Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
  • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
  • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
  • F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
  • F01K13/00—General layout or general methods of operation of complete plants
  • F01K13/02—Controlling, e.g. stopping or starting
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
  • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
  • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
  • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
  • F28D21/0001—Recuperative heat exchangers
  • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
  • F28D2020/0004—Particular heat storage apparatus
  • F28D2020/0008—Particular heat storage apparatus the heat storage material being enclosed in plate-like or laminated elements, e.g. in plates having internal compartments
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
  • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
  • Y02E60/14—Thermal energy storage
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the invention relates generally to the recovery of energy in the exhaust lines of a motor vehicle.
• the invention relates in a first aspect to a motor vehicle exhaust line, of the type comprising:
• a heat exchanger having a first exhaust gas circulation side and a second circulation side of a heat exchange fluid
• the means for recovering the thermal energy of the exhaust gases have little or no thermal inertia.
• the energy recovered by the closed cycle is almost directly proportional to the energy available in the exhaust.
• the power demanded by the driver to the motor can vary for example between 0 kW, when the engine is idling, 10 kW, when the vehicle is traveling at 40 km / h, and up to 100 kW, during violent acceleration.
• the invention aims to provide an exhaust line in which the recovery of the thermal energy of the exhaust gas is performed with a better efficiency.
• the invention relates to an exhaust line of the aforementioned type, characterized in that the heat exchanger comprises an intermediate wall. interposed between the first and second sides of the heat exchanger, the intermediate wall comprising at least one closed cavity containing a phase change material, the wall having a first heat exchange surface in thermal contact with the exhaust gas, and a second exchange surface in thermal contact with the heat exchange fluid.
• the exhaust line may also have one or more of the following characteristics, considered individually or in any technically possible combination: the intermediate wall comprises a plurality of closed cavities each containing a quantity of phase-change material, the cavities closed being isolated from each other;
• the phase-change material comprises one or more inorganic salts, chosen from the group comprising NaOH, KOH, LiOH, NaNO 2 , NaNO 3 , KNO 3 , Ca (NO 3 ) 2 , LiNO 3 , KCl, LiCl, NaCl, MgCl 2 , CaCl 2 , Na 2 CO 3 , K 2 CO 3 , Li 2 CO 3 , KF, LiF;
• the phase change material comprises one or more metals selected from the group consisting of Sn, Pb and Zn;
• the phase-change material has a melting point of between 10 ° C. and 500 ° C .;
• the phase change material has a latent heat of fusion of between 100 and 300 kJ / kg;
• the intermediate wall comprises a mass of phase-change material chosen to allow storage of a thermal energy of between 0.1 kWh and 10 kWh;
• the closed cycle is a Rankine cycle or a Hirn cycle
• the closed cycle comprises a motor shaft, and a drive member in rotation of the motor shaft by the heat exchange fluid;
• the heat exchange fluid essentially comprises water; the closed cycle is dimensioned so that the heat exchange fluid has a reference temperature at the outlet of the heat exchanger, the phase-change material having a melting point between the reference temperature and the reference temperature. plus 100 ° C.
• the exhaust line includes:
• an upstream exhaust gas flow pipe fluidly connected to an inlet on the first side of the heat exchanger;
• an exhaust gas flow downstream duct fluidly connected to an outlet on the first side of the heat exchanger;
• bypass duct connecting the upstream duct to the downstream duct bypassing the heat exchanger
• an exhaust gas guidance device capable of directing a fraction of the exhaust gases to the heat exchanger and another fraction of the exhaust gases to the bypass duct
• a control member of the steering member adapted to selectively control said fraction of the exhaust gas directed to the heat exchanger and said other fraction of the exhaust gas directed to the bypass duct.
• the invention relates to a method of controlling an exhaust line having the above characteristics, the method comprising the following steps:
• the method may further have the following characteristics:
• FIG. 1 is a schematic representation of an exhaust line according to the invention
• FIG. 2 is a schematic representation of the heat exchanger of the exhaust line of FIG. 1;
• FIG. 3 is a step diagram indicating the main steps of the control method of the exhaust line of FIG. 1;
• FIGS. 4 and 5 are graphical and schematic representations of curves indicating the fraction of the flow of exhaust gas directed towards the heat exchanger as a function of the energy available at the exhaust.
• the exhaust line 1 shown in a simplified manner in FIG. 1 comprises:
• a manifold 3 provided for capturing the exhaust gases leaving the combustion chambers of the engine 5 of the motor vehicle;
• a heat exchanger 7 having a first exhaust gas circulation side and a second circulation side of a heat exchange fluid
• a downstream duct 1 1 for the circulation of exhaust gases connected to an outlet 12 on the first side of the heat exchanger 7;
• a bypass duct 13 connecting a point of the upstream duct to a point of the downstream duct 1 1 by bypassing the heat exchanger 7;
• the bypass duct 13 connects a T-shaped intersection 21 formed in the upstream duct to another intersection T 23 formed in the downstream duct 11.
• Unrepresented equipment such as a turbo compressor, can be interposed between the collector 3 and the intersection T 21.
• the downstream duct 1 1 is fluidly connected to the cannula (not shown) for the release of the purified exhaust gas into the atmosphere.
• Other unrepresented members such as a silencer and exhaust gas purification members, are interposed between the intersection T 23 and the cannula.
• the closed cycle 19 for recovering a portion of the thermal energy of the exhaust gases is for example a Rankine cycle.
• the Rankine cycle comprises a turbine 25, a condenser 27, and a pump 29.
• a pipe 31 connects an outlet 33 of the second side of the heat exchanger to a high pressure inlet of the turbine 25.
• a pipe 37 connects a low pressure outlet of the turbine 25 to an inlet of the condenser 27.
• a pipe 37 connects an outlet of the condenser 27 to a suction inlet of the pump 29.
• a pipe 39 connects a discharge outlet of the pump 29 has an inlet 41 on the second side of the heat exchanger 7.
• the turbine 25 drives a motor shaft 43 in rotation, the latter being for example connected to an electric generator 45.
• the shaft 43 may drive a mechanical member of the vehicle.
• the turbine 25 can be replaced by a steam engine coupled to the motor shaft 43.
• the thermal fluid circulating in the closed cycle 19 typically comprises essentially water.
• the fluid may comprise various additives, for example to limit corrosion or prevent freezing.
• the thermal fluid is vaporized in the heat exchanger 7, under the effect of heat ceded by the exhaust gas.
• the thermal fluid may also be an organic fluid adapted to a cycle such as the Rankine cycle.
• the fluid may be for example Genetron ® 245FA, marketed by Honeywell.
• the heat exchanger 7 has an intermediate wall 47 interposed between the first and second side 49 and 51 of the heat exchanger.
• the intermediate wall 47 has a plurality of cavities 53 each containing an amount of a phase change material.
• the intermediate wall 47 typically consists essentially of a heat conducting material, for example aluminum, an aluminum alloy or a steel.
• Each cavity 53 is completely closed, and isolated from the other cavities 53.
• the phase-change material contained in the cavity 53 is completely isolated from the medium outside the cavity.
• the cavities 53 are distributed, preferably uniformly, over most of the surface of the wall 47. Preferably, the cavities 53 are uniformly distributed over the entire surface of the wall 47.
• the intermediate wall 47 has a first exchange surface 55 in thermal contact with the exhaust gas, and a second exchange surface 57 in thermal contact with the heat exchange fluid.
• the surfaces 55 and 57 constitute the two large opposite faces of the intermediate wall.
• the first exchange surface 55 is in direct contact with the exhaust gas flowing from the first side of the heat exchanger.
• the surface 55 partially defines the first side of the heat exchanger.
• the second heat exchange surface 57 is preferably in direct contact with the heat exchange fluid flowing on the second side.
• the surface 57 partially defines the second side of the heat exchanger.
• the heat exchanger 7 is constructed so as to put the exhaust gas in thermal contact with the first heat exchange fluid, the exhaust gas yielding through the intermediate wall part of their thermal energy to the heat exchange fluid.
• the phase change material typically comprises one or more inorganic salts.
• These inorganic salts are chosen from the group comprising NaOH, KOH, LiOH, NaNO 2 , NaNO 3 , KNO 3 , Ca (NO 3 ) 2 , LiNO 3 , KCl, LiCl, NaCl, MgCl 2 , CaCl 2 , Na 2 CO 3. , K 2 CO 3 , Li 2 CO 3 , KF, LiF.
• the phase change material is one of these inorganic salts or a mixture of two or three of these inorganic salts.
• the phase change material may also comprise one or more metals selected from Sn, Pb and Zn.
• said material consists of one or more metals chosen from Sn, Pb and Zn.
• the phase change material has a melting temperature of from 100 ° C to 500 ° C, preferably from 150 to 400 ° C, and more preferably from 200 to 350 ° C.
• the phase change material typically has a latent heat of fusion of between 100 and 300 kJ / kg, for example between 150 and 250 kJ / kg.
• the phase change material is a binary salt comprising about 60% NaNO 3 , and 40% KNO 3 .
• the phase-change material may be the salt sold commercially under the name HitecXL, which is a ternary salt comprising about 48% Ca (NO 3) 2 ,
• the phase change material contained in the intermediate wall is provided to form a thermal energy buffer.
• a portion of the excess energy is stored in the material at phase change of the intermediate wall.
• these materials have a relatively high latent heat of fusion, the excess energy for melting said phase change material.
• the phase-change material restores the stored thermal energy, by solidification of the previously melted material.
• the mass of phase change material incorporated in the intermediate wall is chosen to allow storage of a total thermal energy of between 0.1 and 10 kWh, preferably between 0.5 kWh and 5 kWh.
• the mass is chosen to allow the storage of an energy of between 1 and 2 kWh.
• the Rankine cycle 19 has a temperature-dependent yield having a bell-shaped shape.
• the temperature considered here is the temperature of the heat exchange fluid at the outlet of the heat exchanger 7. This efficiency is zero below the vaporization start temperature of the heat exchange fluid. It increases to a reference temperature Tref, for which the cycle is sized.
• the phase change material is chosen so that its melting temperature substantially corresponds to the optimum operating temperature of the Rankine cycle. For example, said melting temperature is between Tref and Tref + 100 ° C., preferably between Tref and Tref + 50 ° C.
• the orientation member 15 is a 3-way valve, mounted at the intersection T 21. It is controlled by the computer 17.
• the 3-way valve is selectively able to direct all the exhaust gas to the 7, directing all the exhaust gases to the bypass duct 13, or directing a determined fraction of the exhaust gases to the exchanger 7, and the remainder of the exhaust gases to the bypass duct. Said fraction is determined by the computer 17, as described below.
• the exhaust line is furthermore equipped with a probe 47 for measuring the temperature of the exhaust gases and with a probe 49 for measuring the flow of the exhaust gases, implanted for example in the upstream duct 9. probes inform the calculator 17.
• the exhaust line further comprises a probe 51 for measuring the temperature of the heat exchange fluid, and a probe 53 for measuring the pressure of said heat exchange fluid, implanted on the conduit 31 connecting the outlet 33 of the second side. from the heat exchanger 7 to the turbine 25.
• These probes inform the computer 17.
• the motor of a motor vehicle operates at variable load. When the engine is idling, the power demanded by the driver is about 0 kW. When the vehicle is traveling at a speed of 40 km / h, the power demanded by the driver is about 10 kW. In the event of violent acceleration, the power demanded from the motor can go up to 100 kW.
• the closed cycle 19 is sized to recover a thermal power of about 40 kW in the exhaust gas.
• the thermal power available in the exhaust gases leaving the engine is, for example, 60 kW.
• the closed cycle recovers approximately 40 kW of thermal power in the exhaust gas, and a portion of the excess 20 kW is removed and stored by the phase change material.
• the thermal power available in the exhaust gas is for example only 20 kW.
• the buffer capacity constituted by the phase change material then becomes empty, a portion of the thermal energy stored in the phase change material being transferred to the heat exchange fluid of the closed cycle.
• step S1 the computer acquires the temperature T and the flow rate Q of the exhaust gas stream at the outlet of the collector 3 via the probes 47 and 49. From these values, the computer evaluates at step S2 the thermal energy Edispo available in the exhaust gas, and can be recovered by the closed cycle 19 in the heat exchanger 7.
• step S3 the computer acquires from the probes 51 and 53 the pressure P and the temperature T of the heat exchange fluid of the Rankine cycle. From the values of pressure and temperature acquired, the computer evaluates in step S4 the thermal energy Econso actually received by the Rankine cycle. This thermal energy is converted into mechanical energy by the turbine or lost.
• step S5 the computer evaluates the charge of the phase change material.
• charge is meant here the amount of thermal energy stored in the phase change material at the current time. This charge can be expressed as a percentage of the total thermal energy storage capacity of the phase change material. The charge can also be expressed directly as a stored energy.
• the charge of the phase change material is calculated by, for example, periodically performing energy balances for the phase change material.
• the charge of the phase change material at time t + 1 is equal to the charge of the phase change material at the instant t increased by the energy actually transferred by the exhaust gases in the exchanger, decreased Econso energy actually received by the closed cycle.
• the energy actually transferred by the exhaust gases in the exchanger is evaluated by the calculator, among others, from the thermal energy available in the Edispo exhaust gas, from the fraction of the exhaust gas flow directed towards the exhaust gas.
• the exchanger of the pressure and temperature of the thermal fluid in the closed cycle acquired in step S3.
• the calculator determines the fraction of the flow of exhaust gas that must be directed towards the heat exchanger 7, as a function of the thermal energy Edispo provided by the exhaust gas evaluated at step S2, the fluid temperature T of the heat exchange fluid of the closed cycle, acquired via the probe 51, and / or the charge of the phase change material evaluated in step S5.
• the fraction of the exhaust stream that is not directed to the heat exchanger 7 is directed towards the bypass duct.
• the computer then controls the movement of the valve of the 3-way valve 15 to a position in which the flow of exhaust gas is distributed to the exchanger and the bypass duct as determined in step S6.
• the position of the valve is read by the computer in tables or on predetermined curves, as a function at least of the flow of exhaust gas leaving the manifold and the fraction of the flow of exhaust gas to be directed to the exchanger.
• the fraction of the flow of exhaust gas directed towards the heat exchanger is determined by the computer for example using the graph of FIG. 4.
• This figure shows a network of curves, parameterized according to the load. phase change material. Each curve corresponds to a different state of charge of the phase change material.
• the solid curve corresponds to a load of 0%, and the two curves in broken lines at 50% and 100% load.
• Each curve indicates the fraction of the flow of exhaust gas directed towards the exchanger, as a function of the thermal energy provided by the exhaust gases leaving the engine.
• Eref corresponds, for example, to the thermal energy for which the closed cycle of recovery is dimensioned. For example Eref is worth 40 kW.
• these portions could have another shape and be arched or have arcuate portions.
• the curves of FIG. 4, in practice, are determined by simulation and / or experimentally.
• the fraction of the flow of exhaust gas directed towards the exchanger can be determined in step S6 by the computer using the graph of FIG. 5.
• This graph comprises a network of curves parameterized as a function of the temperature of the thermal fluid at the outlet of the exchanger. Each curve corresponds to a different acquired temperature for the heat exchange fluid of the closed cycle 19.
• the curve in solid line corresponds to the temperature of the heat exchange fluid for which the closed cycle has been dimensioned. If the heat exchange fluid is water, this temperature may be for example 250 ° C. This temperature can also be significantly different from
• the phantom curve corresponds to an acquired temperature lower than the reference temperature.
• the dashed curve corresponds to an acquired temperature higher than the reference temperature. It is shown that three curves in Figure 5, but it is possible to integrate much more in the computer memory.
• 100% of the exhaust gas flow is directed to the heat exchanger when the energy provided by the exhaust gas is less than a reference energy.
• the fraction of the flow of exhaust gas directed towards the exchanger decreases progressively. This fraction decreases at an average speed when the acquired temperature corresponds to the reference temperature for the design of the closed cycle. This fraction decreases less rapidly when the temperature acquired is lower than the reference temperature. This fraction decreases faster when the acquired temperature is higher than the reference temperature.
• the computer can determine the fraction of the flow of exhaust gas directed towards the heat exchanger using a network of curves parameterized as a function of both the charge of the phase change material. and the acquired temperature of the heat exchange fluid.
• the heat exchanger has an intermediate wall interposed between the first and second sides of the heat exchanger, the intermediate wall comprising at least one closed cavity containing a phase change material, the wall having a first surface of the heat exchanger. exchange in thermal contact with the exhaust gas and a second exchange surface in thermal contact with the heat exchange fluid, the closed recovery cycle has a significant thermal inertia, to dampen the variations in the amount of thermal energy provided by the exhaust gases leaving the engine. A certain amount of heat energy can be stored inside the heat exchanger itself.
• phase change material When the energy available at the exhaust is greater than the energy that the closed cycle can recover and recover, the phase change material is charged. This charging is carried out by melting the phase change material, which is converted from the solid state to the liquid state. Such a phase change absorbs a large amount of thermal energy, corresponding to the latent heat of melting of said material.
• the phase-change material releases a fraction of the stored thermal energy, transferring an additional energy. to the heat exchange fluid of the closed cycle.
• the closed cycle of recovery can thus continue to operate for a certain duration, even if the energy provided by the exhaust gases is reduced.
• the closed cycle will be de-energized once the phase change material is fully discharged into thermal energy. This defusing occurs when the heat exchange fluid exits the heat exchanger 7 at a temperature below its vaporization temperature.
• the invention makes it possible to postpone the moment of defusing the closed cycle.
• phase change material constituting a heat energy buffer in the exchanger makes it possible to operate the closed cycle as close as possible to its reference temperature.
• the melting temperature of the phase change material is chosen close to the reference temperature of the heat exchange fluid.
• the phase change material will increase its charge by taking a part of the thermal energy transferred from the exhaust gas to the heat exchange fluid.
• This mechanism can contribute to keeping the heat exchange fluid close to its reference temperature, that is to say at a temperature at which the efficiency of the closed cycle is optimal.
• the orientation member could be arranged at the T-intersection located downstream of the heat exchanger.
• this member could not be a three-way valve, but include two two-way proportional valves, one on the bypass duct, and the other in series with the exchanger to modulate the flow of exhaust gas. through the exchanger.
• the closed cycle of energy recovery may not be a cycle of
• Rankine but be a cycle of Hirn, or any other suitable cycle.
• the third magnitude representative of the quantity of thermal energy stored in the phase-change material of the intermediate wall is evaluated by: evaluating a fourth magnitude representative of a quantity of thermal energy actually received by the closed cycle in the heat exchanger; deducing the third magnitude at least from the first magnitude and the fourth magnitude.

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• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Engine Equipment That Uses Special Cycles (AREA)
• Air-Conditioning For Vehicles (AREA)

Priority Applications (3)

Applications Claiming Priority (2)

Publications (2)

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Cited By (6)

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• 2009
  • 2009-03-25 FR FR0951920A patent/FR2943731A1/fr not_active Withdrawn
• 2010
  • 2010-03-25 US US13/259,564 patent/US20120090293A1/en not_active Abandoned
  • 2010-03-25 JP JP2012501360A patent/JP2012522920A/ja active Pending
  • 2010-03-25 WO PCT/FR2010/050545 patent/WO2010109145A2/fr active Application Filing
  • 2010-03-25 DE DE201011001357 patent/DE112010001357T5/de not_active Ceased

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