EP2171258B1 - Soupape de commande pour une soupape d'injection de carburant - Google Patents

Soupape de commande pour une soupape d'injection de carburant Download PDF

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Publication number
EP2171258B1
EP2171258B1 EP08760855.0A EP08760855A EP2171258B1 EP 2171258 B1 EP2171258 B1 EP 2171258B1 EP 08760855 A EP08760855 A EP 08760855A EP 2171258 B1 EP2171258 B1 EP 2171258B1
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EP
European Patent Office
Prior art keywords
valve
control
control sleeve
pressure
valve body
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
EP08760855.0A
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German (de)
English (en)
Other versions
EP2171258A1 (fr
Inventor
Nadja Eisenmenger
Hans-Christoph Magel
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2171258A1 publication Critical patent/EP2171258A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to a control valve for a fuel injector, which can be used for the injection of fuel under high pressure in the combustion chamber of an internal combustion engine.
  • a fuel injector known, as it can be used for injection of fuel into the combustion chamber, preferably of high-speed, self-igniting internal combustion engines.
  • the fuel injector is supplied with fuel under high pressure by means of a high-pressure pump and has a valve needle which alternately releases or closes one or more injection openings by their longitudinal movement.
  • the fuel can be injected into the combustion chamber at a precisely determined time of the power stroke of the internal combustion engine, which takes place at very high pressure in order to achieve good atomization of the fuel.
  • the movement of the valve needle is achieved on the one hand by the hydraulic pressure of the fuel, which acts on the valve needle in the opening direction.
  • the opposite is a closing force, which is generated by the fuel pressure in a control room.
  • a closing force which is generated by the fuel pressure in a control room.
  • control valve The fuel pressure in the control chamber is adjusted via a control valve. That from the DE 10 2006 021 741 A1
  • known control valve has a control sleeve, which is connected to a magnet armature and by the Bestromen or Non-energizing the electromagnet is moved in its longitudinal direction.
  • the control sleeve is seated on a valve seat which limits a pressure chamber connected to the control chamber radially outward, wherein when the control sleeve lifts from the valve seat, the pressure chamber and thus the control chamber is connected to a leakage oil chamber, while sitting on the control sleeve on the Valve seat of the pressure chamber and thus the control room is separated from the leakage oil space.
  • the control sleeve has on its end facing the valve seat on a sealing surface, which is formed substantially annularly circular. It can also be provided that a slightly conical shape of the sealing surface is provided in order to obtain a line contact. This increases the sealing effect, so that even with a relatively small spring force with which the valve sleeve is pressed onto the valve seat, a good seal is achieved.
  • the injection pressure, with which the fuel is introduced by the high-pressure pump in the injector is in modern high-pressure injection systems, such as those used for self-igniting, high-speed internal combustion engines, up to 1800 bar and will continue to rise in the future.
  • This high fuel pressure is also in the control chamber and thus in the pressure chamber and there leads to the control sleeve is radially expanded. Since the pressure drops when the control valve is open and rises again when the control valve is closed, pressure fluctuations in the pressure chamber and thus relative movement of the sealing surface to the valve seat occur. This leads to wear at this point, especially if a line-shaped bearing surface is provided on the sealing surface on the valve seat, so that the sealing surface, which rests effectively on the valve seat, is getting larger.
  • the control valve according to the invention for a fuel injector has the advantage that the wear in the region of the valve seat compared to the known valve is significantly reduced, so that a reliable function over the entire life of the control valve is ensured.
  • a recess is formed on the side of the valve body, on which the valve seat is located, which is in hydraulic communication with the pressure chamber. Varying pressure in the pressure chamber, so on the one hand, the control sleeve, but also the recess in the valve body is radially expanded, wherein the recess is such that the relative movement of the valve seat and the sealing surface is at least approximately equal, which significantly reduces wear in this area ,
  • the control sleeve is guided on a guide pin, which protrudes from the valve body facing away from the side of the guide sleeve into the guide sleeve.
  • the guide sleeve is guided independently of the valve body, so that an accurate alignment of the valve sleeve on the valve seat is possible.
  • the guide pin has an extension which projects into the recess of the valve body. As a result, the volume of the pressure chamber can be reduced, which increases the dynamics of the control valve, since the pressure changes in the pressure chamber and thus in the control room can be made faster. In this case, the function of the recess in the valve body is maintained.
  • valve seat is conical, thus has the shape of a truncated cone, wherein the valve seat is formed around the recess around.
  • the inner diameter of the guide sleeve and the diameter of the recess have the same diameter on.
  • control valve in a fuel injector for internal combustion engines, in which the fuel pressure is adjusted in a control chamber by the control valve. Due to the changing pressure in the control chamber, a valve needle can be moved in its longitudinal direction, which controls the fuel injection of the fuel injector into a combustion chamber of the internal combustion engine.
  • FIG. 1 is a longitudinal section through a fuel injector shown, in which a control valve according to the invention is used.
  • the fuel injector has a housing 1, in which a control valve 3 is formed, which controls the movement of a valve needle 10.
  • the valve needle 10 is in this case piston-shaped and controls with its end remote from the control valve 3 an injection port through which fuel into a combustion chamber of an internal combustion engine can be injected.
  • the valve needle 10 is guided in this case in a valve body 5, which is arranged in the housing 1 and which has a bore 12 in which the valve needle 10 is guided. Through the bore 12 of the valve body 5 and the valve needle 10, a control chamber 7 is limited, the fuel pressure acts on the control valve side facing the valve needle 10 and thus generates a closing force on the valve needle 10.
  • the control chamber 7 is always supplied with fuel under high pressure. This is done via an annular space 14 which surrounds the valve body 5 and which is connected via a bore, not shown in the drawing, to a fuel port, via which fuel compressed by a high-pressure pump is supplied.
  • the annular space 14 is connected through a throttle bore 15 with the control chamber 7, so that with a certain time delay always the same fuel pressure, both in the control chamber 7, as well as in the annular space 14 prevails.
  • the annular space 14 is sealed by a seal 17 with respect to the low-pressure region of the fuel injector.
  • the pressure in the control chamber 7 is regulated by the control valve 3.
  • the valve body 5 has a flow channel 20, which runs centrally and coaxially with the valve needle 10.
  • a throttle 22 is formed, so that the amount of the outflowing fuel can flow only throttled through the drain passage 20.
  • the outlet channel 20 opens into a recess 24, which is part of a pressure chamber 26, wherein the pressure chamber 26 is limited by a control sleeve 25, a guide pin 30 and through the recess 24 of the valve body 5.
  • the control sleeve 25 is slidably guided on the guide pin 30 and connected to a magnet armature 34 which can be moved by an electromagnet 35.
  • a closing spring 32 is supported between the control sleeve 25 and an annular disc 29, which is firmly connected to the guide pin.
  • the electromagnet 35 is energized and the control sleeve 35 pulled by the armature 34 upwards, d. H. away from the valve seat 28.
  • the pressure chamber 26 is connected to the leakage oil chamber 38, which is depressurized, since it is connected via a drain 40 with a low pressure system.
  • the pressure in the pressure chamber 26 and in the control chamber 7 decreases then and the closing force on the valve needle 10 decreases so far that the valve needle 10 moves in the direction of the control chamber 7 and thereby releases injection ports through which fuel is now injected, for example, into a combustion chamber.
  • the solenoid 35 is de-energized, so that the control sleeve 25 is pressed by the closing spring 32 again against the valve seat 28, which closes the pressure chamber 26 against the leakage oil chamber 38.
  • the nachf jobde from the annular space 14 through the throttle bore 15 fuel again increases the fuel pressure in the control chamber 7 and thus also in the pressure chamber 26, which pushes the valve needle 10 in its closed position, whereby the fuel injection is terminated.
  • FIG. 2 the area of the pressure chamber 26 is shown enlarged again.
  • a sealing surface 27 is formed, which is formed substantially annularly circular and which rests on a valve body 5 formed on the flat valve seat 28.
  • the control sleeve 25 is pressed with sufficient surface pressure against the valve seat 28, so that the pressure chamber 26 is sealed against the pressureless leakage oil chamber 38.
  • the valve body 5 has in the region of the valve seat 28 through the recess 24 has a substantially hollow cylindrical shape.
  • the recess 24 is dimensioned such that by the pressure in the pressure chamber 26, a widening of the valve body 5 in the region of the recess 24 takes place radially outward, as well as by the pressure in the pressure chamber 26, the control sleeve 25 is radially expanded.
  • valve seat 28 ' is conical here, and accordingly, the sealing surface 27' also has a conical shape.
  • the sleeve is always centered to the valve seat 28', so that the outflow of fuel from the pressure chamber 26 occurs symmetrically in the opening movement of the control sleeve 25.
  • FIG. 4 shows a further embodiment, in which case an extension 31 is formed here on the guide pin 30 ', which projects into the recess 24.
  • the volume of the pressure chamber 26 can be decisively reduced, which considerably shortens the response time of the control valve 3.
  • the shape environment of the extension 31 also makes it possible to optimize the flow conditions when the fuel flows out into the leakage oil space 38 and to generate only slight losses through swirling of the fuel flow while at the same time minimizing the volume of the pressure chamber 26.
  • valve seat 28 ' is here also conical, but the cone angle with respect to the embodiment according to Fig. 3 significantly enlarged.
  • this cone angle ⁇ the wear between the sealing surface 27 'and valve seat 28' can be further reduced:
  • the valve seat 28 ' is pressed inwards by the control sleeve 25, so that during each closing movement of the control sleeve 25, a relative movement takes place between the valve seat 28' and the sealing surface 27 '.
  • valve seat 28 ' formed as a cone with a large opening angle, this sliding can be prevented when placing the control sleeve, at the same time the relative movement of the valve seat 28' and sealing surface 27 'is suppressed by the fluctuating pressure in the pressure chamber 26.
  • cone angle ⁇ for the valve seat 28 ' so as the opening angle of the corresponding cone, a value of 155 ° to 175 ° has proven to be particularly advantageous, in particular an angle of about 160 °.
  • the sealing surface (27 ') has at least approximately the same cone angle as the valve seat 28'.
  • FIG. 5 another embodiment of the control valve is shown.
  • a bore is provided here, which passes through the entire valve body 5 and extends into the control chamber 7, wherein the diameter of the bore 12 'corresponds to the inner diameter of the control sleeve 25.
  • the guide pin 30 is designed in such a way that on the one hand it guides the control sleeve 25 and far into the valve body 5.
  • 5 bevels 33 are formed in the region of the valve body, so that a hydraulic connection of the pressure chamber 26 'to the control chamber 7 is guaranteed.
  • valve body 5 in the region of the valve seat 28 "exactly the same shape, namely a hollow cylindrical shape as the control sleeve 25, resulting in identical elastic properties, so that a relative movement between the valve seat 28 and sealing surface 27" excluded by the changing pressure in the pressure chamber 26 ' is.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (10)

  1. Soupape de commande pour un injecteur de carburant comprenant un manchon de commande (25), qui limite un espace de pression (26 ; 26') et qui est monté mobile dans une direction longitudinale, le manchon de commande (25) présentant au niveau d'un côté frontal une surface d'étanchéité (27 ; 27' ; 27'') avec laquelle il coopère avec un siège de soupape (28 ; 28' ; 28'') réalisé sur un corps de soupape (5), un évidement (24 ; 24) réalisé sous forme de trou borgne étant réalisé dans le corps de soupape (5) dans le côté du corps de soupape (5) tourné vers l'espace de pression (26 ; 26') et un élargissement du corps de soupape (5) se produisant radialement vers l'extérieur dans la région de l'évidement (24) et du manchon de commande (25), sous l'effet de la pression dans l'espace de pression (26), le manchon de commande (25) étant guidé sur une goupille de commande (30 ; 30' ; 30'') qui pénètre depuis le côté du manchon de commande (25) opposé au corps de soupape (5) dans le manchon de commande (25) de telle sorte que l'espace de pression (26 ; 26') soit limité par le manchon de commande (25), la goupille de guidage (30 ; 30' ; 30'') et le corps de soupape (5), caractérisée en ce que le manchon de commande (25) et l'évidement (24 ; 24') sont réalisés dans le corps de soupape (5) de telle sorte que la déformation du manchon de commande (25) et du corps de soupape (5) par la pression dans l'espace de pression (26 ; 26') ne conduise à aucun mouvement ou un mouvement très faible entre le siège de soupape (28 ; 28' ; 28'') et la surface d'étanchéité (27 ; 27' ; 27'') du manchon de commande (25), et la goupille de guidage (30 ; 30' ; 30'') présente une saillie (31) de diamètre réduit par rapport au diamètre intérieur du manchon de commande (25), laquelle pénètre dans l'évidement (24) du corps de soupape (5).
  2. Soupape de commande selon la revendication 1, caractérisée en ce que l'évidement (24) en forme de trou borgne présente, au niveau de son extrémité ouverte, un plus faible diamètre que le diamètre intérieur du manchon de commande (25).
  3. Soupape de commande selon la revendication 1, caractérisée en ce que le siège de soupape (28 ; 28' ; 28'') est une surface annulaire circulaire plane qui est réalisée autour de l'évidement (24).
  4. Soupape de commande selon la revendication 1, caractérisée en ce que le siège de soupape (28 ; 28' ; 28'') est réalisé sous forme conique, c'est-à-dire présente la forme d'un tronc de cône, le siège de soupape (28 ; 28' ; 28'') étant réalisé autour de l'évidement (24).
  5. Soupape de commande selon la revendication 4, caractérisée en ce que l'angle de conicité (α) du siège de soupape conique (28 ; 28' ; 28'') vaut 155° à 175°, de préférence environ 160°.
  6. Soupape de commande selon la revendication 5, caractérisée en ce que la surface d'étanchéité (27 ; 27') est également réalisée sous forme conique.
  7. Soupape de commande selon la revendication 6, caractérisée en ce que l'angle de conicité de la surface d'étanchéité (27 ; 27') et l'angle de conicité (α) du siège de soupape (28 ; 28' ; 28'') sont identiques.
  8. Soupape de commande selon la revendication 1, caractérisée en ce que l'évidement (24) est réalisé en tant qu'alésage (12') dans le corps de soupape (5), lequel présente le même diamètre que le diamètre intérieur du manchon de commande (25).
  9. Soupape de commande selon la revendication 8, caractérisée en ce que la surface d'étanchéité (27 ; 27' ; 27'') du manchon de commande (25) ainsi que le siège de soupape (28 ; 28' ; 28'') sur le corps de soupape (5) sont réalisés sous forme de surface annulaire circulaire.
  10. Injecteur de carburant pour moteurs à combustion interne comprenant une soupape de commande (3) selon l'une quelconque des revendications 1 à 11, qui ajuste la pression de carburant dans un espace de commande (7), avec un pointeau de soupape en forme de piston (10) qui coopère avec un siège de corps dans le boîtier (1) et ouvre et ferme ainsi une ouverture d'injection de telle sorte qu'en fonction de la position du pointeau de soupape (10), du carburant soit éjecté hors des ouvertures d'injection, la pression dans l'espace de commande (7) permettant d'exercer au moins de manière indirecte une force de fermeture sur le pointeau de soupape (10) dans la direction du siège de soupape et l'espace de commande (7) étant connecté hydrauliquement à l'espace de pression (26 ; 26').
EP08760855.0A 2007-06-21 2008-06-11 Soupape de commande pour une soupape d'injection de carburant Active EP2171258B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007028485 2007-06-21
DE102007044357A DE102007044357A1 (de) 2007-06-21 2007-09-17 Steuerventil für ein Kraftstoffeinspritzventil
PCT/EP2008/057304 WO2008155275A1 (fr) 2007-06-21 2008-06-11 Soupape de commande pour une soupape d'injection de carburant

Publications (2)

Publication Number Publication Date
EP2171258A1 EP2171258A1 (fr) 2010-04-07
EP2171258B1 true EP2171258B1 (fr) 2014-12-17

Family

ID=40030885

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08760769A Active EP2171257B1 (fr) 2007-06-21 2008-06-10 Soupape de commande pour injecteur de carburant, et injecteur de carburant
EP08760855.0A Active EP2171258B1 (fr) 2007-06-21 2008-06-11 Soupape de commande pour une soupape d'injection de carburant

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08760769A Active EP2171257B1 (fr) 2007-06-21 2008-06-10 Soupape de commande pour injecteur de carburant, et injecteur de carburant

Country Status (6)

Country Link
EP (2) EP2171257B1 (fr)
JP (1) JP5345612B2 (fr)
CN (2) CN101688508B (fr)
DE (2) DE102007044357A1 (fr)
RU (2) RU2468244C2 (fr)
WO (2) WO2008155260A1 (fr)

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DE102007052363A1 (de) 2007-11-02 2009-05-07 Robert Bosch Gmbh Partikelschutz für Schaltventile
DE102007060396A1 (de) 2007-12-03 2009-06-04 Robert Bosch Gmbh Mechanische Löschung von Schließprellern bei Einspritzdüsen
DE102008001913A1 (de) * 2008-05-21 2009-11-26 Robert Bosch Gmbh Kraftstoff-Injektor
DE102009026778A1 (de) * 2009-06-05 2010-12-09 Robert Bosch Gmbh Schaltventil
DE102011004640A1 (de) * 2011-02-24 2012-08-30 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor sowie Kraftstoffinjektor
DE102012211283A1 (de) * 2012-06-29 2014-01-02 Robert Bosch Gmbh Leckage- und schlupfreduziertes Ventil
RU2531671C2 (ru) * 2013-07-02 2014-10-27 Погуляев Юрий Дмитриевич Способ управления подачей топлива и устройство управления подачей топлива
RU2531475C2 (ru) * 2013-07-02 2014-10-20 Погуляев Юрий Дмитриевич Способ управления подачей топлива и устройство управления подачей топлива
DE102013214589A1 (de) * 2013-07-25 2015-01-29 Robert Bosch Gmbh Schaltventil für einen Kraftstoffinjektor
DE102013220584A1 (de) * 2013-10-11 2015-04-16 Robert Bosch Gmbh Steuerventil
DE102015204515A1 (de) 2015-03-12 2016-09-15 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor
DE102015213739A1 (de) * 2015-07-21 2017-01-26 Robert Bosch Gmbh Kraftstoffinjektor und Verfahren zur Herstellung eines Kraftstoffinjektors
CN106050499B (zh) * 2016-05-31 2017-05-24 清华大学 控制阀自锁紧的电控高压喷油器
CN206035697U (zh) * 2016-09-13 2017-03-22 罗伯特·博世有限公司 压力控制阀组件和燃料喷射装置
DE102016223914A1 (de) 2016-12-01 2018-06-07 Robert Bosch Gmbh Steuerventil für einen Kraftstoffinjektor, Kraftstoffinjektor
DE102018202107A1 (de) 2018-02-12 2019-08-14 Robert Bosch Gmbh Elektromagnetisch betätigbares Steuerventil für einen Kraftstoffinjektor und Kraftstoffinjektor
DE102018206504A1 (de) * 2018-04-26 2019-10-31 Robert Bosch Gmbh Kraftstoffinjektor
CN112761834B (zh) * 2021-01-14 2022-04-15 北京理工大学 一种电控单体泵油压控制阀

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EP2156046A1 (fr) * 2007-06-01 2010-02-24 Robert Bosch GmbH Ajustement de trajet d'armature pour électrovanne

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DE102007044355A1 (de) 2008-12-24
RU2010101642A (ru) 2011-07-27
CN101688508A (zh) 2010-03-31
DE102007044357A1 (de) 2008-12-24
RU2480616C2 (ru) 2013-04-27
CN101680413A (zh) 2010-03-24
CN101680413B (zh) 2012-10-10
CN101688508B (zh) 2012-03-21
WO2008155260A1 (fr) 2008-12-24
JP2010530492A (ja) 2010-09-09
EP2171257B1 (fr) 2012-08-15
JP5345612B2 (ja) 2013-11-20
RU2468244C2 (ru) 2012-11-27
EP2171258A1 (fr) 2010-04-07
RU2010101640A (ru) 2011-07-27
WO2008155275A1 (fr) 2008-12-24
EP2171257A1 (fr) 2010-04-07

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