EP2136041A2 - Vanne pour déphaser un arbre à cames - Google Patents

Vanne pour déphaser un arbre à cames Download PDF

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Publication number
EP2136041A2
EP2136041A2 EP09005039A EP09005039A EP2136041A2 EP 2136041 A2 EP2136041 A2 EP 2136041A2 EP 09005039 A EP09005039 A EP 09005039A EP 09005039 A EP09005039 A EP 09005039A EP 2136041 A2 EP2136041 A2 EP 2136041A2
Authority
EP
European Patent Office
Prior art keywords
piston
valve
pressure chamber
camshaft
valve according
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.)
Granted
Application number
EP09005039A
Other languages
German (de)
English (en)
Other versions
EP2136041A3 (fr
EP2136041B1 (fr
Inventor
Andreas Knecht
Dirk Pohl
Patrick Gautier
Markus Todt
Jan Eimert
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
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 Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP2136041A2 publication Critical patent/EP2136041A2/fr
Publication of EP2136041A3 publication Critical patent/EP2136041A3/fr
Application granted granted Critical
Publication of EP2136041B1 publication Critical patent/EP2136041B1/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
    • F01L1/34—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
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow camshafts
    • 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
    • F01L2001/34426—Oil control valves
    • F01L2001/34433—Location oil control valves

Definitions

  • the invention relates according to claim 1, a valve for pivoting a camshaft.
  • the DE 196 37 174 A1 shows a valve for a phaser in which a piston is longitudinally displaceable within a bore having a longitudinal axis. From the inner wall of the bore go from two working ports A, B and a pressure medium connection P. The pressure medium connection P is arranged axially between the two working ports A, B.
  • a valve for a phaser From the DE 198 53 670 B4 is also known a valve for a phaser. From the inner wall of the bore go two working ports A, B and a tank drain T from. The tank outlet T is arranged axially between the two working ports A, B. A front side of the valve arranged pressure medium connection P leads to the bore or the hollow piston from the inside pressure.
  • the object of the invention is to provide an axially very short camshaft adjuster.
  • the pressure medium connection P is immediately followed by the first working connection A.
  • This first working connection A is followed directly or indirectly by the second working connection B.
  • the camshaft adjuster can be designed axially correspondingly narrow in a valve, for example, arranged centrally to the camshaft adjuster valve.
  • the pressure medium connection P is arranged axially after or in front of the two working connections A, B.
  • this pressure medium connection P can be connected outside of the camshaft adjuster to channels in the valve, which can promote the supply pressure from a fluid feed pump to the working ports A and B respectively. Consequently, bores in the camshaft adjuster, which conduct the supply pressure from the fluid feed pump to the pressure medium connection P within the camshaft adjuster, are not necessary.
  • Such holes, in particular by the rotor of the camshaft adjuster increase the processing effort and weaken the rotor. In a particularly advantageous manner, therefore, the hydraulic fluid is passed through the piston of the valve.
  • the pressure medium connection P can be arranged in front of or behind the camshaft adjuster.
  • the arrangement behind the Camshaft adjuster is explained to the illustrated embodiments of this application.
  • a possible arrangement of the pressure medium connection P before the camshaft adjuster is for example in the DE 10 2004 038 252 A1 shown.
  • the hydraulic fluid is passed within the piston via a pressure chamber inlet channel from the pressure medium connection P to the respective working port A and B respectively.
  • This pressure chamber inlet channel is composed of two transverse channels and a central channel arranged between them.
  • the lengths of these channels are in a minimum relationship to each other that the lengths of the transverse channels in the direction of the longitudinal axis of the piston together are at least as long as the length of the intermediate central channel.
  • a camshaft adjuster can be used in a particularly advantageous manner, which designed as die gelzellenversteller is.
  • the invention can also find application in a camshaft adjuster according to the axial piston principle or a chain adjuster.
  • two tank connections are provided for quickly emptying the pressure chambers. These two tank connections can be provided in a further advantageous embodiment at the two ends of the valve.
  • the piston is guided axially in a bore.
  • the bore can be incorporated in a particularly advantageous manner in the socket of a cartridge valve.
  • the bore may also be arranged in a housing.
  • the bore is incorporated directly into a central screw, which screws the rotor of the camshaft adjuster with the camshaft.
  • Fig. 1 shows a detail of an internal combustion engine in the range of a camshaft adjuster 1.
  • This camshaft adjuster 1 is provided with a centrally disposed valve 2, which is designed as a 4/3-way proportional valve.
  • the valve 2 is designed as a so-called cartridge valve and comprises a hydraulic part 3 and an electromagnetic actuator 4.
  • the electromagnetic actuator 4 is arranged in alignment with a piston 5 of the hydraulic part 3.
  • An abutment body 6 of a plunger 7 of the actuator 4 abuts against the end face 8 of the piston 5.
  • a housing 9 and a pole core 10 of the electromagnetic actuator 4 are axially fixedly connected via a housing connection not shown in detail with a bush 11 of the hydraulic part 3, in the central bore 12 of the piston 5 is guided axially displaceable. This axial displacement is due to energization of the electromagnetic actuator 4 against the spring force, a helical compression spring 31st
  • valve 2 Function of the valve 2 is the hydraulic pressure on several pressure chambers 13a, 13b of the also in Fig. 5 distributed camshaft adjuster 1, so that a with a rotor 15 of the camshaft adjuster 1 axially and rotationally fixed camshaft 14 is pivoted in the one pivot direction or the opposite other pivoting direction.
  • two pressure chambers 13a, 13b are associated with opposite directions of pivoting.
  • the one of the pivoting direction associated pressure chambers 13a are connected via a in Fig. 2 closer apparent first working port A in the socket 11 is acted upon by a coming from a pressure medium port P pressure.
  • the pressure chambers 13b associated with the opposite direction of rotation are acted upon via a second working port B with the pressure coming from the pressure medium connection P.
  • the valve 2 further has two bypass ports A1 and B1.
  • the bushing 11 has three annular grooves 18, 19, 20, which are separated from each other by means of two annular webs 21, 22.
  • the front - in the drawing plane right - annular groove 18 and the middle annular groove 19 correspond to recesses 23 and 25 in the camshaft 14 and recesses 24 and 26 in the rotor 15. These recesses 23, 24, 25, 26 lead to the pressure chambers 13a, 13b.
  • the front annular groove 18 via the front recesses 25 of the camshaft 14 and the recesses 26 of the rotor 15 leads to the associated one direction of rotation pressure chambers 13b.
  • the middle annular groove 19 leads via the rear recesses 23 of the camshaft 14 and the recesses 24 of the rotor 15 in the pressure chambers 13 a associated with the other direction of rotation.
  • the rear annular groove 20 has a bore 27 which is connected to an annular channel 68, which is in communication with a fluid feed pump 30.
  • an end-side annular web 28, 29 is provided at the ends of the bush 11, which prevents fluid leakage from the rear annular channel 20 and the front annular channel 18.
  • radial bores in the groove bottom of the annular grooves are distributed circumferentially in defined angular positions.
  • the front annular groove 18 from front to rear axially successive bores for the working port B and the bypass port B1.
  • the middle annular groove 19 has From the front to the rear axially successive holes for the bypass port A1 and the working port A on.
  • the left annular groove 20 has from front to rear axially successive holes for the pressure medium connection P.
  • Fig. 3 and Fig. 4 show a valve 102 with a simplified piston 105, wherein with respect to the valve 2 according to Fig. 1 and Fig. 2 No bypass connections A1 and B1 are provided. Otherwise, the piston 105 is constructed equal to the piston 5.
  • the opposite Fig. 1 and Fig. 2 Substantially modified components have increased by 100 reference numerals. Substantially identical components are also provided with the same reference numerals.
  • Fig. 3 shows the piston 105 in a section analog Fig. 1
  • Fig. 4 shows the piston 105, however, 90 ° rotated about its longitudinal axis 34.
  • the piston 105 is in both Fig. 3 as well as in Fig. 4 shown in the foremost position. In this position, the piston 105 is pressed by a helical compression spring 31 when the electromagnetic actuator 4 is energized only slightly or not at all. In this case, a pressure chamber inlet channel 32 extends from the pressure medium connection P to the second working connection B. The pressure chambers 13b assigned to the working connection B are thus filled. At the same time runs to empty the other pressure chambers 13 a, the hydraulic fluid from the first working port A via an in Fig. 4 apparent pressure chamber outlet channel 33 to two tank drains T 1 , T 2 .
  • the shape of the piston 105 makes it possible for the pressure chamber outlet channel 33 to be separated from the pressure chamber inlet channel 32, although these two are guided past one another. That is to say, the pressure chamber outlet channel 33 and the pressure chamber inlet channel 32 run partially in the same axial regions of the valve 102.
  • the piston 105 has a substantially tubular basic shape with a tube wall 80.
  • a slot 35 is provided along the longitudinal axis 34 of the piston 105.
  • This slot 35 has a circumferentially closed wall 36, which separates the slot 35 against two in the tube on both sides of the wall 36 forming part-channels 65a, 65b.
  • said end face 8 is arranged at the front end of the slot 35.
  • an end face 37 is arranged, which supports the helical compression spring 31 elastically against a compression sleeve, which is pressed into the socket 11 to measure.
  • the pressure chamber outlet channel 33 extends to the tank drains T 1 , T 2 through the two partial channels 65a, 65b.
  • the pressure chamber inlet channel 32 extends through the slot 35.
  • the helical compression spring need not be supported on the wall 36 of the piston 105, but in an alternative embodiment also on an in Fig. 4 paragraph 40.
  • the piston 5 and 105 is produced by metal powder injection molding.
  • the tube shape of the piston is exemplary.
  • the piston has a complex integral geometry.
  • One such manufacturing process is injection molding.
  • the metal injection molding process metal injection molding
  • Injection molding processes also include such processes as injection-compression molding.
  • the separation of the pressure chamber discharge channel from the pressure chamber inlet channel takes place with a centrally extending slot. Due to the symmetry, the slot arranged centrally has the advantage that no torques act on the hydraulically actuated piston.
  • Fig. 6 shows in a further embodiment, a central valve 202, which is incorporated directly into a central screw 211, which screws the rotor 215 of the camshaft adjuster 201 with the camshaft 214.
  • a central screw 211 which screws the rotor 215 of the camshaft adjuster 201 with the camshaft 214.
  • an internal thread is cut in the camshaft 214, in which the external thread of the central screw 211 is screwed.
  • a lock 299 can be seen, by means of which the rotor 215 against a stator 298 rotatably locked. This lock 299 can be unlocked by a pressure in the two pressure chambers of the camshaft adjuster 201.
  • the lock is in communication with the pressure medium connection, so that the lock is unlocked immediately depending on the working pressure, the locking analog Fig. 6 done by means of spring force.
  • the camshaft adjuster is preferably designed as die gelzellenversteller.
  • an axial piston adjuster which converts the axial movement into a pivoting movement of the camshaft via helical gearing.
  • Such Axialkolbenversteller find especially in sporty engines with very strong valve springs of the gas exchange valves application, since there strong moment of change of the camshaft must be overcome as a result of the high valve spring forces, which are not forwarded to the axial piston by the self-locking effect of the helical teeth in Axialkolbenversteller.
  • the camshaft may for example be a built camshaft.
  • compression sleeve can also be provided a screwed sleeve, or it may be provided integrally with the socket manufactured bottom.
  • the piston can also be displaced by means of a further hydraulic auxiliary piston.
  • a further hydraulic auxiliary piston depending on the ratio, for example, a force amplification or a very fine positioning of the piston can be achieved.
  • a tank drain on an end face of the piston or an end face of the socket suffice.
  • a tank drain on an end face of the piston or an end face of the socket suffice.
  • a massive design of the piston on one end face of the support surface for the helical compression spring can be increased and voltages can be kept low in the region of this support surface.
  • the tank drains do not have to be arranged on the front side. So it is also possible to run the tank drains as radial holes in the piston and / or in the socket.
  • the outer diameter of the bush or the piston can be rotated in a Spanabhub before the three annular grooves are turned off.
  • the Socket and / or the piston also have stepped outer diameter, wherein the rearmost outer diameter is smallest and the front outer diameter is the largest.
  • This is particularly advantageous for valves with sealing rings - in particular O-rings.
  • These sealing rings can be used in annular grooves in the outer diameter.
  • the sealing rings can be used in êtringnuten the rotor.
  • the stepped design of the outer diameter prevents damage to the seals.
  • Such sealing rings are particularly advantageous for valves for particularly high hydraulic pressures or high demands on the leak-tightness.
  • the use of O-rings is also advantageous when using different materials for the valve components with different thermal expansion coefficients.
  • the piston can be made of metal or plastic.
  • the plastic is produced by injection molding. When using a plastic and a fiber reinforced plastic is advantageous, as this already in the unpublished DE 10 2007 026 831 is shown.

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)
EP09005039A 2008-06-19 2009-04-06 Vanne pour déphaser un arbre à cames Not-in-force EP2136041B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008028846 2008-06-19

Publications (3)

Publication Number Publication Date
EP2136041A2 true EP2136041A2 (fr) 2009-12-23
EP2136041A3 EP2136041A3 (fr) 2010-07-14
EP2136041B1 EP2136041B1 (fr) 2011-06-08

Family

ID=41082411

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09005039A Not-in-force EP2136041B1 (fr) 2008-06-19 2009-04-06 Vanne pour déphaser un arbre à cames

Country Status (2)

Country Link
EP (1) EP2136041B1 (fr)
AT (1) ATE512285T1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2386731A1 (fr) * 2010-05-03 2011-11-16 Hydraulik-Ring GmbH Soupape hydraulique
DE102010060180A1 (de) * 2010-10-26 2012-04-26 Hydraulik-Ring Gmbh Zentralventil
DE102010060181A1 (de) * 2010-10-26 2012-04-26 Hydraulik-Ring Gmbh Zentralventil
WO2012055597A1 (fr) * 2010-10-25 2012-05-03 Schaeffler Technologies AG & Co. KG Soupape de commande pour un dispositif de réglage d'arbre à cames
US9729024B2 (en) 2014-12-12 2017-08-08 Denso Corporation Solenoid actuator

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19637174A1 (de) 1995-09-13 1997-03-27 Aisin Seiki Schaltventil
DE102004038252A1 (de) 2004-05-14 2005-12-15 Ina-Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005013085B3 (de) 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
DE102005041393A1 (de) 2005-09-01 2007-03-08 Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE19853670B4 (de) 1998-11-20 2007-07-26 Hydraulik-Ring Gmbh Einrichtung zur Nockenwellenverstellung
DE102006012775B4 (de) 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006012733B4 (de) 2006-03-17 2008-03-27 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102007026831B3 (de) 2007-06-06 2008-10-02 Hydraulik-Ring Gmbh Elektrohydraulisches Ventil

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB0303571D0 (en) * 2003-02-17 2003-03-19 Delphi Tech Inc Oil flow control valve for a cam phaser

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19637174A1 (de) 1995-09-13 1997-03-27 Aisin Seiki Schaltventil
DE19853670B4 (de) 1998-11-20 2007-07-26 Hydraulik-Ring Gmbh Einrichtung zur Nockenwellenverstellung
DE102004038252A1 (de) 2004-05-14 2005-12-15 Ina-Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005013085B3 (de) 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
DE102005041393A1 (de) 2005-09-01 2007-03-08 Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102006012775B4 (de) 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006012733B4 (de) 2006-03-17 2008-03-27 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102007026831B3 (de) 2007-06-06 2008-10-02 Hydraulik-Ring Gmbh Elektrohydraulisches Ventil

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2386731A1 (fr) * 2010-05-03 2011-11-16 Hydraulik-Ring GmbH Soupape hydraulique
WO2012055597A1 (fr) * 2010-10-25 2012-05-03 Schaeffler Technologies AG & Co. KG Soupape de commande pour un dispositif de réglage d'arbre à cames
CN103189605A (zh) * 2010-10-25 2013-07-03 谢夫勒科技股份两合公司 用于凸轮轴调节器的控制阀
CN103189605B (zh) * 2010-10-25 2015-08-05 谢夫勒科技股份两合公司 用于凸轮轴调节器的控制阀
DE102010060180A1 (de) * 2010-10-26 2012-04-26 Hydraulik-Ring Gmbh Zentralventil
DE102010060181A1 (de) * 2010-10-26 2012-04-26 Hydraulik-Ring Gmbh Zentralventil
DE102010060180B4 (de) * 2010-10-26 2017-06-29 Hilite Germany Gmbh Zentralventil
US9729024B2 (en) 2014-12-12 2017-08-08 Denso Corporation Solenoid actuator

Also Published As

Publication number Publication date
EP2136041A3 (fr) 2010-07-14
EP2136041B1 (fr) 2011-06-08
ATE512285T1 (de) 2011-06-15

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