EP2604817B1 - Dispositif de réglage d'arbres à came - Google Patents

Dispositif de réglage d'arbres à came Download PDF

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Publication number
EP2604817B1
EP2604817B1 EP12181619.3A EP12181619A EP2604817B1 EP 2604817 B1 EP2604817 B1 EP 2604817B1 EP 12181619 A EP12181619 A EP 12181619A EP 2604817 B1 EP2604817 B1 EP 2604817B1
Authority
EP
European Patent Office
Prior art keywords
spring
lubricant
camshaft adjuster
lubricant reservoir
groove
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
EP12181619.3A
Other languages
German (de)
English (en)
Other versions
EP2604817A1 (fr
Inventor
Jürgen Weber
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
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 Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of EP2604817A1 publication Critical patent/EP2604817A1/fr
Application granted granted Critical
Publication of EP2604817B1 publication Critical patent/EP2604817B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46Component parts, details, or accessories, not provided for in preceding subgroups
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01LCYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34Valve-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
    • F01L1/344Valve-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
    • F01L1/3442Valve-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

Definitions

  • the invention relates to a camshaft adjuster.
  • Camshaft adjusters are used in internal combustion engines to vary the timing of the combustion chamber valves in order to make the phase relation between the crankshaft and the camshaft in a defined angular range, between a maximum early and a maximum late position variable. Adjusting the timing to the current load and speed reduces fuel consumption and emissions.
  • camshaft adjuster are integrated into a drive train, via which a torque is transmitted from the crankshaft to the camshaft.
  • This drive train may be formed for example as a belt, chain or gear drive.
  • the output element and the drive element form one or more pairs of mutually acting pressure chambers, which can be acted upon by hydraulic fluid.
  • the drive element and the output element are arranged coaxially. By filling and emptying individual pressure chambers, a relative movement between the drive element and the output element is generated.
  • the rotationally acting on between the drive element and the output element spring urges the drive element relative to the output element in an advantageous direction. This advantage direction can be the same or opposite to the direction of rotation.
  • the vane cell adjuster comprises a stator, a rotor and a drive wheel with an external toothing.
  • the rotor is designed as a driven element usually rotatably connected to the camshaft.
  • the drive element includes the stator and the drive wheel.
  • the stator and the drive wheel are rotatably connected to each other or alternatively formed integrally with each other.
  • the rotor is coaxial with the stator and located inside the stator.
  • the rotor and the stator are characterized by their, radially extending wings, oppositely acting oil chambers, which are acted upon by oil pressure and allow relative rotation between the stator and the rotor.
  • the wings are either formed integrally with the rotor or the stator or arranged as "inserted wings" in designated grooves of the rotor or the stator.
  • the vane cell adjusters have various sealing lids. The stator and the sealing lids are secured together via several screw connections.
  • a displacement element is axially displaced via oil pressure, which generates a helical gear teeth relative rotation between a drive element and an output element.
  • camshaft adjuster Another design of a camshaft adjuster is the electromechanical camshaft adjuster, which has a three-shaft gear (for example, a planetary gear). One of the shafts forms the drive element and a second shaft forms the output element. About the third wave, the system by means of an adjusting device, such as an electric motor or a brake, rotational energy supplied or removed from the system. A spring may additionally be arranged, which supports or returns the relative rotation between the drive element and output element.
  • adjusting device such as an electric motor or a brake
  • the DE 10 2006 002 993 A1 shows a phaser with a sprocket, a rotor, a housing and a spring.
  • the housing and the rotor form the working chambers for relative rotation.
  • the sprocket is rotatably connected to the housing.
  • the spring is arranged outside of the housing and is protected by an additional spring cover, which is connected to the sprocket, against external contamination and thus against life shortening foreign influence as far as possible.
  • the rotor has a pin passing through the housing which provides support for a spring base of the spring.
  • the object of the invention is to provide a camshaft adjuster, which increases the life of the spring.
  • lubricant depots which can provide and provide lubricant for the contact point.
  • a resilient lubricant film builds up between the spring wire of the spring and the spring bearing, which minimizes the sliding friction resulting from the relative movement between the spring wire and the spring bearing.
  • the minimized sliding friction leads to less abrasion of the spring bearing and / or on the spring wire, which is significantly increased just at load limit near dimensioning of spring wire and spring bearing life of the spring and / or the spring bearing.
  • the resulting by the minimized wear particles are collected by the lubricant depot and transported away from the contact point between the spring wire and spring bearing.
  • the formation of a suspension Particles and lubricants at the point of contact, which would further increase wear as time progresses, are avoided.
  • the particles are either discharged from the contact between the spring wire and the spring bearing to the environment, or can collect in the lubricant reservoir at a remote location to the lubricant film, for example, at the bottom of the depot.
  • the lubricant reservoir is defined as a region between a two-line contact of the spring wire with the associated spring bearing.
  • the area between the two line contacts has a distance of the spring to the spring bearing.
  • the resulting space may already contain lubricant or lubricant can be supplied to it.
  • the term two-line contact also includes a two-point contact which, as a result of the relative movement of the two contact partners, converts into a two-line contact after the operating time has progressed.
  • a planar design of the spring bearing with a curvature of a spring coil of any cross-section form such a two-line contact.
  • the planar design of the spring bearing may have a curvature many times smaller than that of the spring coil.
  • it can thus be transverse to the winding direction, or to the course of the spring wire, e.g. Liquid lubricant to be supplied to the lubricant depot.
  • Liquid lubricant to be supplied to the lubricant depot.
  • the lubricant reservoir is designed as a pocket.
  • a pocket any form of well is understood, which is clearly delimited from the lateral surface of the spring bearing and also has a depth.
  • the shape of the demarcation can be square, rectangular, triangular, polygonal, oval and / or circular and their border closed or opened.
  • Such a bag may be filled with liquid lubricant or filled during operation.
  • the bag already solid lubricant, eg graphite.
  • solid lubricants metals with good sliding properties can be used in the bag.
  • the lubricant reservoir is formed as a groove.
  • a groove resembles the bag's definition and also has the delimitation and the depth, but with the peculiarity that one dimension of the delineation, the length, is many times greater than the other, and thus defines the direction of the orientation.
  • the boundary of the boundary does not have to be self-contained.
  • the border of the groove is open at a shorter demarcation section.
  • the cross-section of the groove can take on any shape for producing the groove.
  • the orientation of the groove may be longitudinal, transverse or oblique relative to the direction of extension of the spring wire of the spring.
  • the length of the groove is advantageously not limited to the wire thickness of the spring, but protrudes on both sides or on one side beyond the spring wire.
  • a plurality of grooves distributed over the area of contact of the spring to the spring bearing is advantageous because the reliability of a single lubrication is distributed to a plurality of lubricant depots.
  • the groove formed as a lubricant reservoir is arranged transversely or obliquely to the spring wire of the spring. Transverse is almost an angle of 90 ° between the course of the spring wire and the longitudinal direction of the groove. An angle of almost 0 ° corresponds to the term longitudinal and obliquely, each angle between transverse and longitudinal to consider. In contrast to the longitudinal orientation, it is advantageously an oblique or To select transverse profile of the groove, because then the effect is minimized that the lubricant is displaced from the groove by the relative movement and the lubricant depot no lubricant is stored more.
  • the trained as a groove lubricant reservoir is formed circumferentially.
  • Circumferential grooves are particularly suitable for spring bearings with rotationally symmetrical shape.
  • Circumferential grooves may be partially circumferential or completely circumferential.
  • a completely circumferential groove, formed as a groove, combines their beginning and end together.
  • the width of the groove is smaller than that of the spring wire, so that sufficient lateral surface of the spring bearing remains outside the groove.
  • the groove is disposed within the projected onto the spring bearing surface of the spring wire.
  • the lubricant reservoir is formed as a slot.
  • the slot extends, as a deep groove, through the wall of the spring bearing.
  • the particles resulting from the minimized wear can be better dissipated or flushed out.
  • the width of the slot is sized so that liquid lubricant can be stored within the slot.
  • the spring bearing is designed as a pin.
  • the pin can be rotationally symmetrical shape.
  • Rotationally symmetrical pins as a spring bearing can be pins, hub sections or studs formed integrally on the drive element or driven element.
  • pins may have a stepped diameter for spring mounting.
  • designed as a stepped diameter pins have an implied stop for the spring wire transverse to the direction of extension of the spring wire, so that slippage of the spring wire on the spring bearing is largely counteracted.
  • such trained as a remote diameter pin can be arranged at the free end of a mounting screw and use for spring mounting. at the same time the pins on the aforementioned training of the lubricant depot.
  • the lubricant reservoir is produced by forming.
  • a manufactured by forming lubricant depot has an increased strength, which has a particularly advantageous effect on the minimization of the wear behavior of the bearing.
  • smoothed surfaces of the bearing are achieved, which further minimize abrasion.
  • the lubricant depot is designed as a solid lubricant body.
  • This solid lubricant can in a recording, such as a groove mentioned above, bag or similar. be introduced and remain there over the service life of the camshaft adjuster.
  • Solid lubricants may be metals with good sliding properties, graphite, carburized by case hardening, or coatings.
  • the lubricant body as a lubricant reservoir may be formed either as a component separate from the spring mounting, e.g. be formed as a sleeve, ring, plate, or as integrally formed with the spring bearing lubricant depot. This training can be extended by the preceding materials and / or training forms.
  • Fig. 1 shows a section through a camshaft adjuster 1 with the lubricant depot 6 according to the invention.
  • the function and structure of the camshaft adjuster 1, in particular in vane-type construction, with the drive element 2 and the output element 3 is sufficiently known from the prior art.
  • This camshaft adjuster 1 is provided with a spring 4, which supports the relative rotation between the drive element 2 and driven element 3 in at least one direction of rotation.
  • the spring 4 is mounted by means of spring bearings 5 of the drive element 2 and the driven element 3.
  • the spring bearings 5 are firmly connected to the drive element 2 and the output element 3, respectively.
  • the screw 15 extends through an opening 16 of the drive element 2 and connects the side cover 17 with the drive element 2 rotatably with each other.
  • a nut 18 is anchored in one of the side cover 17, which has the matching thread for the screw 15.
  • a pin 9 of the screw 15 is formed at the end facing away from the screw head of the screw 15.
  • the pin 9 has a smaller diameter than the thread of the screw 15 and is rotationally symmetrical.
  • the pin 9 as a spring bearing 5 is a plurality, extending in the axial direction 19 and provided on the circumference of the pin 9 distributed grooves 7.
  • the grooves 7 are formed as lubricant depots 6. Further details of the spring bearing 5 follow in the Fig. 2 ,
  • Fig. 2 shows a detailed view of the lubricant reservoir 6 after Fig. 1 ,
  • the trained as lubricant depots 6 grooves 7 are distributed uniformly over the circumference of the pin 9.
  • the grooves 7 are formed open at the free end of the pin 9 in the axial direction 19.
  • the lubricant depots 6 are arranged, in particular in contact between the spring wire 10 of the spring 4 and the spring bearing 5.
  • oil or grease is stored, which lubricates the contact between spring wire 10 and spring bearing 5.
  • solid lubricants e.g. Graphite, to be stored. Either the lubricants stored in the lubricant reservoir 6 have been introduced before the assembly of the camshaft adjuster 1 or the lubricant reservoir 6 is provided for storage of leakage oil of the camshaft adjuster 1 during operation.
  • the pin 9 may be formed by a pin or in one piece with one of the side cover 17, the nut 18, the drive element 2 or the driven element 3.
  • the aforementioned difference in diameter between pins 9 and, for example, the screw 15 can be omitted.
  • a stop for the spring wire 10 in the axial direction 19 is formed by the difference in diameter.
  • Fig. 3 shows a first alternative embodiment of the lubricant reservoir 6 after Fig. 2
  • the grooves 7 formed as lubricant depots 6 are formed in the circumferential direction about the axis of symmetry 20 of the pin 9 and the spring bearing 5.
  • Two spaced from each other in the axial direction 19 grooves 7 provide the lubricant reservoir 6 in the contact area between spring wire 10 and spring bearing 5.
  • the grooves 7 may have mutually different cross-sectional shapes, or, as shown in the embodiment, have the same cross-sectional shape.
  • the contact length between spring wire 10 and spring bearing 5 in the axial direction 19 is indeed interrupted by the grooves 7, however, the load on the peripheral surface of the spring bearing 5 and the lubricant in the lubricant reservoir 6 is distributed, which is a particularly advantageous lubrication and thereby increasing the carrying capacity and life has the consequence.
  • the lubricant may be introduced prior to assembly or during operation.
  • Fig. 4 shows a second alternative embodiment of the lubricant reservoir 6 after Fig. 2 ,
  • This lubricant reservoir 6 is designed as a pocket 8.
  • the circumferential surface of the pin 9 and the spring bearing 5 is deviating from the original peripheral surface to the symmetry axis 20, so that a kind of trough or pocket 8 is formed.
  • This pocket 8 has the lubricant reservoir 6.
  • this pocket 8 is formed on a pin or in one piece with the peripheral components formed pin 9. Training on a screw 15 proves to be disadvantageous in that when screwing the screw 15, the orientation of the pocket 8 must be ensured for contact with the spring wire 10.
  • the lubricant may be introduced prior to assembly or during operation.
  • Fig. 5 shows a third alternative embodiment of the lubricant reservoir 6 after Fig. 2 ,
  • the spring bearing 5 is formed as a square.
  • the lubricant reservoir 6 is formed as a region 12 between a two-line contact 13.
  • the two-line contact 13 is formed by the curvature of the spring wire 10 and the planar design of the spring bearing 5.
  • the area 12 of the two-line contact 13 is formed by the curvature of the spring wire 10 as a cavity in the lubricant is stored.
  • the lubricant may be introduced prior to assembly or during operation.
  • Fig. 6 shows a fourth, alternative embodiment of the lubricant reservoir 6 after Fig. 2 ,
  • the lubricant reservoir 6 is formed as a slot 11 of the spring bearing 5.
  • the slot 11 extends radially through the entire spring bearing 5 therethrough.
  • the orientation of the slot 11 to the spring wire 10 is selected so that an open side of the slot 11 facing the spring wire 10 in contact between spring wire 10 and spring bearing 5.
  • the lubricant may be introduced prior to assembly or during operation.
  • Fig. 7 shows a fifth, alternative embodiment of the lubricant reservoir 6 after Fig. 2 .
  • the lubricant reservoir 6 exhibiting component 21 is arranged.
  • This here annular member 21 has a larger diameter than the spring bearing 5, which is designed as a rotationally symmetrical pin 9.
  • the component 21 may advantageously have solid lubricant.
  • materials such as graphite or metals with good sliding properties, such as non-ferrous metals, are suitable.
  • Another variant is to produce the component 21 from a sintered material and to infiltrate with the lubricant.

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)

Claims (10)

  1. Dispositif de réglage d'arbre à cames (1) comprenant un élément d'entraînement (2), un élément de sortie (3) et un ressort (4), l'élément d'entraînement (2) et l'élément de sortie (3) pouvant tourner l'un par rapport à l'autre, le ressort (4) étant fixé par un support de ressort (5) de l'élément d'entraînement (2) et par un support de ressort (5) de l'élément de sortie (3), le ressort (4) supportant la rotation relative entre l'élément d'entraînement (2) et l'élément de sortie (3), caractérisé en ce qu'un dépôt de lubrifiant (6) est prévu entre le fil de ressort (10) du ressort (4) et ses supports de ressort (5), afin de lubrifier le contact entre le fil de ressort (10) et le support de ressort (5).
  2. Dispositif de réglage d'arbre à cames (1) selon la revendication 1, caractérisé en ce que le dépôt de lubrifiant (6) est défini en tant que région (12) entre un contact bilinéaire (13) du fil de ressort (10) avec le support de ressort associé (5).
  3. Dispositif de réglage d' arbre à cames (1) selon la revendication 1, caractérisé en ce que le dépôt de lubrifiant (6) est réalisé sous forme de cavité (8) .
  4. Dispositif de réglage d'arbre à cames (1) selon la revendication 1, caractérisé en ce que le dépôt de lubrifiant (6) est réalisé sous forme de rainure (7) .
  5. Dispositif de réglage d'arbre à cames (1) selon la revendication 4, caractérisé en ce que le dépôt de lubrifiant (6) réalisé sous forme de rainure (7) est disposé transversalement ou obliquement par rapport au fil de ressort (10).
  6. Dispositif de réglage d'arbre à cames (1) selon la revendication 4, caractérisé en ce que le dépôt de lubrifiant (6) réalisé sous forme de rainure (7) est réalisé sous forme périphérique.
  7. Dispositif de réglage d'arbre à cames (1) selon la revendication 1, caractérisé en ce que le dépôt de lubrifiant (6) est réalisé sous forme de fente (11).
  8. Dispositif de réglage d'arbre à cames (1) selon la revendication 1, caractérisé en ce que le support de ressort (5) est réalisé sous forme de tourillons (9).
  9. Dispositif de réglage d'arbre à cames (1) selon la revendication 1, caractérisé en ce que le dépôt de lubrifiant (6) est fabriqué par formage.
  10. Dispositif de réglage d'arbre à cames (1) selon la revendication 1, caractérisé en ce que le dépôt de lubrifiant (6) est réalisé sous forme de corps lubrifiant solide (14).
EP12181619.3A 2011-12-12 2012-08-24 Dispositif de réglage d'arbres à came Not-in-force EP2604817B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011088295A DE102011088295A1 (de) 2011-12-12 2011-12-12 Nockenwellenversteller

Publications (2)

Publication Number Publication Date
EP2604817A1 EP2604817A1 (fr) 2013-06-19
EP2604817B1 true EP2604817B1 (fr) 2014-10-15

Family

ID=46967959

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12181619.3A Not-in-force EP2604817B1 (fr) 2011-12-12 2012-08-24 Dispositif de réglage d'arbres à came

Country Status (4)

Country Link
US (1) US8925507B2 (fr)
EP (1) EP2604817B1 (fr)
CN (1) CN103161540B (fr)
DE (1) DE102011088295A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011081971A1 (de) * 2011-09-01 2013-03-07 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102013206672A1 (de) * 2013-04-15 2014-10-16 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102013216182A1 (de) 2013-08-14 2015-02-19 Schaeffler Technologies Gmbh & Co. Kg Verstelleinrichtung, insbesondere für Brennkraftmaschinen
US11994043B2 (en) 2022-03-03 2024-05-28 Schaeffler Technologies AG & Co. KG Contaminant pathway for camshaft phaser

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10007200A1 (de) 2000-02-17 2001-08-23 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP2005061261A (ja) * 2003-08-08 2005-03-10 Hitachi Unisia Automotive Ltd 内燃機関の可変動弁装置
JP2005240651A (ja) * 2004-02-25 2005-09-08 Aisin Seiki Co Ltd 弁開閉時期制御装置
DE102006002993A1 (de) 2006-01-21 2007-08-09 Schaeffler Kg Nockenwellenversteller für eine Brennkraftmaschine
DE102008048386B4 (de) * 2008-09-22 2016-12-01 Hilite Germany Gmbh Flügelzellennockenwellenversteller
DE102008056796A1 (de) * 2008-11-11 2010-05-12 Schaeffler Kg Rotationskolbenversteller mit Drehfeder

Also Published As

Publication number Publication date
DE102011088295A1 (de) 2013-06-13
CN103161540B (zh) 2017-07-21
US20130180482A1 (en) 2013-07-18
US8925507B2 (en) 2015-01-06
EP2604817A1 (fr) 2013-06-19
CN103161540A (zh) 2013-06-19

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