projecting vanes inserted in vane grooves, wherein a vane groove has groove side surfaces, a groove bottom and the groove side surfaces undercut, rounded transition regions between the groove side surfaces and the groove bottom ,
  • Camshaft adjusters are used to change the timing for opening or closing the valves. The fixed angular relationship between the camshaft and the crankshaft driving it is thereby canceled and the timing can be optimally adjusted depending on the speed and other parameters. Camshaft adjusters allow a relative rotation of the camshaft to the crankshaft.
  • Known vane-type camshaft adjusters include a rotor having a plurality of radially projecting vanes which are urged radially outwardly against a stator housing by the force of a spring.
  • a stator On the stator a plurality of radially inwardly projecting stops are formed, which limit the adjustment movement of the rotor in both directions of rotation when the wings run against the stops.
  • the wings abut with their end edges on the stator, so that between each one wing side and the adjacent side of a stop of the stator, a chamber is formed, in which a fluid, usually the engine oil, is conveyed via a valve associated with the camshaft adjuster.
  • the stator serves on the one hand for separating and sealing the fluid chambers, on the other hand for fixing the adjustment angle between the camshaft and the crankshaft.
  • the torque introduced into the rotor is supported on the stator via the grooves in the grooves and hydraulically on the oil cushion in the stator chambers.
  • the force acting thereon on the wings in turn causes reaction forces in the groove of the rotor.
  • a force acts on the groove edge on the rotor outer diameter, the associated reaction force acts on the opposite groove side in the groove bottom.
  • the JP 11 159 309 discloses a vane phaser with vanes inserted in each groove of the rotor, the range of angular displacement between the rotor and the stator being defined by the contact between the vanes of the stator and the rotor.
  • the EP 1 229 216 A1 discloses a vane actuator with a stator and a rotor, wherein a locking pin is provided which communicates via a hydraulic fluid channel with one of the pressure chambers, wherein in the locked position of the locking pin of this hydraulic fluid channel is interrupted.
  • the US 2004/0074458 A1 discloses a vane-type adjuster according to the preamble of independent claim 1.
  • the invention is therefore based on the object to provide a vane-camshaft adjuster, occur in the lower voltages.
  • a vane-type camshaft adjuster of the type mentioned that the rounded transition areas are at least partially formed as the groove bottom undercut circular arc sections.
  • the groove bottom is not flat, but rather the corner regions are designed as arcuate sections that undercut the groove base. Only the central region of the groove bottom is flat, since there is a spring supported.
  • the solution according to the invention has the advantage that only minor manufacturing changes are required. Due to the optimized cross-section of the vane groove, the stress can be reduced, in particular in the transition region, so that higher-grade materials can be dispensed with, which results in cost savings.
  • the distance of the lower end of the groove side surface from the groove bottom to the groove width may be in a ratio of 0.4 to 0.55, in particular approximately 0.48. With these parameters, the stress concentration in the transition region can already be considerably reduced.
  • the groove width is sufficiently dimensioned so that the wings inserted into the wing groove can withstand the occurring forces.
  • the radius of the circular arc portions is 0.5 times to 0.6 times the distance of the lower end of the groove side surface from the groove bottom.
  • the radius may be 0.56 times the distance.
  • the horizontal distance of the center point of a circular arc portion from the symmetry line of the groove is 0.3 times to 0.4 times the groove width.
  • the value of 0.35 is particularly preferred.
  • the vertical distance of the center of the circular arc portion from the groove bottom may be 0.90 times to 0.99 times the radius of the circular arc portion. Particularly preferred is the value 0.95.
  • the specified geometric values and parameters are not rigid limits, they can be varied as long as this results in the desired voltage reduction.
  • a further optimization of the occurring stresses can be achieved if a groove side surface has a relief notch.
  • the geometric optimization is not limited to the rounded transition region, since the groove side surface also has an optimized shape. Due to the relief notch, the force flow is smoothly deflected from the upper edge of the groove in the direction of the rotor center in a wide arc, so that no high concentration of stress occurs in the groove bottom. The occurring forces and stresses are distributed more evenly by the relief notch, so that the material stress is reduced.
  • the relief notch is spaced from the groove base end of the groove side surface.
  • the wing is thus at the upper, outer end of the groove, further, the wing is located between the relief notch and the rounded portion near the groove bottom at the groove side surfaces so as to be guided in the groove.
  • a particularly effective voltage reduction can be achieved if the relief notch of the vane-type camshaft adjuster according to the invention is at least partially formed as a circular arc section.
  • a circular arc section is omitted on corners that could lead to an increase in voltage.
  • the nutground workede end of the relief notch is approximately perpendicular and the opposite end of the relief notch tangent to the groove side surface.
  • the radius of the circular arc section in the region of the groove bottom is selected such that it opens tangentially into the circular arc section of the relief notch. Accordingly, an envelope can be placed by the boundary of both arc sections, which has a certain radius.
  • Optimum stress ratios can be achieved if the radius of the circular arc section in the area of the relief notch is 0.75 times to 0.85 times the groove height. Particularly preferred is a value of 0.81.
  • the radius of the arcuate section in the area of the groove base may be approximately 0.20 times to 0.28 times the radius of the circular arc section in the region of the relief groove. Particularly preferred is a value of 0.24.
  • Fig. 1 1 shows a conventional vane-type phaser 1 comprising a stator 2 and a rotor 3 with a plurality of vanes 5 inserted in vane grooves 4.
  • the stator 2 is part of a chain or belt drive, whereby the rotation of the crankshaft is transmitted via a chain or a belt via the stator 2 and the rotor 3 to a camshaft.
  • the stator 2 has projections 6, which serve as stops for the wings 5.
  • Fig. 1 is the wing 5 in an end position.
  • In the rotor 3 are on the left and the right side of each wing groove 4 holes through which a fluid in a chamber adjacent to the wings 5 can flow in or out. By the incoming or outflowing fluid, a relative rotation between the rotor 3 and the stator 2 and thus between the crankshaft and the camshaft of an internal combustion engine is achieved.
  • Fig. 2 shows an enlarged section of Fig. 1 in the area of the wing groove 4.
  • the force acting on the wing 5 causes a reaction force 9 at the outer end of the groove side surface 10.
  • a further reaction force 11 is produced on the opposite groove side surface 12.
  • the forces 9, 11 cause a combined tensile and bending stress in the region of the transitions of the groove side surfaces 10, 12 towards the groove bottom 13.
  • the transition between the groove base 13 and the groove side surfaces 10, 12 is formed as an undercut in the Nutrich Chemistry, enter the Corner areas, especially in the Fig. 2 left corner shown very high stresses in the material.
  • Fig. 3 shows the vane groove of a camshaft adjuster according to the first embodiment of the invention.
  • the distance of the lower end of the groove side surface 15, 16 from the groove bottom 17 and the width of the wing groove 14 in a ratio of about 0.48 to each other.
  • the radius of the circular arc sections 18, 19 is 0.56 times the distance of the lower end of the groove side surfaces 15, 16 from the groove bottom 17.
  • the horizontal distance of the center of the circular arc section 18, 19 from the symmetry line of the wing groove 14 is the 0.35- times the width of the wing groove 14.
  • the vertical distance the center point of the circular arc sections 18, 19 to the groove bottom 17 is 0.95 times the radius of the circular arc sections 18, 19th
  • Fig. 4 shows the vane groove of a camshaft adjuster according to a second embodiment of the invention.
  • the wing groove has relief notches 28, 29 in the region of the groove side surfaces 26, 27.
  • the relief notches 28, 29 are spaced from the nutground solution end 30, 31 of the groove side surfaces 26, 27, so that a wing in this area on the Nutrich vom 26, 27 abuts and is guided.
  • the relief notches 28, 29 are at least partially formed as a circular arc portion having a radius 32.
  • the nutground workede end of the relief groove 28, 29, the Fig. 4 lower end, approximately perpendicular to the groove side surface 26, 27.
  • the opposite end, the in Fig. 4 upper end of the relief notch 28, 29 extends tangentially to the groove side surface 26, 27. Since the radius 32 of the relief notches 28, 29 at least partially coincides with the radius of the circular arc sections 33, 34 in the region of the groove bottom 35, the power flow from the upper edge of the groove in deflected in a wide arc, leaving in the corner areas, especially near the in Fig. 4 left arc section shown 33 the formation of stress concentrations is avoided.
  • the radius 36 of the circular arc section 33, 34 in the region of the groove bottom 35 is selected such that the circular arc section 33, 34 opens tangentially into the circular arc section of the relief notch 28, 29.
  • the radius 32 of the circular arc section in the region of the relief notch 28, 29 in the illustrated embodiment is 0.81 times the groove height 37.
  • the radius 36 of the circular arc section 33, 34 in the region of the groove bottom 35 is 0.24 times the radius 32 of the circular arc section in the region of the relief notch 28, 29.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP05010197.1A 2004-06-08 2005-05-11 Flügelzellen-Nockenwellenversteller Active EP1605141B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004027950 2004-06-08
DE102004027950A DE102004027950A1 (de) 2004-06-08 2004-06-08 Flügelzellen-Nockenwellenversteller

Publications (3)

Publication Number Publication Date
EP1605141A2 EP1605141A2 (de) 2005-12-14
EP1605141A3 EP1605141A3 (de) 2009-04-08
EP1605141B1 true EP1605141B1 (de) 2015-07-08

Family

ID=34936377

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05010197.1A Active EP1605141B1 (de) 2004-06-08 2005-05-11 Flügelzellen-Nockenwellenversteller

Country Status (5)

Country Link
US (1) US7188596B2 (ko)
EP (1) EP1605141B1 (ko)
KR (1) KR101239494B1 (ko)
CN (1) CN100543277C (ko)
DE (1) DE102004027950A1 (ko)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010019530A1 (de) * 2010-05-06 2011-11-10 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller und U-förmiges Dichtelement zum Abdichten einer radialen Fläche eines Flügels eines Nockenwellenverstellers
US9341089B2 (en) 2014-04-04 2016-05-17 RB Distribution, Inc. Camshaft phaser
EP3561243B1 (en) * 2018-04-26 2021-01-13 Volvo Car Corporation Camshaft arrangement

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020038501A1 (en) * 2000-10-04 2002-04-04 Kazutoshi Iwasaki Method for manufacturing valve timing adjusting apparatus
US20040074458A1 (en) * 2002-08-28 2004-04-22 Motoo Nakamura Valve timing control device

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ZA837328B (en) * 1982-10-14 1984-05-30 Pfd Ltd Manufacture of article having undercut internal surface
EP0848141B1 (en) * 1996-12-12 2002-07-17 Aisin Seiki Kabushiki Kaisha Valve timing control device
JP3812697B2 (ja) * 1997-09-29 2006-08-23 アイシン精機株式会社 弁開閉時期制御装置
JP3812137B2 (ja) * 1998-04-28 2006-08-23 アイシン精機株式会社 弁開閉時期制御装置
KR200221575Y1 (ko) * 1998-07-29 2001-09-29 구자홍 전자레인용 할로겐히터 커버
DE19860418B4 (de) * 1998-12-28 2008-09-11 Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Nockenwellen-Verstelleinrichtung mit Flügelrad
JP2001193421A (ja) * 1999-10-25 2001-07-17 Mitsubishi Electric Corp バルブタイミング調整装置
DE10064222B4 (de) * 1999-12-24 2006-02-09 Aisin Seiki K.K., Kariya Verstellbares Ventilsteuersystem
JP4595263B2 (ja) 2001-07-31 2010-12-08 アイシン精機株式会社 弁開閉時期制御装置
JP4165749B2 (ja) * 2003-08-04 2008-10-15 ヤマハ発動機株式会社 エンジンのバルブタイミング制御装置
JP4214972B2 (ja) * 2003-08-28 2009-01-28 アイシン精機株式会社 弁開閉時期制御装置
DE10355502A1 (de) * 2003-11-27 2005-06-23 Ina-Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Rotationskolben-Verstelleinrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE102004027951A1 (de) * 2004-06-08 2006-02-16 Ina-Schaeffler Kg Flügelzellen-Nockenwellenversteller

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20020038501A1 (en) * 2000-10-04 2002-04-04 Kazutoshi Iwasaki Method for manufacturing valve timing adjusting apparatus
US20040074458A1 (en) * 2002-08-28 2004-04-22 Motoo Nakamura Valve timing control device

Also Published As

Publication number Publication date
US7188596B2 (en) 2007-03-13
CN100543277C (zh) 2009-09-23
KR20060048224A (ko) 2006-05-18
US20050268874A1 (en) 2005-12-08
CN1707072A (zh) 2005-12-14
DE102004027950A1 (de) 2006-02-16
KR101239494B1 (ko) 2013-03-05
EP1605141A3 (de) 2009-04-08
EP1605141A2 (de) 2005-12-14

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