WO2009049977A1 - Régleur de phase pour un moteur à combustion interne avec un accouplement oldham - Google Patents

Régleur de phase pour un moteur à combustion interne avec un accouplement oldham Download PDF

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Publication number
WO2009049977A1
WO2009049977A1 PCT/EP2008/062161 EP2008062161W WO2009049977A1 WO 2009049977 A1 WO2009049977 A1 WO 2009049977A1 EP 2008062161 W EP2008062161 W EP 2008062161W WO 2009049977 A1 WO2009049977 A1 WO 2009049977A1
Authority
WO
WIPO (PCT)
Prior art keywords
oldham
phase adjuster
adjuster according
disc
actuator
Prior art date
Application number
PCT/EP2008/062161
Other languages
German (de)
English (en)
Inventor
Falko Arnold
Jens Schäfer
Jonathan Heywood
Original Assignee
Schaeffler Kg
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 Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2009049977A1 publication Critical patent/WO2009049977A1/fr

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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
    • 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
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
    • F16D3/04—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted to allow radial displacement, e.g. Oldham couplings

Definitions

  • the present invention relates to a phase adjuster for adjusting a relative angular position of two shafts according to the preamble of claim 1.
  • phase adjusters are used in particular in internal combustion engines for adjusting the relative angular position of a camshaft relative to a crankshaft and comprise an actuator with an output shaft, an actuator with an adjusting shaft, which is connected via an adjusting gear with the shaft to be adjusted, and between output shaft and Adjusting shaft arranged clutch.
  • Phase adjusters in internal combustion engines are preferably used to adjust the opening and closing times of the gas exchange valves (camshaft adjuster) or as a phaser for actuator shafts in variable valve trains.
  • Phase adjusters are arranged in a shaft system. About the drive shaft - z. B. a camshaft sprocket - drive power is supplied to the We- len system, which by means of the output shaft - z. B. the camshaft - is withdrawn again.
  • the phaser serves as a link between the drive shaft and the shaft to be driven. It allows, in addition to the drive power, to couple mechanical power into or out of the shaft system.
  • Phase adjusters can be subdivided into two main groups.
  • the first main group include phaser with an actuator, ie a functional unit which engages in the mass flow or energy flow, which is formed for example hydraulically, electrically or mechanically, and rotates with transmission elements of the camshaft adjuster.
  • the second main group comprises phase adjusters with a separate actuator, ie a functional unit, in which the control output required for the control of the actuator control variable is formed from the controller output, and a separate actuator.
  • the second main group has three types.
  • the first construction form phasing with a co-rotating actuator and a co-rotating actuator, such as a high-ratio gearbox, the actuating shaft can be advanced by a co-rotating hydraulic motor or centrifugal motor and can be reset by means of a spring.
  • the second design includes phasing with a co-rotating actuator and a stationary, motor-fixed actuator, such as an electric motor or an electric or mechanical brake.
  • phase adjusters are used in DE 100 38 354 A1, DE 102 05 034 A1 and EP 1 043 482 B2.
  • the third design includes phase adjuster with a directional combination of the solutions according to the first and second design, such as a motorized brake in which a part of the braking power is used to tension a spring, which allows the return adjustment after switching off the brake.
  • This design is used for example in DE 102 24 446 A1, WO 03 098010, DE 103 24 845 A1 and DE 103 17 607 A1.
  • the adjustment energy can take the form of a provision by means of a drive or a braking power and by utilizing power losses of the shaft system (eg friction) or of inertia or of centrifugal forces. Braking can also be under full utilization or shared use of Friction of the camshaft done.
  • a phase adjuster can be equipped with or without a mechanical limitation of the adjustment range.
  • three-shaft gear or multi-joint or coupling gear of the following types are used: swashplate gear, Exzentner- gear, planetary gear, wave gear, cam gear, multi-joint or coupling gear or combinations of the individual designs in a multi-stage design.
  • the actuator is usually attached to the camshaft by means of a central screw.
  • the actuator is attached to the cylinder head, that is on the side facing away from the camshaft side. Due to the manufacturing tolerances creates a radial, undesirable axis offset between the output shaft of the actuator and the adjusting of the actuator.
  • a coupling arranged between the output shaft and the adjusting shaft is intended to transmit the torque from the actuator or the drive torque for the actuating drive and at the same time compensate for the axial offset between the output shaft and the adjusting shaft.
  • a camshaft adjuster is known from DE 10 2004 041 751 A1, in which the transmission of the drive torque from an actuating shaft driven by a positioning gear takes place via an intermediate clutch to an adjusting gear.
  • the coupling comprises a first coupling half with a radial extension, which rests without play on a second coupling half in the circumferential direction and is displaceable in the radial direction relative to the second coupling half.
  • DE 10 2004 041 751 A1 describes an embodiment in which the force flow between the extension and the second coupling half takes place via an element which is elastic in the circumferential direction, for example a metal spring or a polymer strip. In addition to an elasticity in the circumferential direction, the elastic element can also be used for an axial ensure elastic connection.
  • the extension itself can have its own elasticity, so that it itself forms the elastic element.
  • the elastic element By deformation of the elastic element small axial offsets between the actuating shaft of the actuator and Verstellgetriebewelle can be compensated. In addition, a low-noise function is ensured, even if alternating torques occur at the Verstellgetriebewelle.
  • the central screw can not be mounted separately.
  • the maximum possible axial offsets that can be compensated are limited. Another disadvantage is that due to deformations caused by misalignment and the resulting stresses can lead to the destruction of the elastic element.
  • a valve timing control device for an internal combustion engine is known.
  • the angular position adjustment between crankshaft and camshaft is performed by a rotational phase control mechanism with an intermediate rotary member, which is adjusted by a braking mechanism with a hysteresis.
  • the hysteresis brake comprises a hysteresis ring which has a retaining plate.
  • the holding plate is connected to the intermediate rotary member.
  • the intermediate rotary member or the holding plate is provided with a radial groove, while the holding plate or the intermediate rotary member has a projection which is slidably received in the groove to move the intermediate rotary member radially relative to the Hysteresering.
  • an axial offset of the hysteresis brake can be compensated for the intermediate rotary member.
  • the realized between hysteresis and intermediate intermediate coupling works on the well-known Oldham principle.
  • Oldham couplings are well known in the art, so that an explanation of their basic construction and operation can be dispensed with at this point.
  • the object of the present invention is thus to provide a phase adjuster with an improved clutch, wherein the clutch should be characterized by a low-noise mode of operation and a minimum possible mass moment of inertia. As few components as possible, which are inexpensive to produce, should be used for the coupling. In addition, comparatively large axial offsets between the output shaft of the actuator and the adjusting shaft of the actuator can be compensated with the clutch.
  • phase adjuster according to the appended claim 1 is characterized in that the Oldham disc is made of plastic.
  • a significant advantage of the solution according to the invention is that a considerable reduction of the inertia of the adjusting shaft can be achieved by the use of plastic for the Oldham disc, since plastic has a much lower density compared to steel. Plastic also has very good damping properties, whereby a low-noise function of the clutch is ensured. Compared to conventional clutches using Oldham steel discs, the coupling according to the invention may have a much higher clearance due to the good damping properties of plastic, which does not ultimately lead to a reduction in manufacturing costs.
  • the Oldham disc consists of a thermoplastic material.
  • Components made of thermoplastic materials can be manufactured extremely cheap and are characterized by good performance properties.
  • Polyamides are suitable for the inventive design of the Oldham disk, especially reinforced polyamides.
  • the latter have a high rigidity and strength, as well as an extreme impact resistance. This makes them extremely robust against mechanical stress.
  • polyamides have very good sliding properties.
  • glass fiber reinforced polyamide such as PA 66 GF26 proved to be useful.
  • the Oldham disc four each offset by 90 ° to each other slots or slots.
  • the ends of the output shaft and the adjusting shaft facing the Oldham disc are connected to the slots or slots of the Oldham disc via two respective opposing bolts.
  • either the serving for connecting the output shaft bolts or serving for connecting the adjusting shaft bolts are provided with a head.
  • two opposing bores are introduced into the end faces of the output shaft and the adjusting shaft facing the Oldham disk. In these holes, the bolts are inserted.
  • the second embodiment uses separate connecting washers for fixing the bolts, which are fastened to the ends of the output shaft and the adjusting shaft facing the Oldham disk.
  • the connecting disks each have two opposing bores for fastening the bolts.
  • a drive element is arranged on the end of the output shaft facing the Oldham disc.
  • the bolts used for engagement with the oblong holes or slots of the Oldham disc are formed in this embodiment as extensions of the drive element.
  • the comparatively complex drive element of the third embodiment can be manufactured inexpensively.
  • it can be sintered or as the Oldham disc are made of plastic.
  • the use of the drive element also has a positive effect on the mass moment of inertia.
  • the Oldham disc on a matched to the expected stress wall thickness.
  • the Oldham disc is provided with ribbing.
  • ribbing a high rigidity of the Oldham disc can be realized even with a relatively small wall thickness, in turn, an optimization in terms of mass or inertia can be achieved.
  • FIG. 1 shows a camshaft adjuster according to the prior art in a simplified representation
  • FIG. 2 shows components of a first embodiment of a coupling used in a phase-wave adjuster according to the invention in a schematic illustration
  • FIG. 1 shows a camshaft adjuster according to the prior art in a simplified representation
  • FIG. 2 shows components of a first embodiment of a coupling used in a phase-wave adjuster according to the invention in a schematic illustration
  • FIG. 3 shows the assembled coupling according to FIG. 2 in a schematic sectional representation
  • FIG. 5 the coupling of FIG. 4 in an exploded view.
  • Fig. 1 shows a camshaft adjuster for an internal combustion engine according to the prior art in a simplified representation.
  • the camshaft adjuster serves to adjust the relative angular position of a camshaft 01 with respect to a crankshaft in drive connection with a drive wheel 03.
  • the camshaft adjuster comprises an actuator 05 with an output shaft (not shown) and an actuator 07 with an adjusting shaft 08. Between the output shaft and adjusting shaft 08, a clutch (not shown) is arranged.
  • an electric motor or a brake can be used as an actuator 05.
  • the actuator 05 is mounted on the cylinder head 09 or another engine-fixed part of the internal combustion engine.
  • As actuator 07 is usually a transmission with high translation used.
  • the actuator 07 is attached to the camshaft 01 via a central screw, not shown.
  • the camshaft is subject to the operation of the Internal combustion engine radial operating vibrations. This offset must be compensated by means of the coupling. The vibrations should not be transmitted to the actuator, which is also to be prevented by the coupling.
  • FIGS. 2 and 3 show the individual components of the clutch and FIG. 3 shows the assembled clutch in a schematic representation.
  • the clutch comprises two connecting discs 11 and an Oldham disc 12.
  • the Oldham disc 12 In the Oldham disc 12 four each offset by 90 ° to each other slots or slots 13 are introduced.
  • the Oldham disc 12 is made of plastic, preferably of a thermoplastic material, such as PA 66 GF26.
  • the connecting discs 11 are made similar in the illustrated embodiment. In the connecting discs 11 two holes 14 are respectively introduced, which serve to receive bolts 15, 16.
  • the bolts 15, 16 differ in that the first bolts 15 are made without a head and the second bolts 16 are provided with a head.
  • a connecting disk 11 is fastened on the output shaft of the actuator 05 and the adjusting shaft 08 of the actuator 07.
  • the connecting discs 11 are connected via the bolts 15, 16 with the Oldham disc 12.
  • the Oldham disc 12 has a central opening 17 through which the adjusting mechanism can be secured to the camshaft by means of the central screw.
  • the drive-side connecting disk 11 must have an opening which is at least as large for the passage of the central screw.
  • FIG. 3 are two sectional views of each rotated by 90 ° coupling shown, so that in Fig. A) the connection of the Oldham disc 12 with the connecting disc 11 toward the output shaft of the actuator by means of the first bolt 15 and in Fig. B) the Connection of the Oldham disc 12 with the Stellwellen matteren connection disc 11 by means of the second bolt 16 can be seen.
  • the first bolts 15 are used to connect the connecting disk 11 arranged on the output shaft of the actuator 05 to the Oldham disk 12.
  • the second bolts 16 connect the connecting disk 11 arranged on the adjusting shaft 08 of the actuator 07 to the Oldham 12. Due to the fact that the second bolts 16 are designed with heads, the Oldham disk 12 is in this case axially bound to the connecting disk 11 of the adjusting shaft 08.
  • the second pin 16 may also serve to couple the connecting disk 11 of the output shaft of the actuator 05 with the Oldham disk 12.
  • the Oldham disc 12 would be bound in this case to the connecting disk 11 of the output shaft.
  • An axial offset present between the output shaft and the adjusting shaft 08 can be compensated by the play of the bolts 15, 16 in the oblong holes or slots 13 of the Oldham disk 12.
  • connection disc 11 to be fastened to the actuator 07 When carrying out the connection disc 11 to be fastened to the actuator 07, it should be noted that the inner diameter of the connecting disc 11 must be selected to be so large that the central screw can be carried out.
  • the connection disc 11 to be fastened to the output shaft of the actuator 05 does not have to allow the central screw to be passed through and can therefore be optimized in terms of mass and inertia.
  • the Oldham disc 12 is modified such that the slits 13 provided for receiving the output shaft-side connecting disc 13 extend into the central opening 17 of the Oldham disc 12. Therefore, in this embodiment, instead of the connecting disk 11, a drive element 18 arranged on the output shaft 19 of the actuator 05 can also be used.
  • the drive member 18 has extensions 20 which, like the bolts 15 described above, serve to engage in the oblong holes or slots 13 of the Oldham disk 12. By using a comparatively small NEN drive element, a further reduction of the moment of inertia can be achieved.
  • the Anthebselement 18 may also be made in one piece with the output shaft.
  • the Oldham disc has 12 ribs. By this ribbing the mass of the Oldham disc 12 can be further reduced and still a high rigidity can be achieved.
  • the coupling can alternatively be constructed without connecting disks 11.
  • the holes used for fastening the bolts 15, 16 are introduced directly into the end faces of the ends of the output shaft of the actuator 05 and the adjusting shaft 08 of the actuator 07.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un régleur de phase, en particulier pour un moteur à combustion interne, pour régler la position angulaire relative d'un arbre à cames (01) par rapport à un vilebrequin, comprenant : un actionneur (05) doté d'un arbre de sortie (19); un organe de réglage (07) pourvu d'un arbre de réglage (08) qui est relié à l'arbre à cames (01) par l'intermédiaire d'un mécanisme de réglage; et un accouplement Oldham, disposé entre l'arbre de sortie (19) et l'arbre de réglage (08) et pourvu d'un disque Oldham (12). Le régleur de phase selon l'invention est caractérisé par le fait que le disque Oldham (12) de l'accouplement Oldham est réalisé en matière plastique.
PCT/EP2008/062161 2007-10-12 2008-09-12 Régleur de phase pour un moteur à combustion interne avec un accouplement oldham WO2009049977A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007049072.2 2007-10-12
DE102007049072.2A DE102007049072B4 (de) 2007-10-12 2007-10-12 Phasenversteller für eine Brennkraftmaschine mit einer Oldham-Kupplung

Publications (1)

Publication Number Publication Date
WO2009049977A1 true WO2009049977A1 (fr) 2009-04-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/062161 WO2009049977A1 (fr) 2007-10-12 2008-09-12 Régleur de phase pour un moteur à combustion interne avec un accouplement oldham

Country Status (2)

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DE (1) DE102007049072B4 (fr)
WO (1) WO2009049977A1 (fr)

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WO2016031557A1 (fr) * 2014-08-25 2016-03-03 アイシン精機株式会社 Dispositif synchronisateur d'ouverture/fermeture d'une soupape

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DE102009037403B4 (de) * 2009-08-13 2018-01-11 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller
DE102011103495A1 (de) 2011-06-03 2012-12-06 Magna Powertrain Ag & Co. Kg Kupplungswelle,Aktor,Nockenwellenverstellgetriebe und Nockenwellensteller
WO2014016242A1 (fr) * 2012-07-25 2014-01-30 Hilite Germany Gmbh Engrenage déphaseur d'arbre à cames
DE102012223811A1 (de) 2012-12-19 2014-06-26 Mahle International Gmbh Nockenwelle
DE102014218234B4 (de) 2014-09-11 2023-05-11 Schaeffler Technologies AG & Co. KG Oldhamkupplung und Verfahren zur Herstellung einer Oldhamkupplung
DE102014219364B4 (de) 2014-09-25 2016-07-07 Schaeffler Technologies AG & Co. KG Oldhamkupplung
DE102015201104B3 (de) * 2015-01-23 2016-07-21 Schaeffler Technologies AG & Co. KG Oldhamkupplung
DE102015201103A1 (de) 2015-01-23 2016-07-28 Schaeffler Technologies AG & Co. KG Pressverbindungen von stanzpaketierten Bauteilen mit Wellen
DE102015103132A1 (de) * 2015-03-04 2016-09-08 Ovalo Gmbh Nockenwellenversteller
DE102015206411A1 (de) 2015-04-10 2016-10-13 Schaeffler Technologies AG & Co. KG Oldhamkupplung
DE102015212435A1 (de) 2015-07-02 2017-01-05 Schaeffler Technologies AG & Co. KG Oldhamkupplung
DE102015213272A1 (de) * 2015-07-15 2017-01-19 Schaeffler Technologies AG & Co. KG Drehstarre Ausgleichskupplung und Vorrichtung mit einer solchen
DE102015223903A1 (de) 2015-12-01 2017-06-01 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102015223904B3 (de) * 2015-12-01 2017-03-02 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE202015009214U1 (de) 2015-12-01 2016-11-29 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016204017B3 (de) * 2016-03-11 2017-02-16 Schaeffler Technologies AG & Co. KG Wellgetriebe
DE102016220854B4 (de) 2016-10-24 2018-07-05 Schaeffler Technologies AG & Co. KG Verstellvorrichtung
DE102016222773B3 (de) * 2016-11-18 2018-01-25 Schaeffler Technologies AG & Co. KG Ausgleichskupplung
DE102016222772B3 (de) 2016-11-18 2018-04-26 Schaeffler Technologies AG & Co. KG Ausgleichskupplung
DE102016222884A1 (de) * 2016-11-21 2018-01-18 Schaeffler Technologies AG & Co. KG Getriebeelement für ein Spannungswellengetriebe
DE102016222898A1 (de) 2016-11-21 2018-05-24 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung sowie Wellgetriebe mit der Kupplungsvorrichtung
DE102016222897B4 (de) 2016-11-21 2018-07-12 Schaeffler Technologies AG & Co. KG Kupplungsvorrichtung sowie Wellgetriebe mit der Kupplungsvorrichtung
DE102016222895A1 (de) 2016-11-21 2018-04-05 Schaeffler Technologies AG & Co. KG Kupplungselement
DE102016223372A1 (de) 2016-11-25 2017-11-02 Schaeffler Technologies AG & Co. KG Verstellgetriebe
DE102016223803B4 (de) 2016-11-30 2018-07-19 Schaeffler Technologies AG & Co. KG Kupplungsanordnung zur Verbindung eines elektrischen Antriebs mit einem Verstellgetriebe eines Nockenwellenverstellers zur variablen Ventilsteuerung einer Brennkraftmaschine
DE102018104232B3 (de) 2018-02-26 2019-05-09 Schaeffler Technologies AG & Co. KG Oldhamelement für eine Ausgleichskupplung
DE102019118779A1 (de) * 2019-07-11 2021-01-14 Schaeffler Technologies AG & Co. KG Verstellvorrichtung
DE202022106707U1 (de) 2022-11-30 2024-03-06 Grimme Landmaschinenfabrik GmbH & Co. KG Kupplungsvorrichtung für eine landwirtschaftliche Arbeitsmaschine und landwirtschaftliche Arbeitsmaschine

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US5583630A (en) * 1993-05-25 1996-12-10 Ricoh Company, Ltd. Oldham coupling for a revolving type developing device
EP1069330A2 (fr) * 1999-07-15 2001-01-17 Koyo Seiko Co., Ltd. Couplage de transmission de puissance et dispositif de transmission de puissance
WO2003021125A1 (fr) * 2001-08-31 2003-03-13 Cts Corporation Systeme de compensation d'excentricite a faible hysteresis, a utiliser entre deux arbres rotatifs non coaxiaux
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Publication number Priority date Publication date Assignee Title
WO2016031557A1 (fr) * 2014-08-25 2016-03-03 アイシン精機株式会社 Dispositif synchronisateur d'ouverture/fermeture d'une soupape
JP2016044627A (ja) * 2014-08-25 2016-04-04 アイシン精機株式会社 弁開閉時期制御装置
CN106460590A (zh) * 2014-08-25 2017-02-22 爱信精机株式会社 阀正时控制装置

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DE102007049072A1 (de) 2009-04-16
DE102007049072B4 (de) 2020-06-18

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