EP2756252A1 - Dispositif de transport de chaleur à pompage capillaire - Google Patents
Dispositif de transport de chaleur à pompage capillaireInfo
- Publication number
- EP2756252A1 EP2756252A1 EP12766395.3A EP12766395A EP2756252A1 EP 2756252 A1 EP2756252 A1 EP 2756252A1 EP 12766395 A EP12766395 A EP 12766395A EP 2756252 A1 EP2756252 A1 EP 2756252A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- reservoir
- evaporator
- inlet
- fluid
- outlet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005086 pumping Methods 0.000 title claims abstract description 17
- 239000012530 fluid Substances 0.000 claims abstract description 39
- 239000007788 liquid Substances 0.000 claims abstract description 28
- 238000004891 communication Methods 0.000 claims abstract description 21
- 239000007791 liquid phase Substances 0.000 claims abstract description 16
- 239000012071 phase Substances 0.000 claims abstract description 14
- 230000005484 gravity Effects 0.000 claims description 5
- 229910001220 stainless steel Inorganic materials 0.000 claims description 4
- 239000010935 stainless steel Substances 0.000 claims description 4
- 239000012808 vapor phase Substances 0.000 claims description 4
- 238000005188 flotation Methods 0.000 claims 1
- 230000000694 effects Effects 0.000 description 7
- 239000007789 gas Substances 0.000 description 7
- 238000002156 mixing Methods 0.000 description 5
- 238000000926 separation method Methods 0.000 description 5
- 238000001816 cooling Methods 0.000 description 4
- 238000011144 upstream manufacturing Methods 0.000 description 4
- OKKJLVBELUTLKV-UHFFFAOYSA-N Methanol Chemical compound OC OKKJLVBELUTLKV-UHFFFAOYSA-N 0.000 description 3
- 238000001035 drying Methods 0.000 description 3
- 238000010438 heat treatment Methods 0.000 description 3
- QGZKDVFQNNGYKY-UHFFFAOYSA-N Ammonia Chemical compound N QGZKDVFQNNGYKY-UHFFFAOYSA-N 0.000 description 2
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 238000003825 pressing Methods 0.000 description 2
- 229910021529 ammonia Inorganic materials 0.000 description 1
- 230000002051 biphasic effect Effects 0.000 description 1
- 230000000903 blocking effect Effects 0.000 description 1
- 230000005587 bubbling Effects 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 238000007872 degassing Methods 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 239000013529 heat transfer fluid Substances 0.000 description 1
- 239000011261 inert gas Substances 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 210000000056 organ Anatomy 0.000 description 1
- 239000012782 phase change material Substances 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000010992 reflux Methods 0.000 description 1
- 230000000284 resting effect Effects 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
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
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/04—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure
- F28D15/043—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with tubes having a capillary structure forming loops, e.g. capillary pumped loops
-
- 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
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/06—Control arrangements therefor
Definitions
- the present invention relates to capillary pumping heat transport devices, in particular passive biphasic fluid loop devices.
- the subject of the invention is a capillary pumping thermal transfer device adapted to extract heat from a hot source and to restore this heat to a cold source by means of a two-phase working fluid contained in a enclosed general circuit, comprising:
- At least one evaporator having an inlet and an outlet, and a microporous mass adapted to provide capillary pumping of fluid in the liquid phase
- At least one condenser having an inlet and an outlet, a reservoir having an interior volume and at least one inlet and / or outlet,
- a first communication circuit for essentially vapor phase fluid, connecting the outlet of the evaporator to the inlet of the condenser
- a second communication circuit for fluid essentially in the liquid phase, connecting the condenser outlet to the tank and to the inlet of the evaporator, characterized in that it comprises an anti-return member arranged between the interior volume of the reservoir and the microporous mass of the evaporator, and arranged to prevent the liquid present in the evaporator does not move towards the interior volume of the tank, the device being mainly subjected to gravity, the anti-return member comprising a float floated by a floatation thrust towards a range in the closed state.
- the float is able to let gas bubbles pass and thus avoid the formation of a gas cap; in addition, the anti-return member is simple and reliable and moreover it can pass steam bubbles or gas.
- the float has a density that is lower than the density of the fluid in the liquid phase, and between 60% and 90% of the fluid density in the liquid phase; whereby the anti-return member does not interfere with capillary pumping;
- the float is made of stainless steel; so that its durability is very good;
- the anti-return member is formed in the second fluid communication circuit; so that it can be independent of the tank and the evaporator;
- the anti-return member is formed in the lower zone of the reservoir; so that it can be combined with the tank;
- the anti-return member is formed in the upper zone of the evaporator; so that it can be combined with the evaporator;
- the fluid communication circuit is a tubular conduit; so that its cost is moderate;
- the inlet / outlet orifice is arranged in the lower zone the reservoir, preferably the lower side zone of the reservoir;
- the second fluid communication circuit may be in the form of a single pipe with a 'T' or two independent pipes;
- the reservoir comprises an inlet jet deflector in the vicinity of the inlet orifice; whereby a mixing effect due to the inlet jet can be avoided;
- the reservoir comprises a plurality of distinct volumes remaining in fluid communication; whereby the mixing of the volume of liquid contained in the reservoir is limited;
- the reservoir comprises a plurality of internal walls forming compartments adapted to separate said several distinct volumes;
- the plurality of internal walls forms a compartment structure in the form of a honeycomb; so that the cost-effectiveness ratio is optimized;
- the heat transfer device is preferably without a mechanical pump; whereby its reliability is increased;
- the device further comprises an energy supply element at the reservoir to control the pressurization of the loop during startup; so that the start of the loop can be made reliable.
- FIG. 1 is a general view of a device according to one embodiment of the invention.
- FIG. 2 is a variant of the device of FIG.
- FIG. 3 is another variant of the device of FIG.
- FIGS. 4a and 4b show a nonreturn valve for a device according to FIGS. 1-3,
- FIG. 5 is a detailed view of the anti ⁇ return member when located at the base of the tank
- FIG. 6 is a sectional view of the anti ⁇ return member
- FIGS. 7a and 7b show variants of the device of FIG. 1, with several evaporators.
- FIG. 1 shows a capillary pumping heat transport device with a two-phase fluid loop.
- the device comprises an evaporator 1, having an inlet 1a and an outlet 1b, and a microporous mass 10 adapted to provide capillary pumping.
- the microporous mass 10 surrounds a blind central longitudinal recess 15 in communication with the inlet 1a to receive working fluid 9 in the liquid state from a reservoir 3.
- the evaporator 1 is thermally coupled to a hot source 11, such as an assembly comprising electronic power components or any other element generating heat, for example by joule effect, or by any other process.
- a hot source 11 such as an assembly comprising electronic power components or any other element generating heat, for example by joule effect, or by any other process.
- the evacuated vapor is replaced by the liquid sucked by the microporous mass 10 from the aforementioned central recess 15; it is the phenomenon of capillary pumping well known in itself.
- heat is transferred by the fluid in the vapor phase to a cold source 12, which causes a cooling of the vapor fluid and its phase change to the liquid phase, ie its condensation.
- the temperature of the working fluid 9 is lowered below its equilibrium liquid-vapor temperature, which is also called sub-cooling ('sub-cooling' in English) so that the fluid can not do not iron in a vapor state without a significant amount of heat
- the vapor pressure pushes the liquid towards the outlet 2b of the condenser 2 which opens onto a second communication circuit 5, furthermore connected to the tank 3.
- the reservoir has at least one inlet and / or outlet port 31, here in this case in FIG. 1 an inlet orifice 31a and a separate outlet orifice 31b, and the reservoir 3 has an interior volume 30, filled with heat transfer fluid 9.
- the working fluid 9 may be for example ammonia or any other suitable fluid, but it is preferable to choose methanol.
- the working fluid 9 is two-phase and is partly in liquid phase 9a and partly in vapor phase 9b. In an environment where gravity is exerted (vertical along Z), the gas phase portion 9b is above the liquid phase portion 9a and a separation surface 19 separates the two phases.
- this pressure corresponds to the saturation pressure of the fluid at the temperature prevailing at the separation surface 19.
- the temperature of the liquid is generally lower than the temperature prevailing at the separation surface 19.
- the first and second fluid communication circuits 4,5 are preferably tubular conduits, but could be other types of fluid conduits or communication channels.
- the second fluid communication circuit 5 may be in the form of two separate independent pipes 5a, 5b (see Fig 1) or a single pipe with a 'T' connection 5c (see Fig 2).
- the second fluid communication circuit 5 connects the outlet of the condenser 2b to the inlet of the evaporator 1a, either indirectly via the reservoir (in the case of two independent conduits) or directly (case or single driving with 'T').
- the device comprises a non-return member 6, arranged between the internal volume 30 of the reservoir and the microporous mass 10 of the evaporator 1, to prevent the liquid present in the evaporator from moving towards the volume interior 30 of the tank.
- This non-return member 6 makes it possible to prevent a return of liquid from the evaporator towards the reservoir. Even a limited return of liquid from the evaporator towards the reservoir causes local drying of the microporous mass which can lead to defusing the pumping of the two-phase loop, which is prevented by said non-return member 6. This phenomenon is even more important than the starting power is high (several kW and / or several tens of Watts per cm 2 ) .
- the non-return member 6 thus makes it possible to increase the performance of the system at start-up .
- the position of said non-return member 6 may be selected from several locations of particular interest depending on the purpose and the optimizations pursued.
- the non-return member 6 is positioned on the pipe 5b connecting the reservoir to the evaporator 1. In this way, one non-return member 6 can be inserted in a two-phase loop where the evaporator and the reservoir are given organs that are difficult to modify.
- said non-return member 6 can be positioned, as illustrated in FIG. 2, adjacent to the evaporator 1, so that said non-return member 6 can be combined with one evaporator, which allows the optimize the overall size of the system.
- said non-return member 6 can be positioned, as illustrated in FIG. 3, adjacent to the reservoir, so that said non-return member 6 can be combined with the reservoir as will be detailed later. which optimizes the size of the system.
- this non-return member 6 may comprise a float 60 whose density is slightly less than the fluid density in the liquid phase, the float abutting on a range to close the passage of liquid, as will be specified more far .
- this non-return member 6 can also take the more conventional form of a non-return valve (not shown in the figures), with a valve, a valve seat and an elastic return tending to push said valve towards the seat of valve.
- the elastic restoring force must be moderated so as not to upset the aforementioned capillary pumping force.
- a float member 60 is arranged inside a hollow body 63 in which the float 60 can to move at least in a so-called longitudinal direction.
- the longitudinal direction here coincides with the direction Z in which the buoyancy and the gravity are exerted.
- the hollow body and the float are symmetrical about this Z axis, but it could be otherwise.
- the float comprises an annular support surface 67 which bears on a corresponding annular bearing surface 66 which forms a shoulder directed radially inwards in the hollow body 63.
- bubbles of vapor or non-condensable gas are in said liquid in the downstream part 65, they can escape in the opposite direction (from downstream to upstream) which allows avoid blocking the supply of 1 evaporator fresh liquid: the float is thus able to let gas bubbles pass and thus prevent the formation of a gas cap, this function can also be called degassing function.
- the float has a density lower than the fluid density in the liquid phase, and between 60% and 90% of the fluid density in the liquid phase (at a maximum temperature of about 100 ° C for example).
- the result of the weight and thrust of Archimedes gives a thrust force P oriented upwards.
- This thrust P must however be moderate to be less than the suction effect of the aforementioned capillary pumping.
- an upwardly pressing pressure F has the effect of pressing the float 60 against the bearing surface 66 and thus closing the passage of liquid. Therefore, any reflux of liquid towards the interior space of the tank is avoided.
- the non-return member 6 is arranged at the base of the reservoir, at the outlet orifice 31b (see FIGS. 3 and 5).
- the body 63 comprises a collar 68 which is secured to the base 37 of the tank by means of known fasteners.
- the base 37 at the orifice 31b can serve directly as a closing surface 66.
- the float can be made of stainless steel so that its durability is very good.
- the float 60 may be formed as two half-shells 61, 62 welded together at a diameter by means of a weld 68; the two half-shells 61, 62 then define an interior volume 89 filled with air or preferably inert gas.
- the thickness of the wall of the two half-shells 61, 62 as well as the size of the inner volume 89 are chosen to obtain the desired density for the complete float 60.
- the reservoir may comprise an inlet jet deflector 8 in the vicinity of the inlet orifice 31a or the inlet / outlet orifice 31 according to the configuration of the second conduit.
- This inlet jet deflector 8 prevents a rapid arrival of liquid in the tank creates a bubbling or a current promoting the mixing of the liquid. It may be in the form of a downward U-shaped profile, or a bell or other shape creating a sufficient deflection of the path of the inlet jet.
- the compartment structure 71 may have vertical walls 7, that is to say oriented in the direction of gravity. It should be noted, however, that the walls may equally well be slightly or substantially inclined, as illustrated for example in FIG. 7a.
- the reservoir may have any shape, and in particular parallelepipedal or cylindrical.
- the compartment structure may be formed of stainless steel.
- said plurality of separate volumes communicate through passages of small section, preferably less than 1/10 of the largest section of the tank.
- the compartment structure may comprise a phase change material imparting a thermal inertia to said structure which contributes to limiting the sudden variations in temperature.
- Figures 7a and 7b show that it is possible in the context of the present invention to have several evaporators 1 in parallel with each other to increase the calorie evacuation capacity and / or to place the evaporators closer to the sources of heat.
- each evaporator has an anti-return member 6 in its particular liquid supply circuit, whereas according to the configuration of FIG. 7b, the anti-return member 6 is placed in the common branch 5d in upstream of the distribution 5e, 5f to the evaporators, which allows to commonize the non-return member 6 and thus optimize the cost of a multi-evaporator system.
- the device may further comprise a power supply element 36, for example a heating element or pressurizing, located at the reservoir to control the pressurization of the loop during startup.
- a control system 'Ctrl' 38 controls, in the case of a heating element, the contribution of calories on this heating element 36, as a function of temperature information and / or pressure information delivered by sensors (not shown), and this to ensure the start of the two-phase loop.
- this control system 'Ctrl' can also prepare the two-phase loop for an imminent and important arrival of calories on one evaporator, which makes it possible to anticipate the reaction of the two-phase loop with respect to the need for heat dissipation.
- the design of the loop can be optimized for large quantities of heat to be evacuated.
- the device is devoid of any mechanical pump although the invention does not exclude the presence of a mechanical booster pump.
Landscapes
- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Filling Or Discharging Of Gas Storage Vessels (AREA)
- Jet Pumps And Other Pumps (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR1158203A FR2979982B1 (fr) | 2011-09-14 | 2011-09-14 | Dispositif de transport de chaleur a pompage capillaire |
PCT/EP2012/067753 WO2013037785A1 (fr) | 2011-09-14 | 2012-09-12 | Dispositif de transport de chaleur à pompage capillaire |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2756252A1 true EP2756252A1 (fr) | 2014-07-23 |
EP2756252B1 EP2756252B1 (fr) | 2017-10-11 |
Family
ID=46940453
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12766395.3A Active EP2756252B1 (fr) | 2011-09-14 | 2012-09-12 | Dispositif de transport de chaleur à pompage capillaire |
Country Status (7)
Country | Link |
---|---|
US (1) | US9766016B2 (fr) |
EP (1) | EP2756252B1 (fr) |
JP (1) | JP6163491B2 (fr) |
CN (1) | CN104094073B (fr) |
ES (1) | ES2645370T3 (fr) |
FR (1) | FR2979982B1 (fr) |
WO (1) | WO2013037785A1 (fr) |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20080283221A1 (en) * | 2007-05-15 | 2008-11-20 | Christian Blicher Terp | Direct Air Contact Liquid Cooling System Heat Exchanger Assembly |
FR2979981B1 (fr) * | 2011-09-14 | 2016-09-09 | Euro Heat Pipes | Dispositif de transport de chaleur a pompage capillaire |
FR3003725B1 (fr) * | 2013-03-22 | 2015-04-17 | Alstom Transport Sa | Convertisseur de puissance electrique pour un vehicule ferroviaire. |
FR3006431B1 (fr) * | 2013-05-29 | 2015-06-05 | Euro Heat Pipes | Dispositif de transport de chaleur a fluide diphasique |
US20150168079A1 (en) * | 2013-12-17 | 2015-06-18 | General Electric Company | System and method for transferring heat between two units |
DE102015107473A1 (de) | 2015-05-12 | 2016-11-17 | Benteler Automobiltechnik Gmbh | Kraftfahrzeug-Wärmeübertragersystem |
CN105115329A (zh) * | 2015-08-14 | 2015-12-02 | 北京空间飞行器总体设计部 | 一种适应于小空间、多点热源的高效散热系统 |
JP6579275B2 (ja) * | 2016-09-09 | 2019-09-25 | 株式会社デンソー | 機器温調装置 |
ES2910103T3 (es) * | 2017-03-12 | 2022-05-11 | Zuta Core Ltd | Sistemas y procedimientos de refrigeración |
CN107575272A (zh) * | 2017-08-23 | 2018-01-12 | 山西德泓利科技有限责任公司 | 一种基于多毛细双相控蒸发器的orc发电系统 |
CN113304375B (zh) * | 2021-05-12 | 2023-06-27 | 湖南万脉医疗科技有限公司 | 一种新型呼吸机管路及其呼吸机 |
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US20080115843A1 (en) * | 2006-11-20 | 2008-05-22 | Chi-Chang Wang | Negative check valve of a pneumatic transfer pipe |
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JPS4827346A (fr) * | 1971-08-12 | 1973-04-11 | ||
DE2235792A1 (de) | 1972-07-21 | 1974-01-31 | Dornier System Gmbh | Vorrichtung zur uebertragung von waermeenergie |
US4061131A (en) * | 1975-11-24 | 1977-12-06 | Acme Engineering And Manufacturing Corporation | Heat transfer system particularly applicable to solar heating installations |
JPH0230439B2 (ja) * | 1985-01-30 | 1990-07-06 | Matsushita Electric Ind Co Ltd | Ruupushikihiitopaipu |
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WO2007146083A2 (fr) * | 2006-06-06 | 2007-12-21 | Albert Montague | Clapet anti-retour |
FR2919923B1 (fr) * | 2007-08-08 | 2009-10-30 | Astrium Sas Soc Par Actions Si | Dispositif passif a micro boucle fluide a pompage capillaire |
US8196395B2 (en) * | 2009-06-29 | 2012-06-12 | Lightsail Energy, Inc. | Compressed air energy storage system utilizing two-phase flow to facilitate heat exchange |
FR2949642B1 (fr) * | 2009-08-27 | 2012-05-04 | Alstom Transport Sa | Convertisseur de puissance electrique pour un vehicule ferroviaire |
-
2011
- 2011-09-14 FR FR1158203A patent/FR2979982B1/fr active Active
-
2012
- 2012-09-12 ES ES12766395.3T patent/ES2645370T3/es active Active
- 2012-09-12 EP EP12766395.3A patent/EP2756252B1/fr active Active
- 2012-09-12 WO PCT/EP2012/067753 patent/WO2013037785A1/fr active Application Filing
- 2012-09-12 CN CN201280055586.0A patent/CN104094073B/zh active Active
- 2012-09-12 JP JP2014530189A patent/JP6163491B2/ja not_active Expired - Fee Related
- 2012-09-12 US US14/344,883 patent/US9766016B2/en active Active
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS60205187A (ja) * | 1984-03-28 | 1985-10-16 | Showa Alum Corp | 熱輸送システム |
US5725018A (en) * | 1994-09-16 | 1998-03-10 | Paczonay; Joseph R. | Gravity check valve |
US20080115843A1 (en) * | 2006-11-20 | 2008-05-22 | Chi-Chang Wang | Negative check valve of a pneumatic transfer pipe |
Non-Patent Citations (1)
Title |
---|
See also references of WO2013037785A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN104094073B (zh) | 2020-03-10 |
US20150114605A1 (en) | 2015-04-30 |
WO2013037785A1 (fr) | 2013-03-21 |
US9766016B2 (en) | 2017-09-19 |
FR2979982B1 (fr) | 2016-09-09 |
FR2979982A1 (fr) | 2013-03-15 |
CN104094073A (zh) | 2014-10-08 |
EP2756252B1 (fr) | 2017-10-11 |
JP6163491B2 (ja) | 2017-07-12 |
JP2014526670A (ja) | 2014-10-06 |
ES2645370T3 (es) | 2017-12-05 |
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