US20100112498A1 - Hollow jet injector for liquid fuel - Google Patents

Hollow jet injector for liquid fuel Download PDF

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Publication number
US20100112498A1
US20100112498A1 US12/593,488 US59348808A US2010112498A1 US 20100112498 A1 US20100112498 A1 US 20100112498A1 US 59348808 A US59348808 A US 59348808A US 2010112498 A1 US2010112498 A1 US 2010112498A1
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US
United States
Prior art keywords
liquid fuel
injector
intake duct
channels
outer face
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.)
Abandoned
Application number
US12/593,488
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English (en)
Inventor
Patrice Rouchy
Joseph Vernaz
Laurent GARNIER
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.)
Saint Gobain Glass France SAS
Verallia France SA
Original Assignee
Saint Gobain Glass France SAS
Saint Gobain Emballage SA
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 Saint Gobain Glass France SAS, Saint Gobain Emballage SA filed Critical Saint Gobain Glass France SAS
Assigned to SAINT-GOBAIN GLASS FRANCE, SAINT-GOBAIN EMBALLAGE reassignment SAINT-GOBAIN GLASS FRANCE ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GARNIER, LAURENT, ROUCHY, PATRICE, VERNAZ, JOSEPH
Publication of US20100112498A1 publication Critical patent/US20100112498A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
    • F23D11/106—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet
    • F23D11/107—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet at least one of both being subjected to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/11101—Pulverising gas flow impinging on fuel from pre-filming surface, e.g. lip atomizers

Definitions

  • the invention relates to a combustion method and device in which the fuel is fed by at least one injector.
  • the invention is described more particularly for an application for melting glass in glass furnaces, in particular furnaces for manufacturing flat glass of the float type or furnaces for manufacturing holloware, for example furnaces operating by inversion like those using checker chambers (energy recuperators), but it is not necessarily limited to these applications.
  • NOx gases are harmful to humans and to the environment.
  • NO 2 is an irritant gas and the cause of respiratory ailments.
  • NOx in contact with the atmosphere, NOx can gradually form acid rain.
  • NOx causes the formation of ozone called tropospheric ozone, which, when its concentration increases at low altitude, becomes harmful to humans, especially in very hot periods.
  • the parameters that influence NOx formation have already been analyzed. They are essentially the temperature, because above 1300° C. the NOx emissions increase exponentially, due to the excess air, because the NOx concentration varies with the square root of the oxygen concentration or of the N 2 concentration.
  • a first technique consists in using a reducing agent on the emitted gases to convert the NOx to nitrogen.
  • the reducing agent may be ammonia, but this raises drawbacks such as the difficulty of storing and handling such a product. It is also possible to use a natural gas as reducing agent, but this is to the detriment of the consumption of the furnace and increases the CO 2 emissions. The presence of reducing gases in certain parts of the furnace, such as the checker chambers, can also cause accelerated corrosion of the refractories in these zones.
  • an injector is dedicated to the propulsion of the fuel, which has the function of being burned by an oxidizer.
  • the injector may form part of a burner, the term burner generally designating the device comprising both the fuel and the oxidizer intake.
  • EP921349 (or U.S. Pat. No. 6,244,524) has proposed a burner equipped with at least one injector, comprising an intake duct for a liquid fuel, of the fuel oil type, and a spray fluid intake duct placed concentrically around said liquid fuel intake duct, said liquid fuel intake duct comprising an element perforated with oblique channels to shape the liquid fuel into a hollow jet substantially matching the inside wall, the generatrix of each of said channels making an angle of at least 10°, in particular between 15° and 30°, preferably equal to 20°, with the liquid fuel intake direction.
  • a further object of the invention is to propose a combustion furnace and method suitable for all mineral glass melt preparation configurations, permitting optimal heat transfer, in particular by generating a flame having an adequate length and a sufficiently large volume to promote the maximum coverage of the glass melt and the melting batch materials.
  • the injector according to the invention is suitable for any type of glass furnace, like end-fired furnaces and cross-fired furnaces, which can be equipped with checker chambers or unit melters.
  • the invention relates to a liquid fuel spray injector comprising a liquid fuel intake duct and a spray fluid intake duct, said liquid fuel intake duct comprising an element perforated with oblique channels for shaping said fuel into a hollow rotating jet before ejection from said injector, the generatrix of each of said channels making an angle of less than 10° with the liquid fuel intake direction.
  • the injector comprises an intake duct for liquid fuel, particularly of the fuel oil type, and a spray fluid intake duct generally placed concentrically around the liquid fuel intake duct, said liquid fuel intake duct comprising an element perforated with oblique channels for shaping said fuel into a hollow rotating jet before ejection from said injector, the generatrix of each of said channels making an angle of less than 10° with the liquid fuel intake direction.
  • the liquid fuel and the spray fluid both discharge onto an outer face of the injector.
  • the spray fluid exits via a concentric orifice about the liquid fuel injection orifice. It is advantageous for the outer face of the liquid fuel intake duct and the outer face of the injector to be in the same plane.
  • the liquid fuel intake duct may also terminate in a nozzle for ejecting the liquid fuel through its outer face.
  • the outer face of the liquid fuel intake duct is the outer face of the nozzle.
  • the spray fluid intake duct may terminate in a block perforated with an orifice ejecting the spray fluid, at least part of the nozzle being inserted in said block, the outer face (terminal part) of the nozzle being aligned in the plane defined by the outer face of the block (which has no contact with the spray fluid) and onto which the orifice opens.
  • the outer face of the injector therefore corresponds here to the addition of the outer faces of the nozzle and the outer face of the block.
  • the outer face of the liquid fuel intake duct is the outer face of the nozzle here, because the liquid fuel intake duct terminates in a nozzle.
  • the liquid fuel may be ejected at a feed drive pressure of at least 1.2 MPa.
  • the liquid fuel is ejected at a temperature of between 100° C. and 150° C., preferably between 120° C. and 140° C.
  • Such a temperature range serves to adjust any type of liquid fuel used in present-day installations, in particular glass furnaces, to the viscosity required immediately before it is ejected from its intake duct.
  • This viscosity may advantageously be at least 5 ⁇ 10 ⁇ 6 m 2 /s, in particular between 10 ⁇ 5 and 2 ⁇ 10 ⁇ 5 m 2 /s.
  • the angle of the opening cone of liquid fuel ejection is correlated with the angle made by the oblique channels in the element for shaping the liquid fuel into a hollow jet with the liquid fuel intake direction.
  • the liquid fuel is ejected in a cone having an apex angle of at least 10°, especially between 3° and 8°.
  • An apex angle of about 5° is particularly suitable.
  • the spray fluid it is ejected very advantageously at a flow rate of not more than 70 Sm 3 /h, generally between 30 and 60 Sm 3 /h.
  • the spray fluid flow rate is correlated with the pressure of said fluid, a pressure that must be reduced to the maximum.
  • a maximum flow rate like the rate mentioned above, a sufficient flame length can be obtained for all existing glass furnace configurations.
  • the liquid fuel intake duct may comprise a cylindrical tube and a nozzle.
  • the nozzle may be fixed, in particular screwed, to the end of the cylindrical tube.
  • a particularly suitable nozzle geometry for the injector of the invention is such as to comprise a frustoconical swing chamber prolonged by an end piece having a cylindrical inside wall.
  • the apex angle theta of the swing chamber is at least 30°, preferably between 55° and 65°, in particular 60°, thereby minimizing the pressure drops of the liquid fuel flow.
  • the element used to form the hollow rotating jet of liquid fuel substantially obstructs the liquid fuel intake duct and is perforated with channels, in particular cylindrical, oblique with regard to the liquid fuel intake direction.
  • This element confers on the liquid fuel a rotating flow enabling it to assume the shape of a hollow jet, and gives it a sufficiently high level of mechanical energy for it to be sprayed at the outlet of its intake duct into droplets having an optimal size dispersion.
  • the channels may advantageously be uniformly distributed on the circumference of the element.
  • This element has a suitable shape for being inserted into the liquid fuel intake duct and may, for example, be a cylinder, preferably having two substantially parallel faces (pellet shape). These faces are also preferably oriented in a direction perpendicular to the liquid fuel intake direction.
  • the element comprising the channels may therefore in particular have a cylindrical shape whereof the axis coincides with the liquid fuel intake direction.
  • the orientation of each of the channels is selected so that their generatrix makes an angle alpha of less than 10°, and even of less than 8°, and even of less than 6°, in particular about 5° with the liquid fuel intake direction.
  • the orientation of each of the channels is selected so that their generatrix makes an angle alpha of more than 2°, or even more than 3°, even more than 4° with the liquid fuel intake direction.
  • This particular orientation serves to obtain a synergy between all the “divided” jets of liquid fuel leaving their corresponding channels, so that, when they exit therefrom, they contribute to the creation, downstream, of a single hollow jet matching the inside wall of any duct following the element comprising the channels (swing chamber followed by end piece for liquid fuel expulsion).
  • each channel is defined in particular by an orifice on each side of the element, that is by two orifices per channel.
  • the center of the orifices of all the channels located on one side of the element are uniformly distributed on a circle of which the center corresponds to the axis of the element and of the injector. It is possible thereby to define two circles each located on either side of the element.
  • the radius R of these two circles may be identical.
  • R may be between 2.5 and 4.5 mm.
  • S is the surface area of all the channels included in the element, then an S/R ratio of 6 to 13 mm is preferred.
  • the element may be mounted in a sealed manner upstream of the nozzle, in the liquid fuel intake duct, preferably against the swing chamber.
  • downstream and upstream must be understood with reference to the liquid fuel intake direction.
  • the spray fluid intake duct preferably comprises at least one cylindrical tube at the end of which a block drilled with an orifice is placed, preferably screwed, and in which at least part of the nozzle according to the invention is inserted.
  • the orifice of the block and the outer wall of the part of the nozzle inserted therein are positioned concentrically.
  • This preferred arrangement can also be obtained by the abovementioned screwing, for ensuring the self-centering of the elements described above, that is the orifice of the block with regard to the part of the nozzle inserted therein.
  • This concentricity is advantageous insofar as its absence incurs a risk of formation of very large droplets of liquid fuel, of the fuel oil type, at the periphery of the hollow jet which may cause mediocre combustion, particularly with a risk of increasing the threshold of appearance of carbon monoxide.
  • the outer face (terminal part) of the nozzle prefferably be aligned in the plane defined by the outer face of the block, that is the face lacking any contact with the spray fuel, and onto which the orifice opens.
  • an incorrect alignment implies a modification of the aerodynamics of the liquid fuel and of the spray fluid when they leave their respective intake duct.
  • the injector according to the invention described above is mounted in a sealed manner in a refractory block using a sealing device comprising a plate provided with cooling fins.
  • a sealing device comprising a plate provided with cooling fins.
  • the injector according to the invention may be fixed to an adjustable support, a ventilation nozzle being oriented toward the downstream end of the injector, more particularly toward the abovementioned plate.
  • the support is preferably adjustable for inclination, bearing and translation, in particular to bear against the plate of the sealed device.
  • the ventilation nozzle As to the ventilation nozzle, it blows air, serving to prevent excessive local overheating at the downstream end of the injector.
  • the liquid fuel intake duct may comprise at least one diffuser.
  • the liquid fuel used in the context of the invention is a liquid fossil fuel commonly used in combustion devices to heat glass batch materials in a glass furnace. It may for example be heavy fuel oil.
  • the spray fluid is similarly the one commonly found in conventional installations and which serves to spray the abovementioned liquid fuel. This may for example be air (in this case called primary air as opposed to the secondary air which serves as the main oxidizer). It may also be natural gas, oxygen (in the case of oxycombustion) or steam.
  • the invention applies in particular to fuels of the heavy fuel oil type and it serves to circulate very large throughshapes (500 to 600 kg/h) of this type of fuel on a single injector according to the invention.
  • the liquid fuel flow rate in the injector is to be determined from the type of furnace on which it is to be mounted, of its operating parameters such as its outshape, and the type of liquid fuel used. These values may be determined without difficulty by a person skilled in the art, who can in particular prepare charts by performing tests. A person skilled in the art will also be sure to select a carefully prepared surface, respectively of the swing chamber, the channels, and the end piece of the inside walls, so as to ensure a minimum of pressure drops caused by friction of the liquid fuel flushing said elements at high speed.
  • the injector according to the invention generates little NOx in the combustion chamber, for example a furnace, it operates with a low spray fluid flow rate, allowing a broad and flexible use of the oxidizer, and therefore, ultimately obtaining good results from the energy standpoint.
  • the injector is generally integrated with a burner further comprising an oxidizer inlet.
  • This oxidizer may be air, oxygen-enriched air or pure oxygen.
  • the injector is placed under the oxidizer inlet.
  • the oxidizer is air or oxygen-enriched air
  • the air enters via an opening having a relatively large cross section, which may in particular be between 0.5 and 3 m 2 , a plurality of injectors possibly being combined at each air inlet.
  • the invention is particularly suitable for manufacturing high grade glass, in particular optical, such as flat glass prepared by the float process, or holloware.
  • the furnace equipped with the injector according to the invention emits little NOx, without any risk of reducing combustion that is potentially harmful to the color of the glass.
  • the invention may in particular advantageously supplement the techniques described in U.S. Pat. No. 6,047,565 and WO9802386.
  • FIG. 1 shows a schematic partial section of an injector according to the invention.
  • FIG. 2 shows an element according to the invention, perforated with channels shaping the fuel into a hollow jet in a side view of a section ( FIG. 2 a ) and a plan view ( FIG. 2 b ).
  • FIG. 3 shows a vertical section of a wall of a glass furnace comprising an injector according to FIG. 1 .
  • FIG. 1 shows a partial section of an injector 1 according to the invention.
  • This injector 1 comprises two fluid feeds, that is respectively the liquid fuel intake duct 2 and the spray fluid intake duct 3 .
  • liquid fuel and spray fluid intake ducts are connected respectively, upstream of the flow of each of the two fluids, to a circuit issuing from a liquid fuel source and a spray fluid source not shown.
  • the liquid fuel intake duct 2 consists essentially of a cylindrical tube 21 at the end whereof a nozzle 22 is screwed. Said nozzle, at its downstream end, comprises a frustoconical swing chamber 23 prolonged by an end piece 24 having a cylindrical inside wall 25 .
  • the apex angle theta of the swing chamber 23 is 60°.
  • a cylinder mounted in a sealed manner thrusting against said chamber 23 .
  • Said cylinder 4 is the element perforated with the oblique channels shaping the liquid fuel into a hollow jet.
  • the cylinder 4 comprises channels 41 uniformly distributed on its circumference and has two faces 42 , 43 parallel to one another and substantially perpendicular to the liquid fuel intake direction symbolized by the arrow f in FIG. 1 , a direction that is also identical to that of the spray fluid intake.
  • the channels 41 are cylindrical, their generatrix making an angle alpha of 5° with the abovementioned intake direction.
  • the spray of fluid intake duct 3 essentially comprises a cylindrical tube 31 at the end of which a block 32 is screwed, whereof the inside shoulder 33 thrusts against the downstream end of the tube 31 .
  • the block 32 is perforated with an orifice 34 having a shape suitable for the insertion of part of the nozzle 22 .
  • the block 32 on the side of the orifice 34 , also has a projecting part 35 suitable for screwing the block 32 to the cylindrical tube 31 to ensure perfect self-centering of the outer wall 26 of the end piece 24 inside the orifice 34 .
  • Such an arrangement serves to preserve the aerodynamics of the two fluids when they exit from their respective intake ducts.
  • FIG. 2 shows the cylinder 4 in FIG. 1 in greater detail, in a side section ( FIG. 2 a ) and a plan view ( FIG. 2 b ).
  • FIG. 2 b shows that the cylinder comprises 8 channels 20 whereof the centers are uniformly distributed on a circle having a radius R.
  • FIG. 2 b only shows the orifice emerging from these channels, that is the orifice opening from the top of the part, except for one of these channels, for which the upper orifice 21 is drawn by a continuous circle and the bottom orifice 22 is drawn by a dotted circle. All the channels are obviously identical.
  • FIG. 2 a shows the cylinder in a side view, and only the channel of the orifices 21 and 22 has been shown.
  • the axis of this channel makes an angle alpha with the axis of the cylinder itself which corresponds to the liquid fuel intake direction. In the context of the invention, the angle alpha is lower than 10°.
  • FIG. 3 shows a vertical section of a wall of a glass furnace comprising an injector 5 according to FIG. 1 .
  • the injector 5 comprises a support 6 that is adjustable for inclination, bearing and translation. Fixed to this adjustable support 6 is the injector 5 which bears against the walls of a refractory block 7 , via a plate 8 provided with cooling fins.
  • the refractory block 7 is itself mounted in an opening of the wall of the furnace 9 .
  • the injector 5 also comprises a ventilation nozzle 10 oriented toward the abovementioned plate.
  • the liquid fuel conveyed via the cylindrical tube 21 , is divided into as many individual jets as the number of tangential channels 41 .
  • the individual jets then enter the swing chamber 23 , striking its walls, with a minimum of pressure drops due to the fact that the value of the apex angle theta is 60°.
  • This centrifugation in the swing chamber serves, downstream, to enable the fuel to follow a helicoidal trajectory by assuming the shape of a hollow jet matching the inside wall 25 of the end piece 24 .
  • the liquid fuel has thereby acquired maximum mechanical energy and, under the influence of the spray fluid, it bursts vertically into very fine droplets having an optimal size dispersion.
  • Such a dispersion gives the flame leaving the injector, once activated by the main oxidizer, a very uniform temperature along its whole length.
  • Such a fuel spray for a given fuel flow rate, also considerably lengthens the flame in comparison with a spray that would be caused by the same injector 1 without cylinder 4 .
  • the cylinder 4 must be dimensioned in such a way that it is never completely filled, and that according to the invention, a hollow jet substantially matching this inside wall is always obtained.
  • the injector described above is of simple and inexpensive design. It is also completely and easily removable and adaptable to already existing installations.
  • a 144 m 2 (surface area of glass melt) end-fired furnace is equipped with a burner comprising an air inlet stream under which four injectors of liquid fuel oil heated to 130° C. are placed. This burner has a capacity of 15 megawatts.
  • Each injector contains an element for rotating the fuel oil comprising 8 holes 2.3 mm in diameter, whereof the axis makes a 5° angle to the liquid fuel oil intake direction. The axes of these holes are arranged on a circle having a radius of 3.75 mm.
  • the total fuel oil flow rate (sum of flow rates fed to all the injectors) was 2000 kg/h.
  • the air was fed to the burner in stoechiometric conditions with regard to the fuel oil.
  • the NOx measured in the fluid gases was 550 mg per Sm 3 .
  • example 1 The procedure of example 1 was followed, except that the holes had an axis making a 20° angle to the liquid fuel oil intake direction.
  • the NOx measured in the flue gases was 800 mg per Sm 3 .

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)
  • Nozzles (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Telephone Function (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Clamps And Clips (AREA)
US12/593,488 2007-03-26 2008-03-21 Hollow jet injector for liquid fuel Abandoned US20100112498A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR0754028 2007-03-26
FR0754028A FR2914397B1 (fr) 2007-03-26 2007-03-26 Injecteur a jet creux de combustible liquide.
PCT/FR2008/050492 WO2008132388A1 (fr) 2007-03-26 2008-03-21 Injecteur a jet creux de combustible liquide

Publications (1)

Publication Number Publication Date
US20100112498A1 true US20100112498A1 (en) 2010-05-06

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ID=38858906

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/593,488 Abandoned US20100112498A1 (en) 2007-03-26 2008-03-21 Hollow jet injector for liquid fuel

Country Status (15)

Country Link
US (1) US20100112498A1 (fr)
EP (1) EP2126470B1 (fr)
JP (1) JP5603230B2 (fr)
CN (1) CN101680654B (fr)
AT (1) ATE473397T1 (fr)
BR (1) BRPI0809072B1 (fr)
DE (1) DE602008001722D1 (fr)
EA (1) EA015872B1 (fr)
ES (1) ES2348575T3 (fr)
FR (1) FR2914397B1 (fr)
MX (1) MX2009010318A (fr)
PL (1) PL2126470T3 (fr)
PT (1) PT2126470E (fr)
UA (1) UA97977C2 (fr)
WO (1) WO2008132388A1 (fr)

Cited By (1)

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US20100304314A1 (en) * 2007-05-10 2010-12-02 Saint-Gobain Emballage Low nox mixed injector

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US8161751B2 (en) * 2009-04-30 2012-04-24 General Electric Company High volume fuel nozzles for a turbine engine
FR2974884A1 (fr) * 2011-05-02 2012-11-09 Air Liquide Procede de pulverisation assistee et pulverisateur robuste correspondant
SE537347C2 (sv) * 2012-08-31 2015-04-07 Reformtech Heating Holding Ab Apparat för förbränning
CN103574639B (zh) * 2013-11-13 2015-09-30 中国南方航空工业(集团)有限公司 燃油喷嘴和发动机
CN106705680B (zh) * 2016-12-16 2023-05-12 昆明理工大学 一种炉膛底部供热的旋转射流氧枪及其应用方法

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US1757023A (en) * 1926-10-20 1930-05-06 Ira E Smith Oil burner
US2325495A (en) * 1940-01-12 1943-07-27 Nat Airoil Burner Company Inc Oil burner
US3785570A (en) * 1972-08-30 1974-01-15 Us Army Dual orifice fuel nozzle with air-assisted primary at low flow rates
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US3897200A (en) * 1974-03-04 1975-07-29 Howe Baker Eng Cyclonic multi-fuel burner
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US4487369A (en) * 1982-01-11 1984-12-11 Essex Group, Inc. Electromagnetic fuel injector with improved discharge structure
US4644878A (en) * 1985-11-05 1987-02-24 The United States Of America As Represented By The United States Department Of Energy Slurry burner for mixture of carbonaceous material and water
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BRPI0809072B1 (pt) 2019-09-24
JP2010522864A (ja) 2010-07-08
CN101680654B (zh) 2012-09-05
EA015872B1 (ru) 2011-12-30
CN101680654A (zh) 2010-03-24
WO2008132388A1 (fr) 2008-11-06
ATE473397T1 (de) 2010-07-15
FR2914397B1 (fr) 2009-05-01
BRPI0809072A2 (pt) 2014-09-09
PL2126470T3 (pl) 2010-12-31
MX2009010318A (es) 2009-10-19
UA97977C2 (ru) 2012-04-10
PT2126470E (pt) 2010-10-14
JP5603230B2 (ja) 2014-10-08
ES2348575T3 (es) 2010-12-09
EA200970888A1 (ru) 2010-04-30
FR2914397A1 (fr) 2008-10-03
EP2126470B1 (fr) 2010-07-07
DE602008001722D1 (de) 2010-08-19
EP2126470A1 (fr) 2009-12-02

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