EP2531702B1 - Dispositif pour modifier les temps de réglage de soupapes de renouvellement des gaz d'un moteur à combustion interne - Google Patents

Dispositif pour modifier les temps de réglage de soupapes de renouvellement des gaz d'un moteur à combustion interne Download PDF

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Publication number
EP2531702B1
EP2531702B1 EP11700264.2A EP11700264A EP2531702B1 EP 2531702 B1 EP2531702 B1 EP 2531702B1 EP 11700264 A EP11700264 A EP 11700264A EP 2531702 B1 EP2531702 B1 EP 2531702B1
Authority
EP
European Patent Office
Prior art keywords
latching
spring
radial
cover
latching hook
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
EP11700264.2A
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German (de)
English (en)
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EP2531702A2 (fr
Inventor
Christian Bösel
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
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Schaeffler Technologies AG and Co KG
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Publication of EP2531702A2 publication Critical patent/EP2531702A2/fr
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Publication of EP2531702B1 publication Critical patent/EP2531702B1/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
    • F01L1/3442—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

Definitions

  • the invention relates to a device for changing the timing of gas exchange valves of an internal combustion engine, comprising a stator and a rotor therein, which is adjustable by a pressure medium in the circumferential direction relative to the stator, wherein the rotor is connectable to a camshaft, further comprising a front cover plate and a rear cover plate, between which the stator and the rotor are received, wherein the rear cover plate is provided with a connectable with a crankshaft drive wheel, and a torsion spring for rotating the rotor relative to the stator.
  • a camshaft adjusting device with the same structure is known from DE 10 2009 005 114 A1 known.
  • the device In modern internal combustion engines devices for changing the timing of gas exchange valves are used 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.
  • the device is integrated in a drive train via which torque is transmitted from the crankshaft to the camshaft.
  • This powertrain can be used, for example, as belt, chain or gear drive to be realized.
  • Such a device usually comprises an output element (rotor) which is arranged rotatably to a drive element (stator), wherein the stator is in driving connection with the crankshaft and the rotor is rotatably connected to the camshaft.
  • the concentric arrangement of stator and rotor is axially limited by two cover plates.
  • the stator, the rotor and the two cover plates define a plurality of pressure chambers, wherein each of the pressure chambers is divided by means of a wing into two counteracting pressure chambers.
  • pressure medium supply or pressure fluid discharge from the pressure chambers the wings are moved within the pressure chambers, whereby a targeted rotation of the rotor to the stator and thus the camshaft is caused to the crankshaft.
  • springs are sometimes used. Often flat spiral torsion springs are used, which are typically attached to the rotor and stator by means of pins or screws.
  • a spring cover is provided for fixing the spring.
  • the spring is arranged between the spring cover and a front cover, wherein a plurality of bolts pass through the spring cover, the front cover, the stator and the rear cover.
  • spring covers are mainly made of sheet steel or plastic. In order to be able to fulfill their task, it is particularly important that they do not become detached from the device when operating loads occur.
  • the invention has for its object to enable a simple and safe installation of a spring cover on a device for changing the timing of gas exchange valves.
  • a device for changing the timing of gas exchange valves of an internal combustion engine comprising a stator and a rotor therein, which is adjustable by a pressure medium in the circumferential direction relative to the stator, wherein the rotor is connectable to a camshaft, further comprising a front cover and a rear cover, between which the stator and the rotor are received, wherein the rear cover is provided with a connectable with a crankshaft drive wheel, and a torsion spring for rotating the rotor relative to the stator, wherein the spring between the rear cover and a spring cover is arranged and wherein the spring cover is fixed to the front side of the drive wheel.
  • the invention is based on the consideration that a simple attachment of the spring cover is ensured on the device via a positive connection of the spring cover with the end face of the drive wheel, with the spring cover facing the end face.
  • the rear cover plate is preferably the cover plate, which faces the camshaft or from which the camshaft extends axially.
  • the drive wheel is in this case, for example, a pulley, a sprocket or a gear and is in a plane with the rear cover.
  • the drive wheel which extends radially further than the other components of the device, provides sufficient surface to which the spring cover is mounted.
  • the advantage here is that thanks to the frontal connection, the size of the spring cover is set to a required minimum for grasping the spring.
  • the attachment of the spring cover is independent of the attachment of the cover plates on the stator and is carried out in a simple manner in a separate step.
  • the spring is arranged in particular directly between the rear cover and the drive wheel and the spring cover.
  • the spring cover is in this case configured approximately pot-shaped, so that it bounds the spring axially on one side and surrounds in the circumferential direction.
  • fasteners are provided exclusively for the attachment of the spring cover and adapted to the appropriate requirements.
  • latching elements are on the spring cover and the drive wheel recordings are provided for the latching elements, with the aid of a snap connection between the spring cover and the drive wheel is made.
  • the snap connection is thereby produced by the latching elements are guided from the inside to the outside, ie from a side facing the camshaft to a side facing away from the camshaft side of the drive wheel through the slots, so that the latching elements engage on the outside.
  • a snap connection offers a number of advantages, for example, the latching elements are in particular formed integrally with the spring cover in the same manufacturing step and the latching elements have a relatively simple geometry, with no further fasteners, such as adhesives, solvents, welding or special equipment are required.
  • the receptacles are provided on the drive wheel, which are preferably designed as elongated holes.
  • the oblong holes in particular follow a circular arc, but may alternatively be straight.
  • Slotted holes are characterized by their particularly simple shape and manufacture. The design of the images according to Art Slots allow for an elongated shape of the snap-in elements so that the loads they absorb are distributed over a larger area.
  • anti-rotation pins are preferably provided on the spring cover, which prevent rotation of the spring cover relative to the drive wheel.
  • the anti-rotation pins are preferably arranged adjacent to the latching elements and extend axially, so that both the latching elements and the anti-rotation pins are inserted into the slots on the drive wheel. By their stop against the edges of the slots they prevent rotation locking pins rotation of the lid in the circumferential direction.
  • the latching elements comprise a radial latching hook for radial engagement with the drive wheel.
  • the latched radial latching hook extends in particular radially outward with respect to the oblong hole, so that the radially outer edge is covered by the radial latching hook. So that the radial latching hook does not break during assembly, it advantageously covers a contour of the receptacle up to a maximum of 1 mm.
  • the size of the radial latching hook and thus the size of the overlapped contour of the slot varies depending on the size of the spring cover, the size of the spring force and the number of latching elements.
  • the latching elements comprise a tangential latching hook for engagement with the drive wheel in the circumferential direction.
  • the spring cover When used, the spring cover is exposed to temperatures in the range of -40 ° C to + 130 ° C. Due to the thermal expansion of the spring cover in the higher temperature range, it may come at the radial latching hooks, which rest against the edge of the slots, to deformations. In the cold state, after the spring cover has shrunk again, there is a risk that the spring cover radially no longer locked. This danger is counteracted by the tangential latching hooks cause a locking of the spring cover in the circumferential direction and thus prevent its release.
  • the radial latching hook is larger than the tangential latching hook, in particular two to five times larger.
  • the radial latching hook is made more massive than the tangential latching hook and carries the main burden. This means that the forces that are introduced by the spring in the spring cover are taken in the first place by the radial latching hook.
  • the tangential latching hook is mainly used for additional protection in cold operation, so that even with a deformation of the radial latching hook of the spring cover does not come off the drive wheel.
  • each radial latching hook is arranged between a tangential latching hook and an anti-rotation pin.
  • the radial latching hook which has the largest volume of all introduced into the slot elements, extends almost completely along one longitudinal side of the elongated hole and engages behind its edge.
  • On one side of the radial latching hook is the tangential latching hook and on the other side of the anti-rotation pin is arranged, which engage in the semi-circular narrow sides of the slot and fulfill their function by their interaction with the contour of the slot.
  • all two anti-rotation pins are advantageously arranged mirror-symmetrically about a radial axis with respect to the radial latching hooks.
  • the latching elements are grouped in particular in pairs and the side of two such latching elements is ever arranged a rotation locking pin, wherein the one anti-rotation pin on the left and the other anti-rotation pin is positioned to the right of the respective latching element. Due to the mirror-symmetrical arrangement of the anti-rotation pins against the latching elements an anti-rotation is ensured both clockwise and counterclockwise.
  • the spring cover is expediently made of plastic.
  • Plastic is a very light material, which is also particularly easy to deform.
  • the latching elements can also be formed integrally with the spring cover.
  • the spring cover is in particular a sheet metal part made of metal.
  • a device 1 for changing the timing of gas exchange valves of an internal combustion engine is shown.
  • the device 1 is provided for mounting on a camshaft not shown in detail.
  • the camshaft extends in the axial direction to the rear, ie perpendicular to the plane of the drawing to the rear, so that in Fig. 1 a front or an outside of the device 1 is shown.
  • the device 1 essentially comprises a stator 3 (see Fig. 3 ), a rotor 5 and a front cover 7 and a rear cover 9.
  • the stator 3, which is the drive element is connected to a crankshaft, not shown in detail and concentrically about the rotor 5, the output element disposed.
  • the rotor 5 is rotatably connected to the camshaft and arranged pivotally with respect to the stator 5.
  • the stator 5 and the rotor are received between the front and the rear cover 7, 9. By means of screws 10, the two cover elements 7, 9 are screwed to the stator 3.
  • pressure chambers are formed, which are axially limited by the cover plates 7, 9. With the help of likewise not shown here blades of the rotor 5, the pressure chambers are divided into two oppositely acting pressure chambers.
  • a pressure means e.g. Oil, directed into the pressure chambers.
  • the front cover 7 is designed as a sealing cover and serves for the axial sealing of the pressure chambers.
  • the rear cover 9 also has a sealing function, circumferentially it is also provided with a drive wheel, here a pulley 11, which is connectable to the crankshaft.
  • the pulley is in the same plane as the rear cover 9 and thus represents a radial extension of the rear cover 9 is.
  • a spring 13 which returns the rotor 5 in a rest or initial position.
  • the spring 13 is positioned between the rear cover 9 and the spring cover 15, which in Fig. 3 and Fig. 4 is shown.
  • the spring cover 15 limits the spring 13 axially to the rear and also surrounds them circumferentially.
  • the spring cover 15 is in the illustrated embodiment made of plastic, but may also be made of metal. The use of plastic makes it easier to achieve desired geometric shapes.
  • the spring cover 15 is positively secured via latching elements 17 on the end face of the pulley 11.
  • the latching elements 17 comprise in the illustrated embodiment each have a radial latching hook 21 and a tangential latching hook 23.
  • the radial latching hook 21 is engaged with a radially outer longitudinal side of the slot 19.
  • the tangential latching hook 23 is disposed laterally of the radial latching hook 21 and has a width, which substantially corresponds to the width of the slot 19.
  • the radial latching hook 21 is formed solid than the tangential latching hooks 23.
  • the radial latching hook 21 is about three times larger than the tangential latching hook 23 and carries the main load. If the spring cover 15 expands during operation at elevated temperatures, it may happen that deforms the radial latching hook 21 and that after cooling, when the spring cover 15 is shrunk again, the radial latching hook 21 no longer locked. In this case, prevents the tangential latching hook 21, which acts in the circumferential direction U, that the spring cover 15 from the pulley 11 dissolves. So that the radial latching hook 21 does not break during assembly, it is designed so that the overlap of the contour of the oblong hole 19 is limited to a maximum of 1 mm.
  • rotation locking pins 25 are formed, which are arranged in the region of the latching elements 17 and are also guided in the axial direction A through the slots 19.
  • Each radial latching hook 21 is positioned between a tangential latching hook 23 and an anti-rotation pin 25.
  • By its abutment against the wall of the slot 19 prevents the anti-rotation pin 25, a rotation of the spring cover 15 relative to the pulley 11.
  • the anti-rotation pin 25 of the tangential latching hook 23 is not against the wall of the slot 19 and the tangential locking hooks 23 covers the slot 19 slightly smaller than the radial latching hooks 21st

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

Claims (9)

  1. Dispositif (1) pour modifier les temps de réglage de soupapes d'échange de gaz d'un moteur à combustion interne, comprenant :
    - un stator (3) et un rotor (5) reçu dans celui-ci, lequel peut être réglé par un moyen de pression dans la direction périphérique (U) par rapport au stator (3), le rotor (5) pouvant être connecté à un arbre à cames,
    - un disque de recouvrement avant (7) et un disque de recouvrement arrière (9) entre lesquels sont reçus le stator (3) et le rotor (5), le disque de recouvrement arrière (9) étant pourvu d'une roue d'entraînement (11) pouvant être connectée à un vilebrequin,
    - un ressort (13) pour la rotation du rotor (5) par rapport au stator (3),
    caractérisé en ce que le ressort (13) est disposé entre le disque de recouvrement arrière (9) et un couvercle de ressort (15), le couvercle de ressort (15) étant fixé du côté frontal à la roue d'entraînement (11), des éléments d'encliquetage (17) étant prévus au niveau du couvercle de ressort (15) et des logements (19) pour les éléments d'encliquetage (17) étant prévus au niveau de la roue d'entraînement (11), des goupilles de fixation en rotation (25) étant prévues au niveau du couvercle de ressort (15) et la goupille de fixation en rotation (25) étant disposée en position adjacente à l'élément d'encliquetage (17).
  2. Dispositif (1) selon la revendication 1,
    caractérisé en ce que les logements (19) sont réalisés sous forme de trous oblongs.
  3. Dispositif (1) selon la revendication 1 ou 2,
    caractérisé en ce que les éléments d'encliquetage (17) comprennent un crochet d'encliquetage radial (21) pour l'engagement radial avec la roue d'entraînement (11).
  4. Dispositif (1) selon la revendication 3,
    caractérisé en ce que le crochet d'encliquetage radial (21) recouvre un contour du logement (19) jusqu'à 1 mm au maximum.
  5. Dispositif (1) selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce que les éléments d'encliquetage (17) comprennent un crochet d'encliquetage tangentiel (23) pour l'engagement avec la roue d'entraînement (11) dans la direction périphérique (U).
  6. Dispositif (1) selon la revendication 3 et la revendication 5,
    caractérisé en ce que le crochet d'encliquetage radial (21) est plus grand que le crochet d'encliquetage tangentiel (23), en particulier est deux à cinq fois plus grand.
  7. Dispositif (1) selon les revendications 1, 3 et 5,
    caractérisé en ce que chaque crochet d'encliquetage radial (21) est disposé entre un crochet d'encliquetage tangentiel (23) et une goupille de fixation en rotation (25).
  8. Dispositif (1) selon la revendication 7,
    caractérisé en ce que les deux goupilles de fixation en rotation (25) sont toutes les deux disposées autour d'un axe radial (R) avec une symétrie spéculaire par rapport aux crochets d'encliquetage radiaux (21).
  9. Dispositif (1) selon l'une quelconque des revendications précédentes,
    caractérisé en ce que le couvercle de ressort (15) est fabriqué en plastique ou en métal.
EP11700264.2A 2010-02-01 2011-01-12 Dispositif pour modifier les temps de réglage de soupapes de renouvellement des gaz d'un moteur à combustion interne Active EP2531702B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010006415A DE102010006415A1 (de) 2010-02-01 2010-02-01 Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
PCT/EP2011/050342 WO2011092055A2 (fr) 2010-02-01 2011-01-12 Dispositif pour modifier les temps de réglage de soupapes de renouvellement des gaz d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2531702A2 EP2531702A2 (fr) 2012-12-12
EP2531702B1 true EP2531702B1 (fr) 2015-03-18

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11700264.2A Active EP2531702B1 (fr) 2010-02-01 2011-01-12 Dispositif pour modifier les temps de réglage de soupapes de renouvellement des gaz d'un moteur à combustion interne

Country Status (6)

Country Link
US (1) US8789501B2 (fr)
EP (1) EP2531702B1 (fr)
CN (1) CN102741509B (fr)
BR (1) BR112012018369A2 (fr)
DE (1) DE102010006415A1 (fr)
WO (1) WO2011092055A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010005602A1 (de) * 2010-01-25 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Nockenwellenversteller
DE102011004588A1 (de) * 2011-02-23 2012-08-23 Schaeffler Technologies Gmbh & Co. Kg Nockenwellensteller
DE102014201608A1 (de) * 2014-01-30 2015-07-30 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
JP6422829B2 (ja) * 2015-06-29 2018-11-14 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置
CN105927308A (zh) * 2016-05-31 2016-09-07 绵阳富临精工机械股份有限公司 一种皮带式凸轮相位器
US10895178B2 (en) * 2017-03-08 2021-01-19 ECO Holding 1 GmbH Actuator for cam phaser and cam phaser
US10612430B2 (en) * 2017-06-20 2020-04-07 ECO Holding 1 GmbH Oil control valve to control a cam phaser with a spool positioned by external actuator

Family Cites Families (14)

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Publication number Priority date Publication date Assignee Title
US5172658A (en) * 1992-02-24 1992-12-22 Eaton Corporation Camshaft phase change device
JP4147435B2 (ja) 1998-01-30 2008-09-10 アイシン精機株式会社 弁開閉時期制御装置
JP2005061261A (ja) * 2003-08-08 2005-03-10 Hitachi Unisia Automotive Ltd 内燃機関の可変動弁装置
DE102005020529A1 (de) * 2005-05-03 2006-11-09 Schaeffler Kg Nockenwellenversteller
DE102006002993A1 (de) * 2006-01-21 2007-08-09 Schaeffler Kg Nockenwellenversteller für eine Brennkraftmaschine
DE102007039282B4 (de) 2007-08-20 2017-06-01 Hilite Germany Gmbh Hydraulisch dichter Nockenwellenversteller
DE102009005114A1 (de) 2008-01-30 2009-08-06 Schaeffler Kg Nockenwellenverstellvorrichtung
DE102008001078A1 (de) * 2008-04-09 2009-10-15 Robert Bosch Gmbh Vorrichtung zum Verändern der Nockenwellenphasenlage
DE102009042215B4 (de) * 2008-10-14 2018-06-07 Schaeffler Technologies AG & Co. KG Nockenwellenversteller für eine konzentrische Nockenwelle
CN201321880Y (zh) * 2008-11-26 2009-10-07 绵阳新晨动力机械有限公司 一种发动机可变凸轮轴相位调节器
ITMI20091719A1 (it) * 2009-10-08 2011-04-09 Industrie De Nora Spa Catodo per processi elettrolitici
DE102009054049B4 (de) * 2009-11-20 2020-08-27 Schaeffler Technologies AG & Co. KG Nockenwellenverstellanordnung
JP5360080B2 (ja) * 2011-01-20 2013-12-04 株式会社デンソー バルブタイミング調整装置
DE102012200099A1 (de) * 2012-01-05 2013-07-11 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Also Published As

Publication number Publication date
CN102741509B (zh) 2015-12-09
CN102741509A (zh) 2012-10-17
EP2531702A2 (fr) 2012-12-12
BR112012018369A2 (pt) 2019-09-24
US20130055975A1 (en) 2013-03-07
WO2011092055A2 (fr) 2011-08-04
DE102010006415A1 (de) 2011-08-04
US8789501B2 (en) 2014-07-29
WO2011092055A3 (fr) 2011-10-13

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