Classifications

• • 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
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
  • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
• • 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
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0006—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the plate-like or laminated conduits being enclosed within a pressure vessel
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
  • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
  • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, plate-like elements

Definitions

• the invention relates to a heat exchanger especially for a motor vehicle, such as an internal heat exchanger disposed in an air conditioning circuit.
• heat exchangers for motor vehicles consisting of a bundle of tubes arranged in parallel on one or more rows, the tubes being intended for the circulation of a heat transfer fluid through the heat exchanger.
• Heat exchangers are also known comprising a plurality of superimposed plates configured to define circulation channels for a heat transfer fluid for the heat exchange between the heat transfer fluid and a surrounding medium.
• the subject of the invention is a heat exchanger between a first fluid and a second fluid, comprising a plurality of thermal modules constituted respectively of an upper plate and a lower plate assembled by defining between them a first internal cavity. forming a first circulation channel for the first fluid and at least one circulation space defined between two consecutive thermal modules forming a second circulation channel for the second fluid.
• the circulation space comprises fins, called second fins, with a length of between 50 mm and 130 mm.
• the second fins have a height of between 2.0 mm and 4.8 mm.
• the second fins have a pitch of between 1.3 mm and 1.8 mm, preferably 1 .4 mm.
• the first internal cavity comprises fins, called first fins, of length between 50 mm and 130 mm.
• the first fins have a height of between 1.0 mm and 1.5 mm.
• the first fins have a pitch of between 0.9 mm and 1.5 mm, preferably 1 .0 mm.
• the first fins and / or the second fins have a width of between 45.0 mm and 70.0 mm.
• the upper plate and / or the lower plate of each heat exchange module has a thickness of between 0.5 mm and 1.5 mm, preferably 1 .0 mm.
• the plurality of thermal modules is disposed inside a housing.
• the housing has a thickness of between 1.0 mm and 2.0 mm, preferably 1.5 mm.
• FIG. 1 is a partially exploded view of a heat exchanger according to the present invention
• FIG. 2 is a sectional view along a longitudinal direction (plane A-A of FIG. 1) of the heat exchanger according to the present invention
• FIGS. 3a and 3b show plates forming a heat exchange module of the heat exchanger according to the present invention
• FIG. 4 is a side view of an alternative embodiment of a housing of the heat exchanger according to the present invention.
• FIG. 5 is a section in a transverse direction (plane similar to plane B-B of FIG. 1) of an alternative embodiment of the heat exchanger according to the present invention.
• FIGS. 6 to 9 are graphs showing the evolution of the thermal efficiency and / or of the losses of the heat exchanger according to the present invention as a function of the dimensional parameters of the fins.
• the identical elements bear the same references. Unless otherwise indicated, they have the same specificities and will not be detailed again.
• FIG. 1 shows a heat exchanger 1, in particular for an air conditioning circuit of a motor vehicle, capable of ensuring a heat exchange between a first fluid, intended to be heated or cooled, and a second fluid, intended to absorb or yield heat with the first fluid.
• the first fluid HP is a high-pressure fluid and high temperature to be cooled by the second fluid and the BP second fluid is a low-pressure, low-temperature fluid for absorbing heat from the first HP fluid.
• the present invention also covers all types of fluids used as a first fluid and a second fluid.
• FIGS 1 and 2 show a first embodiment.
• the heat exchanger 1 comprises a housing 3 comprising a housing body 3a and a cover 3b, intended to be fixed to the housing body 3a.
• the housing body 3a has a plurality of fastening tabs 5 tightened on the lid 3b once the heat exchanger 1 assembled.
• the plurality of latching tabs 5 extend beyond a circumferential edge of the casing body 3a.
• the housing body 3a and the lid 3b can be assembled by soldering, welding, ...
• the housing body 3a is obtained, for example, by a stamping process.
• the casing body 3a is obtained by extrusion, molding, ...
• the attachment tabs 5, the circumferential edge and the bottom of the casing body 3a are integral and form a unit, in that they are made from the same strip.
• the volume delimited by the circumferential edge and the bottom delimit a space which receives heat exchange modules 15 stacked flat in this space.
• the housing 3 has introducer ports for the first HP fluid and the second LP fluid, and discharge ports for the first HP and the second BP fluids.
• the housing body 3a is closed by a bottom through which passes a first inlet port 7 for the first fluid HP and a first outlet port 9 for the second BP fluid.
• the lid 3b also has a second inlet port 11 for the second LP fluid and a second outlet port 13 for the first HP fluid.
• the first inlet orifice 7 and the second outlet orifice 13 of the first fluid HP are sealingly connected to an air conditioning circuit (not shown) providing the supply of the first fluid HP in the heat exchanger 1.
• the second inlet orifice 11 and the first outlet orifice 9 of the second fluid BP are sealingly connected to the air conditioning circuit (not shown) supplying the second fluid BP in the heat exchanger 1.
• the housing 3, and more particularly the housing body 3a, houses a plurality of substantially identical heat exchange modules 15 superimposed in the housing 3 and fixed in the housing 3, for example by brazing.
• an intermediate heat exchange module 15c disposed between the lower heat exchange module 15a and the upper heat exchange module 15b.
• Each heat exchange module 15 is composed of an upper plate 17 and a lower plate 19 assembled together.
• the upper plate 17 and the lower plate 19 are shown in more detail in FIG. 3.
• the upper plate 17 and the lower plate 19 are, for example, metal plates of generally parallelepipedal shape which have a small thickness, especially between 0.5 and 1.5 mm.
• the upper plate 17 and the lower plate 19 therefore comprise, respectively, two small sides 39 and two long sides 40 alternately arranged along a contour 23 of the upper plate 17 and the lower plate 19.
• the upper plate 1 7, respectively the lower plate 1 9, comprises two protrusions 42 having a rounded contour i and comprising first and second connecting portions 27a and 27b arranged at each end.
• the first and second connecting portions 27a and 27b are arranged in the diagonal of the upper plate 17, respectively the bottom plate 19.
• the first embodiment has a heat exchanger 1 having a circuit of the first HP fluid and the second LP fluid in a single direction to define a T-shaped circulation.
• the first fluid HP and the second LP fluid may be flown in two distinct directions in order to define a LT circulation.
• the contour of the upper plate 17, respectively the lower plate 19 is inclined towards the second connecting portion 27b, respectively the first connecting portion 27a, placed opposite. This constitutes a notch whose function is to distribute the fluid in the spaces between the heat exchange modules 15.
• the inclined contours delimit, with the inner wall of the housing body 3a and the lid 3b, an inlet chamber dedicated to one of the fluids, in particular the second fluid BP.
• the existence of the inclined contour allows to release a sufficient volume so that the second inlet port 11 is not obstructed by the upper heat exchange module 15b.
• the upper plate 17 and the lower plate 19 are assembled by defining between them a first internal cavity 21, as shown in FIG.
• the contour 23 of the upper plate 17 and the contour 23 of the lower plate 19 may be raised relative to an outer surface 31 of the upper plate 17, respectively the lower plate 19.
• the contours 23 of the upper plate 17 and the lower plate 19 are then contiguous so as to define the first inner cavity 21.
• only one of the two plates (lower or upper) of the same heat exchange module 15 may comprise a raised contour, thus delimiting the first internal cavity 21.
• the first internal cavity 21 forms a first circulation channel of one of the fluids, in particular the first HP fluid.
• the heat exchanger 1 therefore comprises three first circulation channels.
• the first circulation channels, thus formed are parallel to each other, and have, for example, a height of between 1 mm and 1.5 mm.
• First fins 25 may be disposed in the first inner cavities 21 to improve the heat exchange between the first HP fluid flowing in the first channels and the second BP fluid.
• the first fins 25 take the form of a corrugated metal plate.
• the first fins 25 can be obtained by various processes such as stamping, extrusion, rolling, ...
• the first fins 25 are not shown on the section AA of FIG. 2.
• the heat exchanger 1 is assembled via junction portions 27 on the housing 3 and first and second second connection portions 27a and 27b on the heat exchange modules 15.
• the first and second connection portions 27a and 27b make it possible to assemble the heat exchange modules 15 together by cooperating with first and second connection portions 27a and adjacent 27b associated with a neighboring heat exchange module.
• the junction portions 27 make it possible to assemble the heat exchange modules 15 with the housing 3. More specifically, the bottom of the housing body 3a in contact with the module 15a has at least one junction portion 27. Similarly, the cover 3b in contact with the upper heat exchange module 15b also has at least one junction portion 27.
• each heat exchange module 15 has at least the first connecting portion 27a, respectively the second connecting portion 27b. More specifically, each upper plate 17 and each lower plate 19 comprises at least the first and second connecting portions 27a and 27b respectively placed at each end of the upper plate 17, respectively the lower plate 19, at the level of the protrusion 42 present on the small side 39 of the upper plate 17, respectively the lower plate 19.
• the bottom of the case body 3a and the cover 3b respectively comprise a junction portion 27.
• the junction portions 27 cooperate respectively with the first inlet orifice 7 of the first HP fluid. and the second outlet port 13 of the first HP fluid.
• the upper plate 17 and the lower plate 19 comprise, in turn, the first connecting portion 27a and the second connecting portion 27b.
• the first connection portions 27 a of the heat exchange modules 15 are aligned with one another and with the junction portion 27 of the housing body 3 a.
• the second connection portions 27b of the heat exchange modules 15 are aligned with each other and with the junction portion 27 of the cover 3b.
• the joining portion 27 of the housing body 3a cooperates with the first connecting portion 27a associated with the lower plate 19 of the lower heat exchange module 15a,
• first and second connection portions 27a and 27b of the upper plate 17 of the lower heat exchange module 15a cooperate with the first and second connection portions
• connection portions 27a and 27b of the upper plate 17 of the intermediate heat exchange module 1 5c cooperate with the connecting portions 27a and 27b associated with the lower plate 19 of the upper heat exchange module 15b, and
• the second connecting portion 27b of the upper plate 17 of the upper heat exchange module 15b cooperates with the associated junction portion 27 of the lid 3b.
• first and second connection portions 27a and 27b of the heat exchange modules 15 thus have holes or holes for the passage of the first fluid HP.
• first connecting portions 27a communicate with each other and with the first inlet port 7 of the first fluid HP.
• An input channel of the first HP fluid is thus defined.
• the second connecting portions 27b communicate with each other and with the second outlet 13 of the first fluid HP.
• An output channel of the first HP fluid is thus defined.
• junction portions 27, the first and second connecting portions 27a and 27b cooperate with each other, for example by brazing, waterproof way to prevent any leakage.
• first connecting portions 27a and the second connecting portions 27b of the upper plate 17, respectively the lower plate 19 can be arranged on each side. other of the upper plate 17, respectively the lower plate 19, on a common diagonal of the relevant plate, shown in dashed lines in FIG. 3.
• Other circuits, not shown, are, of course, conceivable in the context of FIG. the present invention.
• first and second connecting portions 27a and 27b in order to improve the flow of the first fluid HP, it is also possible for the first and second connecting portions 27a and 27b to form recesses on the internal surfaces 29 opposite the top plate 17 and the lower plate 19.
• the joining portion 27 of the housing body 3a forms a boss inwardly of the surface of the housing body 3a facing the module of the housing. lower heat exchange 15a.
• the junction portion 27 of the cover 3b forms a boss inwardly of the surface of the lid 3b vis-à-vis the upper heat exchange module 15b.
• the connecting portions 27a and 27b of the heat exchange modules 15 form bosses on the outer surfaces 31 of the upper plates 17 and lower plates 19.
• the bosses formed extend respectively to the connecting portions 27 and the first and second connecting portions 27a or 27b adjacent adjacent.
• the bosses of the junction portions 27, and first and second connecting portions 27a and 27b make it possible to define circulation spaces 33 between one or more modules d consecutive heat exchange 15c and between the lower heat exchange module 1 5a, respectively the upper heat exchange module 15b, and the bottom of the housing body 3a, respectively the lid 3b.
• the circulation spaces 33 thus delimited form second circulation channels of the second fluid BP.
• the second circulation channels are parallel to each other with a height that can be between 2 mm and 4.8 mm.
• the heat exchanger 1 has four second circulation channels. The second circulation channels are thus located above and below the first circulation channels in order to optimize the heat exchange between the first fluid HP and the second fluid BP.
• first and second circulation channels are obtained, here three first circulation channels and four second circulation channels.
• second fins 35 may be obtained by various processes such as stamping, extrusion, rolling, etc. For greater clarity, the second fins 35 are not shown on the drawing. AA cut of Figure 2.
• the second circulation channels are also parallel to the first circulation channels so that the first fluid HP and the second fluid BP flow in two parallel directions.
• the first fluid HP always flows in a direction parallel to and opposite the direction of flow of the second fluid BP.
• the second inlet orifice 11 of the second fluid BP being at the level of the second outlet orifice 13 of the first fluid HP and the first outlet orifice 9 of the second fluid BP being at the first inlet orifice 7 of the first fluid HP
• the first fluid HP and the second fluid BP circulate against the current.
• the countercurrent circulation makes it possible to reduce the temperature differences at the outlet of the heat exchanger 1 and thus to further optimize the performance of the heat exchanger 1.
• the circulation of the first fluid HP and the second LP fluid can be in the same direction, for a co-current flow.
• additional holding portions 37 can be provided on the upper plates 17 and the lower plates 19.
• the additional holding portions 37 are arranged next to the first connecting portions 27a and / or the second connecting portions 27b with the same hollow characteristics on the inner surfaces 29 and bosses on the outer surfaces 31 of the upper plates 17 and lower plates 19 and with a plus size reduced with respect to the first and second connecting portions 27a and 27b.
• the additional support portions 37 have an additional function in that they prohibit any movement of the second fins 35 present in the circulation spaces 33.
• the thermal exchange performance is thus improved by keeping a relatively simple form of the upper plates 17 and the lower plates 19 forming the heat exchange modules 15.
• the heat exchanger 1 differs from the first embodiment previously described in that the housing 3 is formed in the form of two half-housings 3 'and 3 ".
• each half-casing 3 'and 3 "respectively in contact with the lower heat exchange modules 15a and the upper heat exchange modules 15b, comprises a junction portion 27.
• the exchange modules thermal 1 5 remain identical with respect to the first embodiment previously described.
• the two half-housings 3 'and 3 are fixed, for example by soldering, at a junction 41 between the two half-housings 3' and 3" to ensure the sealing of the housing 3.
• Such a heat exchanger 1 is particularly suitable for use within an air conditioning loop for a motor vehicle comprising a gas condenser or cooler, an expansion member, an evaporator and a compressor traversed in this order by a refrigerant fluid.
• the loop The air conditioning system comprises a high pressure branch, starting at the compressor outlet and terminating at the inlet of the expansion member, and a low pressure branch, starting at the outlet of the expansion member and terminating at the inlet of the compressor.
• the heat exchanger 1 according to the invention is used as an internal heat exchanger, that is to say a heat exchanger traversed by the high-pressure refrigerant fluid and high temperature, circulating in the first channels, and traversed by the same refrigerant fluid at low pressure and low temperature, flowing in the second channels.
• Figure 5 is a sectional view in a transverse direction, in a plane similar to the plane BB of Figure 1, a heat exchanger 1 according to the present invention.
• the heat exchanger 1 does not include a housing 3 that houses a plurality of heat exchange modules 15.
• the heat exchanger 1 comprises four modules. heat exchange 1 5 superimposed.
• the first inner cavities 21 and the circulation spaces 33 are constituted by interstitial zones between upper plates 17 and consecutive lower plates 19.
• the upper plates 17 and the lower plates 19 comprise recesses oriented towards the first inner cavities 21 in order to define the circulation spaces 33.
• the heat exchanger 1 has different dimensional sizes which will now be detailed.
• the heat exchanger 1 has a height H 1 H x defined as being the distance between the lower plate 19 of the lower heat exchange module 15a and the upper plate 17 of the upper heat exchange module 15b.
• the heat exchanger 1 has a width W i H x defined as being the width of the bottom plate 19 or the upper plate 17 of the upper heat exchange modules 15a, 15b or 15c.
• the first fins 25 disposed in the first inner cavities 21 for the circulation of the first fluid HP are of defined height HJFHP being the distance between the lower plate 19 and the upper plate 17 of the heat exchange module 15a, 15b or 15c, taken at level of the first interior cavity 21.
• the first fins 25 have a width WJFHP defined as the extension width of the first fins 25 in the first inner cavity 21.
• WJFHP defined as the extension width of the first fins 25 in the first inner cavity 21.
• P HP defined as the half-distance between two successive peaks of the corrugations forming the first fins 25.
• the second fins 35 disposed in the circulation spaces 33 for the circulation of the second LP fluid are of height HJFBP defined being the distance between the lower plate 19 and the upper plate 17 of two successive heat exchange modules 15a, 15b or 15c taken at the circulation space 33.
• the second fins 35 have a width WJFBP defined as the extension width of the second fins 35 in the circulation space 33.
• WJFBP width of the second fins 35 in the circulation space 33.
• P_BP defined as the half distance between two successive peaks of the undulations forming the second fins 35.
• the first fins 25 and the second fins 35 are made from aluminum or aluminum alloy.
• the first fins 25 and second fins 35 have a thickness of between 0.07 mm and 0.15 mm, preferably 0.10 mm.
• the width WJFHP of the first fins 25 and the width W IFBP of the second fins 35 are between 45.0 mm and 70.0 mm.
• the height HJFHP of the first fins 25 is between 1.0 mm and 1.5 mm and the height HJFBP of the second fins 35 is between 2.0 mm and 4.8 mm.
• the pitch PJFHP of the first fins 25 is between 0.9 mm and 1.5 mm, preferably 1 .0 mm
• the pitch PJFBP of the second fins 35 is between 1.3 mm and 1.8 mm, preferably 1 mm. .4 mm.
• the upper plate 17 and the lower plate 19 of each heat exchange module 15 have a thickness of between 0.5 mm and 1.5 mm, preferably 1 .0 mm.
• the heat exchanger 1 comprises a housing 3, in order to promote the resistance of the heat exchanger 1, the housing body 3a and the cover 3b, or the two half-housings 3 'and 3 ", have a thickness between 1.0 mm and 2.0 mm, preferably 1 .5 mm.
• FIG. 6 shows the evolution of the heat efficiency of the heat exchanger 1 as a function of a length LJFHP of the first fins 25 and / or a length LJFBP of the second fins 35.
• the heat efficiency of the heat exchanger 1 is set between 35% and 62% in order to meet the requirements related to the use of various refrigerant fluids, especially subcritical coolants such as the refrigerants known under the name R134A or 1234yf.
• the width W JF HP of the first fins 25 and the width WJFBP of the second fins 35 substantially equal to 55 mm
• the height HJFHP of the first fins 25 substantially equal to 1 .2 mm
• the height HJFBP of the second fins 35 substantially equal to 3.6 mm
• the pitch PJFHP of the first fins 25 substantially equal to 1 .0 mm
• the pitch PJFBP of the second fins 35 substantially equal to 1 .4 mm. According to a particular embodiment, the number of heat exchange modules 15 of the heat exchanger 1 is equal to seven.
• FIG. 7 shows the evolution of the thermal efficiency, represented in solid lines, and shows the evolution of the loss of charge, represented in dotted lines, of the heat exchanger 1 as a function of the pitch PJFBP of the second fins 35 .
• the thermal efficiency of the heat exchanger 1 is set between 55% and 62% in order to meet the increased requirements associated with the use of certain refrigerant fluids, especially the known subcritical refrigerant fluid. under the name 1234yf.
• the maximum pressure drop of the heat exchanger 1 is set to 100%.
• the length LJFHP of the first fins 25 and / or the length LJFBP of the second fins 35 substantially equal to 130 mm
• the width W JF HP of the first fins 25 and the width WJFBP of the second fins 35 substantially equal to 55 mm
• the height HJFHP of the first fins 25 substantially equal to 1 .2 mm
• the height HJFBP of the second fins 35 substantially equal to 3.6 mm
• the pitch PJFHP of the first fins 25 substantially equal to 1 .0 mm.
• the number of exchange modules The heat exchanger 15 of the heat exchanger 1 is equal to seven.
• FIG. 8 shows the evolution of the thermal efficiency, represented in solid lines, and presents the evolution of the loss of charge, represented in dotted lines, of the heat exchanger 1 as a function of the height HJFBP of the second fins 35 .
• the heat efficiency of the heat exchanger 1 is set between 55% and 62% in order to meet the increased requirements related to the use of certain refrigerant fluids, notably the known subcritical refrigerant fluid. under the name 1234yf.
• the maximum pressure drop of the heat exchanger 1 is set to 100%.
• the length LJFHP of the first fins 25 and / or the length L IFBP of the second fins 35 substantially equal to 130 mm
• the width W JF HP of the first fins 25 and the width WJFBP of the second fins 35 substantially equal to 55 mm
• the height HJFHP of the first fins 25 substantially equal to 1 .2 mm
• the pitch PJFHP of the first fins 25 substantially equal to 1 .0 mm.
• the number of heat exchange modules 15 of the heat exchanger 1 is equal to seven.
• Figure 9 shows the evolution of the thermal efficiency, shown in solid lines, and presents the evolution of the loss of charge, represented in dashed line, of the heat exchanger 1 as a function of the width WJFBP of the second fins 35.
• the thermal efficiency of the heat exchanger 1 is set between 60% and 62% in order to meet the increased requirements associated with the use of certain refrigerant fluids, especially the known subcritical refrigerant fluid. under the name 1 234yf.
• the maximum pressure drop of the heat exchanger 1 is set to 100%.
• the length LJFHP of the first fins 25 and / or the length LJFBP of the second fins 35 substantially equal to 130 mm
• the height HJFHP of the first fins 25 substantially equal to 1 .2 mm
• the height HJFBP of the second fins 35 substantially equal to 3.6 mm
• the pitch PJFHP of the first fins 25 substantially equal to 1 .0 mm
• the pitch PJFBP of the second fins 35 substantially equal to 1 .4 mm.
• the number of heat exchange modules 15 of the heat exchanger 1 is equal to seven.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

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• 2010
  • 2010-01-29 FR FR1000350A patent/FR2955928B1/fr active Active
• 2011
  • 2011-01-18 JP JP2012550389A patent/JP5878480B2/ja active Active
  • 2011-01-18 WO PCT/EP2011/050559 patent/WO2011092076A1/fr active Application Filing
  • 2011-01-18 EP EP11700349A patent/EP2529172A1/de not_active Withdrawn

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