EP2470757B1 - Vanne de commande - Google Patents

Vanne de commande Download PDF

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Publication number
EP2470757B1
EP2470757B1 EP10742794.0A EP10742794A EP2470757B1 EP 2470757 B1 EP2470757 B1 EP 2470757B1 EP 10742794 A EP10742794 A EP 10742794A EP 2470757 B1 EP2470757 B1 EP 2470757B1
Authority
EP
European Patent Office
Prior art keywords
valve housing
securing ring
valve
control
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.)
Not-in-force
Application number
EP10742794.0A
Other languages
German (de)
English (en)
Other versions
EP2470757A1 (fr
Inventor
Ali Bayrakdar
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 EP2470757A1 publication Critical patent/EP2470757A1/fr
Application granted granted Critical
Publication of EP2470757B1 publication Critical patent/EP2470757B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/3444—Oil filters
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a control valve for a device for variably setting the timing of gas exchange valves of an internal combustion engine with a substantially hollow cylindrical valve housing a control piston and a locking ring, wherein the valve housing is arranged in a receptacle within the device, wherein the retaining ring, the valve housing in the radial direction surmounted and wherein the control piston is slidably disposed within the valve housing.
  • a device and a control valve are for example from the DE 102 11 468 A1 known.
  • the device comprises an output element, which is arranged rotatably to a drive element and rotatably connected to a camshaft.
  • the drive element is in drive connection with a crankshaft.
  • a plurality of oppositely acting pressure chambers are provided by means of which the phase position of the output element relative to the drive element can be selectively adjusted within a defined angular range.
  • a targeted rotation of the camshaft can be effected relative to the crankshaft.
  • the device is designed in vane-type. But are also known other types, such as Axialkolbenversteller from the DE 42 18 082 A1 ,
  • the camshaft is supported by a plurality of camshaft bearing in a cylinder head of the internal combustion engine. Via one of the camshaft bearing, a pressure medium channel formed in the camshaft pressure medium is supplied, which can be passed via a control valve which is arranged in a receptacle of the camshaft in the pressure chambers.
  • the control valve consists of a valve housing and an axially slidably received in the valve housing control piston.
  • the control piston can be positioned by means of an electromagnetic actuator against the force of a spring element in the axial direction relative to the valve housing and thus the pressure medium flows are controlled.
  • the present invention has for its object to provide a control valve, the assembly cost to be reduced.
  • the object is achieved in that on an inner circumferential surface of the receptacle an annular groove is formed, into which the retaining ring can engage, wherein the retaining ring rests against an axial side surface of the valve housing and wherein at least a positive locking element is formed on the valve housing, by means of which the retaining ring is attached to the valve housing.
  • the positive-locking element on the axial side surface of the valve housing, against which the retaining ring is formed can be provided.
  • the circlip is used to attach the control valve in the receptacle, which may be formed for example within the camshaft or the inner rotor.
  • the control valve is thus positioned radially inside the device.
  • the locking ring is designed as an elastically deformable component, which can be elastically compressed and enlarged in the radial direction, so that its diameter can be reduced and increased under the action of force from the idle state. If the force fails, the retaining ring returns to its original state.
  • the diameter of the securing ring is compressed when entering the receptacle by the wall in the radial direction. If the circlip arrives in the region of the annular groove of the receptacle, it engages in the annular groove. At the same time, this is in the axial direction of the valve housing, for example on an axial side surface of the valve housing, so that the axial position of the valve housing and thus of the control valve is fixed in the receptacle.
  • control valve including retaining ring can be delivered as an assembly to the assembly line.
  • assembly of the control valve in the receptacle only one assembly must be mounted and not two separate components. In addition, it is ensured that the circlip is installed during assembly.
  • the mounting of the locking ring on the valve housing is effected in that the securing ring is first bent elastically in the radial direction enlarging the diameter and inserted into the hook. Subsequently, the force, which has led to the increase in the diameter, terminated and the retaining ring returns to its original state, so that it is captive absorbed in the hook.
  • the retaining ring has a radially inwardly extending portion which serves as an axial stop for the control piston.
  • FIG. 1 an internal combustion engine 1 is sketched, wherein a seated on a crankshaft 2 piston 3 is indicated in a cylinder 4.
  • the crankshaft 2 is in the illustrated embodiment via a respective traction mechanism 5 with an intake camshaft 6 and exhaust camshaft 7 in combination, wherein a first and a second device 11 for variably setting the timing of gas exchange valves 9, 10 of an internal combustion engine 1 for a relative rotation between the crankshaft 2 and the camshafts 6, 7 can provide.
  • Cams 8 of the camshafts 6, 7 actuate one or more inlet gas exchange valves 9 or one or more Auslassgas scaffoldventile 10.
  • it may be provided only one of the camshafts 6, 7 with a device 11, or provide only a camshaft 6, 7, which with a Device 11 is provided.
  • FIGS. 2 and 3 show a device 11 in longitudinal or in cross section, wherein in FIG. 2 in addition, a camshaft 6, 7 and a control valve 12 according to the invention are shown.
  • the device 11 comprises a drive element 14 and an output element 16.
  • the drive element 14 consists of a housing 15 and two side covers 17, 18, which are arranged on the axial side surfaces of the housing 15 and secured by screws thereto.
  • the output element 16 is designed in the form of an impeller and has a substantially cylindrical hub member 19, extend from the outer cylindrical surface in the illustrated embodiment, five wings 20 in the radial direction outwardly.
  • projections 22 extend radially inwardly.
  • the projections 22 and the wings 20 are integrally formed with the peripheral wall 21 and the hub member 19, respectively.
  • the wings 20 and / or the projections 22 are formed as separately manufactured components, which are subsequently mounted on the corresponding component.
  • the drive element 14 is mounted by means of radially inner circumferential walls of the projections 22 relative to the output member 16 rotatably mounted thereon.
  • a sprocket 23 is formed, via which by means of a chain drive, not shown, torque can be transmitted from the crankshaft 2 to the drive member 14.
  • the output member 16 has a central opening 13 which is penetrated by the camshaft 6,7. In this case, the output element 16 by means of a press fit rotationally fixed to the camshaft 6, 7 attached.
  • a pressure space 28 is formed between each two circumferentially adjacent projections 22.
  • Each of the pressure chambers 28 is circumferentially bounded by opposing, substantially radially extending boundary walls of adjacent projections 22, in the axial direction of the side covers 17, 18, radially inwardly of the hub member 19 and radially outwardly of the peripheral wall 21.
  • a wing 20 In each of the pressure chambers 28 projects a wing 20, wherein the wings 20 are formed such that they rest against both the side covers 17, 18, and on the peripheral wall 21.
  • Each wing 20 thus divides the respective pressure chamber 28 into two counteracting pressure chambers 29, 30th
  • phase position of the drive element 14 to the output element 16 and thus the phase angle of the camshaft 6, 7 to the crankshaft 2 can be varied.
  • phase position can be kept constant.
  • FIG. 4 shows the control valve 12 within the camshaft 6, 7 in an enlarged view.
  • the control valve 12 has a substantially hollow cylindrical valve housing 34, a cylindrical sleeve 35 and a substantially hollow cylindrical control piston 36.
  • a radial inlet port P On the valve housing 34, a radial inlet port P, two radial working ports A, B and an axial discharge port T are formed.
  • the drain port T is formed as an axial opening on the valve housing 34.
  • the working ports A, B are formed as radial openings on the lateral surface of the valve housing 34, wherein each of the working ports A, B communicates via formed in the driven element 16 pressure fluid channels 46 with a group of pressure chambers 29, 30.
  • the inlet port P is also formed as a radial opening on the lateral surface of the valve housing 34, wherein this is arranged in the circumferential direction offset from the working ports A, B and formed as a slot ( FIG. 5 ).
  • the inlet port P extends in the axial direction up to a check valve receptacle 32, which communicates via an axial opening, not shown, with the interior of the camshaft 6, 7.
  • a spring plate 33 is arranged, which is biased against the axial opening, not shown, so that a check valve is realized, which allows a pressure fluid flow from the camshaft 6, 7 to the inlet port P and an opposite Pressure medium flow blocks.
  • a cup-shaped filter element 47 is attached to the valve housing 34.
  • the valve housing 34 is disposed within the camshaft 6, 7, wherein its axial position is determined by a formed on the inner circumferential surface of the camshaft 6, 7 and the outer circumferential surface of the valve housing 34 shoulder and a locking ring 42.
  • the locking ring 42 projects beyond the valve housing 34 in the radial direction, is arranged in an annular groove 44, which is formed on the inner lateral surface of the camshaft 6, 7, and bears against an axial side surface 43 of the valve housing 34.
  • the sleeve 35 is arranged, whose outer diameter is adapted to the inner diameter of the valve housing 34.
  • the sleeve 35 has a plurality of openings 37, each of the openings 37 communicating with one of the working ports A, B or the inlet port P.
  • control piston 36 Within the sleeve 35, the control piston 36 is received axially displaceable.
  • the control piston 36 has two control sections 38 whose outer diameter is adapted to the inner diameter of the sleeve 35. Between the control sections 38, an annular groove 39 which surrounds the control piston 36 is provided.
  • the control piston 36 can be positioned against the force of a spring element 40 in the axial direction relative to the valve housing 34 by means of an electromagnetic actuating unit, not shown, which acts on the end of the control piston 36 facing away from the camshaft 6, 7.
  • the spring element 40 is arranged in a formed on the valve housing 34 spring receptacle 41 and is based on the one hand on the spring seat 41 and on the other hand to control piston 36 from. In this case, the path of the control piston 36 in the axial direction on the one hand by the spring seat 41 and on the other hand by radially inwardly extending portions 45 of the locking ring 42 is limited ( Figure 4-6 ).
  • one of the working ports A, B is connected to the inlet port P, at the same time the other working port A, B directly or via the interior of the control piston 36 is connected to the drain port T.
  • control edges are formed on the control sections 38 of the control piston 36 and the openings 37 of the sleeve 35, by means of which the pressure medium flows are controlled.
  • pressure medium is supplied to the interior of the camshaft 6, 7 via camshaft openings 48 by a pressure medium pump, not shown.
  • the pressure medium passes through the filter element 47, via the axial opening, not shown, in the valve housing 34 and the spring plate 33 to the inlet port P and from there into an annular space bounded by the formed on the control piston 36 groove 39 and the sleeve 35.
  • each of the interlocking elements 49 On the axial side surface 43 on which the locking ring 42 abuts two circumferentially spaced hook-shaped form-locking elements 49 are formed, which are designed to be open radially outward.
  • Each of the interlocking elements 49 starting from the side surface 43, initially extends in the axial direction and has an adjoining radial section 50.
  • the interlocking elements 49 engage behind the locking ring 42 in the axial direction, so that it is captively received between the axial side surface 43 and the radial portions 50.
  • the slotted securing ring 42 is elastically bent by means of a force directed in the circumferential direction and positioned on the side surface 43. Subsequently, the force is terminated, so that the retaining ring 42 assumes its original shape of smaller diameter again and thus attached to the valve housing 34. Due to the radially inwardly extending portions 45, both the sleeve 35 and the control piston 36 and thus the spring element 40 are captively received in the valve housing 34, so that the entire control valve 12 can be delivered as an assembly to the assembly line without a Loss of components is to be feared.
  • FIG. 7 shows a further embodiment of a control valve 12 according to the invention analogous to the representation in FIG. 4 ,
  • the attachment of the locking ring 42 is realized on the valve housing 34 by means of a clip connection.
  • the securing ring 42 has a through opening 51, which is penetrated by an axially extending, barbed positive-locking element 49, which is formed on the valve housing 34.
  • valve housing 34 may be formed in one or more parts.
  • valve housings 34 which consist of several axially extending ones Subsections are formed with circumferentially opposite open ends, a positive locking element 49 is preferably formed on each of the sections, so that the sections are also secured by the locking ring 42 relative to each other.
  • the valve housing 34 may be made for example of steel, aluminum or plastic.
  • Inlet gas exchange valve 10 Auslassgas crispventil 11 contraption 12
  • Form-fitting element 50 radial section 51 Through opening A first work connection B second work connection P inflow connection T drain connection

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

Claims (4)

  1. Soupape de commande (12) pour un dispositif (11) pour l'ajustement variable des temps de commande de soupapes d'échange de gaz (9, 10) d'un moteur à combustion interne (1), comprenant :
    - un boîtier de soupape (34) réalisé essentiellement sous forme cylindrique creuse, un piston de commande (36) et une bague de fixation (42),
    - le boîtier de soupape (34) étant disposé dans un logement (31) à l'intérieur du dispositif (11),
    - la bague de fixation (42) dépassant du boîtier de soupape (34) dans la direction radiale et
    - le piston de commande (36) étant disposé de manière déplaçable à l'intérieur du boîtier de soupape (34),
    caractérisée en ce qu'une rainure annulaire (44) est réalisée sur une surface d'enveloppe interne du logement (31), dans laquelle la bague de fixation (42) peut s'engager,
    - la bague de fixation (42) s'appliquant contre une face latérale axiale (43) du boîtier de soupape (34) et
    - au moins un élément d'engagement par correspondance de forme (49) étant réalisé sur le boîtier de soupape (34), au moyen duquel la bague de fixation (42) est fixée au boîtier de soupape (34).
  2. Soupape de commande (12) selon la revendication 1, caractérisée en ce que l'élément d'engagement par correspondance de forme (49) est réalisé sur la surface latérale axiale (43) du boîtier de soupape (34) contre laquelle s'applique la bague de fixation (42).
  3. Soupape de commande (12) selon la revendication 1, caractérisée en ce que dans la région de la surface latérale (43) du boîtier de soupape (34), contre laquelle s'applique la bague de fixation (42), sont réalisés deux éléments d'engagement par correspondance de forme (49) en forme de crochets, espacés dans la direction périphérique, qui sont réalisés de manière ouverte radialement vers l'extérieur et qui viennent en prise par l'arrière dans la direction axiale avec la bague de fixation (42), de telle sorte que la bague de fixation (42) s'applique à la fois contre la surface latérale axiale (43) du boîtier de soupape (34) et contre des portions s'étendant radialement (50) des éléments d'engagement par correspondance de forme (49) en forme de crochets.
  4. Soupape de commande (12) selon la revendication 1, caractérisée en ce que la bague de fixation (42) présente une portion (45) s'étendant radialement vers l'intérieur, qui sert de butée axiale pour le piston de commande (36).
EP10742794.0A 2009-08-29 2010-07-29 Vanne de commande Not-in-force EP2470757B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009039385A DE102009039385A1 (de) 2009-08-29 2009-08-29 Steuerventil
PCT/EP2010/061009 WO2011023488A1 (fr) 2009-08-29 2010-07-29 Soupape de commande

Publications (2)

Publication Number Publication Date
EP2470757A1 EP2470757A1 (fr) 2012-07-04
EP2470757B1 true EP2470757B1 (fr) 2013-07-24

Family

ID=42931803

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10742794.0A Not-in-force EP2470757B1 (fr) 2009-08-29 2010-07-29 Vanne de commande

Country Status (6)

Country Link
US (1) US8567360B2 (fr)
EP (1) EP2470757B1 (fr)
CN (1) CN102482957B (fr)
BR (1) BR112012004446A8 (fr)
DE (1) DE102009039385A1 (fr)
WO (1) WO2011023488A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011003556B4 (de) 2011-02-03 2022-03-24 Schaeffler Technologies AG & Co. KG Vorrichtung zur Veränderung der relativen Winkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
WO2013174563A1 (fr) * 2012-05-25 2013-11-28 Schaeffler Technologies AG & Co. KG Soupape de commande d'un déphaseur d'arbre à cames
DE102012208809B4 (de) * 2012-05-25 2020-11-26 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012208812B4 (de) * 2012-05-25 2018-02-01 Schaeffler Technologies AG & Co. KG Steuerventil eines Nockenwellenverstellers
DE102012220626A1 (de) * 2012-11-13 2014-05-15 Schaeffler Technologies Gmbh & Co. Kg Steuerventil für eine hydraulische Vorrichtung mit Verriegelung
DE102012220830B4 (de) * 2012-11-15 2018-01-18 Schaeffler Technologies AG & Co. KG Steuerventil für eine hydraulische Vorrichtung mit einer austauschbaren Hydraulikeinheit
DE102013200399B4 (de) 2013-01-14 2024-08-01 Schaeffler Technologies AG & Co. KG Zentralschraube mit einem Ventil für einen Nockenwellenversteller
DE102014201562A1 (de) * 2014-01-29 2015-07-30 Schaeffler Technologies AG & Co. KG Steuerventil für einen Nockenwellenversteller
GB201512687D0 (en) * 2015-07-20 2015-08-26 Delphi Automotive Systems Lux Valve

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5207462A (en) * 1990-11-02 1993-05-04 Proprietary Technology, Inc. Apparatus and method for a push assemble retaining ring
DE4218082C5 (de) 1992-06-01 2006-06-29 Schaeffler Kg Vorrichtung zur kontinuierlichen Winkelverstellung zwischen zwei in Antriebsverbindung stehenden Wellen
DE10211468A1 (de) 2002-03-15 2003-09-25 Daimler Chrysler Ag Nockenwellenversteller für eine Brennkraftmaschine
DE102005052481A1 (de) * 2005-11-03 2007-05-24 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102006002993A1 (de) * 2006-01-21 2007-08-09 Schaeffler Kg Nockenwellenversteller für eine Brennkraftmaschine
DE102008006179A1 (de) * 2008-01-26 2009-07-30 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen in Brennkraftmaschinen

Also Published As

Publication number Publication date
US20120152189A1 (en) 2012-06-21
CN102482957B (zh) 2014-10-29
CN102482957A (zh) 2012-05-30
EP2470757A1 (fr) 2012-07-04
BR112012004446A8 (pt) 2017-12-19
WO2011023488A1 (fr) 2011-03-03
US8567360B2 (en) 2013-10-29
DE102009039385A1 (de) 2011-03-03
BR112012004446A2 (pt) 2016-03-22

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