EP3553445B1 - Verbessertes wärmerohr mit kapillarstrukturen mit wiedereintrittsrillen - Google Patents

Verbessertes wärmerohr mit kapillarstrukturen mit wiedereintrittsrillen Download PDF

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Publication number
EP3553445B1
EP3553445B1 EP19168586.6A EP19168586A EP3553445B1 EP 3553445 B1 EP3553445 B1 EP 3553445B1 EP 19168586 A EP19168586 A EP 19168586A EP 3553445 B1 EP3553445 B1 EP 3553445B1
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EP
European Patent Office
Prior art keywords
plates
heat pipe
channel
intermediate plate
heat
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EP19168586.6A
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English (en)
French (fr)
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EP3553445A1 (de
EP3553445B8 (de
Inventor
Jean-Antoine Gruss
Bénédicte CHAMPEL
Mathieu Mariotto
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Airbus Defence and Space SAS
Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
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Commissariat a lEnergie Atomique CEA
Commissariat a lEnergie Atomique et aux Energies Alternatives CEA
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Publication of EP3553445B1 publication Critical patent/EP3553445B1/de
Publication of EP3553445B8 publication Critical patent/EP3553445B8/de
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    • 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
    • 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
    • F28D15/0233—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 the conduits having a particular shape, e.g. non-circular cross-section, annular

Definitions

  • the present invention relates to an improved functioning reentrant groove capillary pumped heat pipe.
  • the invention relates to a capillary pumped heat pipe as defined by the preamble of claim 1, and as disclosed by FR 2 776 763 .
  • the invention belongs to the field of heat exchange devices, in particular heat pipes, more particularly capillary pumped heat pipes.
  • a heat pipe comprises a hermetically sealed enclosure, a working fluid and a capillary network. During manufacture, all the air present in the heat pipe is evacuated and a quantity of liquid is introduced which makes it possible to saturate the capillary network. An equilibrium is then established between the liquid phase and the vapor phase.
  • the liquid Under the effect of a hot source applied to one of the ends, designated the evaporator, the liquid vaporizes by inducing a slight overpressure which causes the movement of the vapor towards the second end, designated the condenser.
  • the condenser In the condenser, the vapor condenses and returns to the liquid phase.
  • the condensed fluid circulates in the capillary network and returns to the evaporator under the effect of capillary forces.
  • the return of the liquid fluid from the condenser zone to the evaporator zone is obtained by capillary pumping.
  • Grooved heat pipes work on the principle of capillary pumping. They have a tube, in which the inner surface has longitudinal or slightly spiral-shaped grooves. Grooved heat pipes have a vapor core and a capillary network in which the liquid circulates. Due to a variation in curvature of the vapor-liquid interface between the condenser zone and the evaporator zone, a pressure gradient appears in the liquid, which leads to a variation in capillary pressure. The smaller the width of the grooves, the greater the capillary pumping effect.
  • the maximum power that can be transported by grooved heat pipes is generally fixed by the capillary limit, the driving term of which is the capillary pressure, and the term essentially limiting the loss of liquid pressure in the grooves.
  • Heat pipes with reentrant grooves are particular examples of heat pipes with grooves, in which the grooves have a narrow window with respect to the rest of the groove, which makes it possible to increase the capillary pumping effect while limiting the pressure drops.
  • These heat pipes are used mainly in the space field, for example for thermal regulation in satellites and / or spacecraft.
  • Another technique uses mechanical machining, with this technique also the depth to width ratio is not appreciably greater than 1. In addition, this technique has a relatively high cost price and is not suitable for manufacturing on average and large series.
  • Another technique uses chemical etching. But it does not make it possible to have a significant depth to width ratio either.
  • the document US 7 051 793 describes a heat pipe comprising one or more zones of circulation of the fluid in vapor form and on either side of these zones of the porous zones of circulation of the liquid, these capillary zones extending over the entire heat pipe.
  • the heat pipe is made by stacking plates.
  • the capillary zones are obtained by stacking plates comprising windows, the windows having orthogonal directions from one plate to another.
  • the pumping effect is not optimal. In addition, there is a significant pressure drop. This heat pipe spreads the heat flow across the width of the heat pipe and is not optimized for transporting the heat flow along its length.
  • a heat pipe with reentrant grooves comprising a stack of plates secured together in a hermetic manner.
  • the end plates form closure plates and the spacer plates are structured such that the stack of spacer plates defines reentrant grooves extending the entire length of the heat pipe channel.
  • the heat pipe comprises at least three intermediate plates, two first plates each having a central window delimiting the steam channel and two side windows, on either side of the central window, and delimiting the grooves. , and a second plate disposed between the two first plates and forming a spacer.
  • the thickness of the spacer is used to define the width of the entry end.
  • the depth of the grooves is fixed by the transverse dimension of the side windows and the width of the grooves is fixed by the thickness of the first two plates and the thickness of the second plate. It is thus easy to fix the dimensions of the grooves reentrants and to make such grooves. It is then possible to choose, on the one hand, the dimensions of the exchange zone to optimize the pumping effect, and on the other hand the dimensions of the grooves to limit the pressure drops.
  • the grooves are delimited by stacked plates.
  • the depth and the width of the grooves are obtained separately, so the limitations on the depth to width ratio do not arise, which arise for example in the case of production by extrusion or chemical etching.
  • the heat pipe according to the invention can comprise grooves of variable section between the vaporizer zone and the condenser zone.
  • the present invention therefore relates to a capillary pumped heat pipe with reentrant grooves extending at least along a first longitudinal direction, comprising a first longitudinal end intended to be heated and a second longitudinal end intended to be cooled, an enclosure sealed extending between the first end and the second end, the enclosure comprising a stack of plates along a second direction, said stack comprising two closure plates, at least one module of at least two intermediate plates between the closure plates.
  • the intermediate plates comprise at least a first intermediate plate comprising at least one central window, the edges of which partly define a vapor channel extending along the first direction, in which the vapor is intended to circulate, and on each side of the central window (in a third direction orthogonal to the first and second directions, a structure whose edges partially define a liquid channel, at least one other intermediate plate comprising at least one window whose edges partially define the vapor channel.
  • the heat pipe comprising also at least two exchange zones delimited between the first intermediate plate and the other intermediate plate, connecting the vapor channel and the liquid channel.
  • the other intermediate plate is a first intermediate plate
  • the structures are recesses made in at least one of the faces of said first intermediate plates, in the stack, the recesses are placed opposite each other, and the areas of 'exchange are delimited by two edges of two recesses of the first two intermediate plates facing.
  • the first intermediate plates may have recesses in their two faces.
  • a second intermediate plate is interposed between two first intermediate plates at the level of the outer edges of the first intermediate plates, the thickness of which defines the dimension in the direction of the stacking of the exchange zones.
  • the recesses can advantageously comprise a bottom and at least one edge connecting the bottom to the exchange zone, said edge being inclined away from the steam channel or said edge connecting to said bottom by a connection fillet.
  • the other plate is a third intermediate plate, the window of which has the same section as the central window of the first intermediate plate, so that two of its side edges in the third direction delimit with the first plate interlayer of the exchange zones.
  • a second intermediate plate may be interposed between the first intermediate plate and the third intermediate plate at the level of the outer edges of said first and third intermediate plates, the thickness of which defines the dimension in the direction of the stacking of the exchange zones.
  • the other intermediate plate is a first intermediate plate
  • the structures are windows.
  • the heat pipe comprises a second intermediate plate interposed between the two first intermediate plates at the level of the outer edges of the first intermediate plates, the thickness of which defines the dimension in the direction of the stacking of the exchange zones, and the heat pipe comprises a third intermediate plate, the window of which has the same section as the central windows of the first intermediate plates, in contact with one of the first intermediate plates and closing the side windows on either side of the central window in the second direction.
  • the reentrant-groove capillary pumped heat pipe may have n modules on top of each other, n being an integer> 1, defining a single vapor channel and n liquid channels on each side of the liquid channel and n exchange zones, each connecting the vapor channel with a liquid channel.
  • the structures can advantageously have a trapezoidal shape in a plane orthogonal to the second direction.
  • the central windows of the intermediate plates may include an upright extending in the first direction so that the vapor channel has a wall extending over the entire height of the stack and in the first direction.
  • the window it comprises may include at least one transverse post extending in the third direction.
  • the reentrant-grooved capillary pumped heat pipe may include several vapor channels, each connected to liquid channels by exchange zones.
  • At least one of the end plates may have a surface greater than that of the intermediate plates in a direction transverse to the stack so as to form thermal diffusers.
  • the heat pipe comprises heat exchange means at the first end and / or second end.
  • the heat exchange means at the second end may comprise one or more fins in thermal contact with at least one of the closure plates and / or a fluidic circuit in thermal contact with at least one of the closure plates, said circuit being formed by a plate structured so as to delimit the channels, said channels being closed by said closure plate and an additional closure plate, the heat exchange means also comprising means for supplying said fluidic circuit with heat transfer fluid.
  • the present invention also relates to a heat exchange system comprising several heat pipes according to the invention, in which the heat pipes are arranged in several planes, the heat pipes of two successive planes crossing each other and in which the heat pipes of two successive planes share a same end plate.
  • At least one heat pipe of one layer is advantageously connected hydraulically to at least one heat pipe of the same layer.
  • the heat exchange system can advantageously include a single-phase or two-phase heat exchange circuit.
  • the plates have an aluminum alloy at the core and on its outer faces an eutectic aluminum alloy with a lower melting point than that of the core aluminum alloy and the connection is obtained by eutectic brazing.
  • the longitudinal direction is that given by the X axis.
  • the heat pipe C1 comprises a hermetic enclosure 2 extending along the longitudinal axis X and comprising a first longitudinal end 4 and a second longitudinal end 6.
  • the first end 4 is for example intended to be placed at a hot source SC .
  • the first end 4 is designated the evaporator, and the second end 6 is for example intended to be placed at a cold source SF.
  • the second end is called the condenser.
  • the hot source is for example an electrical or electronic component, a heat storage, an exothermic chemical reactor.
  • the cold source is for example a radiative surface, fins in forced convection, cold plates in mono or two-phase flow, cold storage, an endothermic chemical reaction, etc.
  • the heat pipe advantageously has a shape such that it extends in the XY plane, so as to have faces 7.1, 7.2, parallel to the XY plane, having a large surface area promoting heat exchanges with the hot source and the cold source .
  • the heat pipe is in contact with the hot source and the cold source on one or both sides 7.1, 7.2 of large area.
  • the faces 7.1, 7.2 of larger area are in the example shown orthogonal to the Z direction.
  • the heat pipe C1 comprises a channel 8 extending along the longitudinal axis X and grooves 10 extending along the longitudinal axis X on either side of the channel 8.
  • the channel 8 is used for circulation. of the vapor phase from the evaporator zone to the condenser zone, and will be designated by “vapor channel” and the grooves are used for the circulation of the liquid phase from the condenser zone to the evaporator zone.
  • the grooves 10 include an exchange zone 10.1 and a liquid channel 10.2 connected to the vapor channel 8 by the exchange zone 10.1.
  • the liquid channel is intended for the circulation of the liquid from the condenser zone to the evaporator zone.
  • the exchange zone has a section in the XZ plane that is smaller than that of the liquid channel 10.2.
  • the grooves are formed in the side walls 8.1, 8.2 of the channel 8.
  • the side walls are viewed with respect to the longitudinal direction X.
  • the heat pipe enclosure comprises a stack of plates delimiting the vapor channel 8 and the grooves 10.
  • the stack comprises two end plates 12 located at the ends of the stack in a Z direction orthogonal to the X and Y directions.
  • the end plates 12 are intended to close the channel 8 and are also referred to as “closure plates”. .
  • the stack also comprises intermediate plates 14, 16, 17 arranged between the end plates 12.
  • the intermediate plates comprise a set of first intermediate plates 14, a set of second intermediate plates 16, and a set of third intermediate plates 17 , the plates of the different sets being superimposed so as to delimit the channel 8 and the grooves 10.
  • the surface of the plates can vary. It is conceivable that the surface of the plates decreases in the Z direction. It is also conceivable that the width of the intermediate plates is variable along the X direction, for example to provide a condenser with a larger area than the evaporator.
  • the windows are shaped so as to cover the entire surface, they are not parallel.
  • the stack comprises sub-groups G1, G2 ... of intermediate plates comprising, in this order, a first plate 14, a second plate 16 and a first plate 14. Two sub-groups are separated by a third plate 17. At the ends of the stack, the third plates 17 are replaced by the closure plates 12.
  • a sub-group and two third plates define two grooves 10 with their exchange zone and the liquid channel.
  • the first intermediate plates have a central window 18 extending along the longitudinal axis X, and two side windows 19, located on either side of the central window 18 and extending along the longitudinal axis. X.
  • the central window 18 is separated from each side window 19 by an upright 21.
  • the first intermediate plates 14 have a thickness e1.
  • the window 18 is designated “central window” because it is located between the two side windows, but it will be understood that it is not necessarily located in the center of the first plate.
  • the windows 18 and 19 have a rectangular shape having the same dimension in the X direction.
  • the central window 18 has a dimension L1 in the Y direction and the side windows 19 have a dimension L1 'in the Y direction.
  • Each second spacer plate 16 has a thickness e2 and has a window 20 extending in the X direction and in the Y direction.
  • the window 20 has a rectangular shape having a dimension I2 in the X direction and a dimension L2. in the Y direction.
  • the dimensions of the windows 18 and 20 in the X direction are preferably equal or close and correspond to the length of the channel 8.
  • the dimension L2 is close to or equal to the distance between the two outer lateral edges of the windows 19, so that by placing a second intermediate plate 16 between two first intermediate plates 14, and by superimposing the windows, the lateral edges exterior windows 19 are aligned with the side edges of window 20.
  • This alignment defines a flat bottom for grooves 10.
  • the third intermediate plates 17 close the grooves in the Z direction.
  • Two uprights 19 of two successive first intermediate plates 14 form the transverse edges of the exchange zone 10.1 of a groove, and the thickness e2 of the second intermediate plate defines the dimension of the exchange zone in the Z direction.
  • the third plates advantageously participate in delimiting two superimposed grooves 10 in the Z direction.
  • each group has its own two third plates.
  • each group G1, G2 ... defines two facing grooves.
  • only one groove could be defined, in this case the first plates 14 would have only one side window.
  • the vapor channel 8 has a dimension along the Y direction equal to L1 ′ and a dimension along the Z direction equal to the sum of the thicknesses of all the first, second and third intermediate plates.
  • the exchange zone 10.1 of each groove has a dimension in the Z direction equal to e2.
  • the liquid channel 10.2 has a dimension in the Z direction equal to 2e1 + e2 and a dimension in the Y direction equal to L1 '.
  • the invention has the advantage of being able to separately fix the width of the exchange zone 10.1 and the section of the liquid channel 10.2.
  • the width is defined along the Z direction.
  • second intermediate plates of very small thickness e2 it is possible to use second intermediate plates of very small thickness e2 to have a small width of the exchange zone 10.2, and to use first intermediate plates 14 of large thickness e1 and of large dimensions L1 '. to produce a liquid channel of large section.
  • the width of the reentrant grooves n ' is not less than 0.5mm and the size of the liquid channel in extruded cylindrical heat pipes is typically 1.5mm in diameter, then it provides a channel section of 1.76mm 2 .
  • the width / section ratio of the liquid channel is approximately 0.28.
  • the width of the exchange zone can reach approximately 0.05 mm
  • the liquid channel which is for example of rectangular section can have a dimension in the Z direction of 1.2 mm and a dimension in the Y direction of 2 mm, i.e. a section of 2.4 mm 2 .
  • Capillary pressure is the pressure difference between the vapor phase and the liquid phase near the meniscus.
  • the menisci M shown at the exchange zone 10.1 of the grooves 10 at the evaporator, and on the figure 4B at the condenser.
  • the wetting angle is close to 90 °, and at the evaporator zone, the wetting angle is at its minimum value. Depending on the materials used, the surface treatments and the fluid, this minimum angle may be equal to 0.
  • the capillary pressure is inversely proportional to the radius of curvature of the meniscus. This radius of curvature is very large at the condenser, and is appreciably smaller at the evaporator.
  • the figure 4C we can see the retreat of the meniscus in the exchange zone between the evaporator and the condenser.
  • the heat pipe has several liquid channels along the Z direction separated by the third spacer plates.
  • the third intermediate plates conduct the heat from the plate 12 to the menisci of each liquid channel where evaporation occurs.
  • the first plates have a thickness between 0.05 mm and 6 mm, preferably equal to 0.5 mm.
  • the second plates which fix the width of the exchange zones have a thickness of between 0.05 mm and 1 mm, preferably equal to 0.2 mm.
  • the liquid channels have, for example, a dimension in the Y direction which can vary between 1 mm and 4mm, and preferably be equal to 2 mm.
  • the vapor channels have a width of between 2 mm and 8 mm, and preferably equal to 4 mm.
  • the external dimensions of the heat pipes are between a few centimeters and a few meters.
  • the maximum size of heat pipes is generally limited by the tools available. Indeed, the assembly of sheets by vacuum brazing requires large vacuum furnaces, a few meters in length. For cutting and machining of sheet metal, large machines are also required. In addition, the mechanical strength of sheets with small width and great length cuts must be taken into account.
  • the windows are produced by punching, cutting, for example with a laser or with a water jet.
  • the heat pipe is filled with a two-phase fluid, it may be a fluid well known to those skilled in the art. This is chosen for example according to the operating and storage temperature range of the device, according to the constraints due to the pressure, the flammability, the toxicity of the fluid and the chemical compatibility between the fluid and the material. forming the heat pipe.
  • the heat pipe C2 has vapor channels 108.1 to 108.6 arranged parallel to each other in the longitudinal direction X, each vapor channel being connected to grooves 110.1 to 110.6 arranged laterally on either side of each vapor channel 108.1 to 108.6 .
  • Heat pipe C1 is a pattern repeated several times in heat pipe C2. The pattern is delimited by the dotted lines.
  • the heat pipe C2 is produced by superimposing plates extending in one piece in the Y direction. Thus all the channels and all the grooves are produced by stacking the same plates. The production is then simplified, because a large heat pipe is produced in one piece, without the problem of the arrangement of the channels and of the grooves relative to one another during assembly.
  • the intermediate plates are structured so that the bottoms of two grooves opening into two neighboring channels are formed by the same elements of the intermediate plates.
  • the time for producing the plates is reduced and the density of channels and grooves is optimized.
  • the heat pipes are fluidly isolated from each other.
  • the heat pipes fluidly communicate with each other. The dimensions and the pitch between the heat pipes are chosen according to the application.
  • This heat pipe C3 differs from heat pipe C1 in that each groove 210 is delimited between two third plates 217 by a first plate 214 and a second plate 216.
  • the first plate 214 has a structure similar to that of the plate 14.
  • the exchange zone 210.1 is delimited in the Z direction, on one side by the upright 221 of the first intermediate plate 214 and on the other side by the third intermediate plate 217.
  • the width of the exchange zone 210.1 is equal to the thickness of the second intermediate plate 216.
  • the dimension of the liquid channel 210.2 in the Z direction is equal to the sum of the thicknesses of the first intermediate plate 214 and of the second intermediate plate 216.
  • the number of plates used to make the C3 heat pipe is reduced.
  • the heat pipe C4 comprises between two closure plates 312, a stack of groups of plates H1, H2 ... Each group comprising two first intermediate plates 314 and a second intermediate plate 316 disposed between the two first intermediate plates 314.
  • the second intermediate plate 316 is similar in shape to the second intermediate plate 16.
  • the first intermediate plates 314 ( figure 7B ) have a central window 318 and two side recesses 319 made in one of the faces of the first plates 314.
  • the first intermediate plates 314 have a thickness e1 and the recesses 319 have a depth p1 less than the thickness e1.
  • the recesses 319 are bordered by a frame 319 '.
  • the dimension along the Y direction of the window 320 of the second intermediate plate 316 is equal to the distance between the outer edge of a recess 319 and the outer edge of the other recess 319.
  • each group the first intermediate plates 314 are arranged on either side of the second intermediate plate 316 with the recesses 319 facing each other.
  • the liquid channels 310.2 of the grooves 310 are delimited by the recesses 319.
  • the width in the Z direction of the exchange zone 310.1 is equal to the thickness e2 of the second intermediate plate and the width of the liquid channel 310.2 in the Z direction is equal to 2e1 + e2.
  • This example of a heat pipe offers better mechanical strength of the grooves, in fact the first plates have greater strength.
  • this exemplary embodiment has the advantage of not requiring the implementation of third intermediate plates, and sealing is simpler to achieve because of the reduced number of interplate interfaces.
  • the windows 318 of the first intermediate plates 314 are for example made by punching and the recesses 319 are made by machining.
  • the first intermediate plates comprise a central window 418 and two lateral recesses 419 on either side of the central window.
  • the C5 heat pipe does not have a second intermediate plate between the two first intermediate plates 414. These are the first intermediate plates which define both the exchange zone 410.1 and the liquid channel 410.2.
  • FIG 8B we can see a top view of a first intermediate plate 414, and on the figure 8C a sectional view can be seen along the Y direction of the first spacer plate 414. It includes the central window 418 and the recesses 419.
  • the recesses 419 have three contiguous outer edges 419.1 located on the contiguous outer edges of the plate 414, and an inner edge 419.2 on the side of the window 418.
  • the outer edges 419.1 have a thickness in the Z direction equal to the thickness e1 of the plate 419, and the inner edge 419.2 has a thickness h1 less than the thickness e1.
  • the inner edges 419.2 of the two facing recesses are not in contact and leave a space forming the exchange zone 410.1 .
  • the exchange zone then has a width in the Z direction equal to 2x (e1-h1).
  • This exemplary embodiment has the advantage of offering improved mechanical strength of the grooves, of further reducing the number of different parts required to produce the heat pipe and of further simplifying the production of the seals.
  • first intermediate plates 514 have recesses in their two faces and thus participate in each delimiting two grooves 510 in the Z direction.
  • a second intermediate plate 516 is disposed between two first intermediate plates and defines the width in the Z direction. of the exchange zone 510.1.
  • the edges of the recesses all have the same thickness.
  • the inner edge of the recesses is thinned.
  • C7 heat pipe comprising two closure plates 612 and first intermediate plates 614 comprising recesses on their two faces, the recesses comprising an inner edge 619.2 thinned with respect to the outer edges 619.1.
  • the exchange zone is delimited by the thinned inner edges 619.2.
  • the number of plates is reduced, which simplifies assembly and further reduces the number of interfaces, and therefore the risk of leakage.
  • the stack comprises first plates provided with recesses and a third plate which defines, with the first plate, the exchange zones.
  • the first intermediate plates of the examples of figures 9 and 10 can be made by extrusion.
  • the plates do not come from clad sheets, and they are advantageously welded to each other with a laser by transparency layer by layer.
  • the cut of the recesses along the Y axis has a rectangular shape.
  • first intermediate plates 714 and 814 seen in section, provided with recesses 719, 819 on either side of the central window 718, 818.
  • the inner face 719.21 of the inner edge 719.2 of the recess 719 is inclined towards the open face of the recess.
  • connection fillet On the figure 11B , the inner face 819.21 and the bottom 819.3 of the recess 819 are connected by a connection fillet.
  • the side windows 919 of the first spacer plate 914 have a trapezoidal shape in the XY plane, the large base 919.1 being located on the side of the condenser zone and the smaller base 919.2 being located on the evaporator side.
  • the section of the liquid channel is smaller at the evaporator, where the liquid flow rate is less, and the exchange zone is larger in order to be able to accept a greater meniscus retreat.
  • the exchange zone 910.1 has a larger dimension in the Y direction at the level of the evaporator zone than at the level of the condenser zone. This longer exchange zone allows the meniscus of the liquid to move back more in the evaporator zone, which reduces the risk of the meniscus entering the liquid channel, and therefore reduces the risk of a sudden decrease in capillary pressure. Such a decrease can cause the heat pipe to defuse.
  • the arrows symbolize the circulation of the fluid between the condenser zone and the evaporator zone, in the vapor channel and in the reentrant grooves.
  • the lengthening of the exchange zone at the level of the evaporator zone has the effect of reducing the section of the liquid channel 910.2 at the level of the evaporator zone.
  • the liquid flow rate is lower in the evaporator zone, the liquid pressure drop is little increased, and the capillary limit is little reduced.
  • the side windows 1019 have a trapezoidal shape, the large base being located on the side of the condenser zone and the smaller base being located on the evaporator side; and the central window 1018 also has a trapezoidal shape, the larger base being on the evaporator zone side and the smaller base being on the condenser zone side.
  • This variant makes it possible to optimize the losses of liquid and vapor pressure.
  • the closure plates 12 ' have a larger area than those of the stack in the YX plane so that they protrude on either side of the stack.
  • the heat flow then spreads over a larger area, which ensures homogenization of the flow.
  • the heat pipe may have closure plates with a larger surface only in the useful zone or zones, i.e. in the condenser zone and / or in the evaporator zone.
  • the surface of the plates is advantageously reduced in the non-useful zone, for example cut before or after assembly, which makes it possible to reduce the mass of the heat pipe.
  • closure plates also applies to multichannel heat pipes.
  • the heat pipe C10 has two steam channels each surrounded by two reentrant channels, instead of a steam channel if we consider the Y direction as the heat pipe C1.
  • This arrangement makes it possible to obtain improved pressure resistance compared to the heat pipe C1.
  • each reentrant channel heat pipe is filled individually, the failure of a heat pipe makes it possible to keep 50% of the entire transport capacity.
  • the thickness of the wall between two vapor channels can be thinner than the outer walls which have to maintain a higher pressure difference.
  • the heat pipe C10 has a lower limit power than that of the heat pipe C1, but the thermal resistance, which is linked to the surface of the exchange zones, is lower.
  • the heat pipe C11 comprises a partition 24 in the vapor channel mechanically connected to the two closure plates and providing reinforcement of the heat pipe in the Z direction.
  • the partition 24 is formed by stacking the plates.
  • the partition 24 may be such that it provides fluid communication between the two parts of the steam channel, which simplifies filling.
  • the partition 24 so separates the steam channel and two steam half-channels, which allows in the event of failure of one of the half-heat pipes to retain 50% of the transport capacity.
  • the stack comprises reinforcing strands 26 extending in the Y direction and which pass through the channel.
  • the strands are formed by the third intermediate plate 17 which is visible on the figure 20 .
  • the strands 26 connect the two uprights 28 of the third intermediate plate and define a plurality of windows.
  • the reinforcement of the internal structure of the heat pipe can also be obtained by increasing the thickness of the walls formed by the stacking of the plates.
  • edges of the openings defining the grooves are straight and parallel to each other.
  • This shape makes it possible to increase the length of the triple line (connection zone between liquid / vapor and wall), in particular in the evaporator zone, which makes it possible to increase the heat exchange coefficient in evaporation.
  • the corrugated shape makes it possible to obtain walls not wetted by the condensation film at the tops of the corrugations. This also makes it possible to increase the condensation exchange coefficient by minimizing the interface resistance of the condensation film. In addition, at the condenser level, the meniscus is flush with the vapor zone, which increases the condensation surface.
  • the corrugations can be provided at the level of the condenser zone, and / or at the level of the evaporator zone.
  • the corrugations are formed over the entire length of the heat pipe, which simplifies the production and makes it possible to adapt to different lengths of the condensation zone or of the evaporation zone.
  • the bottom of the grooves is planted.
  • the filling of a single-channel heat pipe can be done by means of a filling plug inserted on the edge of the stack or by means of a plug fixed on an orifice made in one of the closure plates, for example perpendicularly. to these.
  • one channel connects all the channels.
  • This channel is for example formed by a transverse slot 30 formed on an edge of one of the third intermediate plates 1317.
  • the side windows 1319 of the first plate 1317 are extended along the X axis so that, when stacking in the Z direction, the longitudinal ends of the side windows 1319 are in line with the light 30.
  • the heat pipe C12 does not have a straight shape, it comprises two straight portions D1 and D2 oriented at right angles to one another.
  • the portions D1 and D2 extend in orthogonal planes.
  • the portion D1 extends in the XY plane and the portion D2 extends in the XZ plane.
  • the orientation of the portions D1 and D2 with respect to each other is for example obtained by folding after stacking of the plates and their securing. P1 designates the fold.
  • the C12 heat pipe can be conformed to the application.
  • the heat pipe may have several folds.
  • the portion D1 forms the evaporator and the portion D2 forms the condenser and, on its outer surfaces, is provided with fins A1 forming a radiator making it possible to evacuate the heat.
  • the radiator works for example in natural convection or in forced convection.
  • the fins A1 are provided on the two large surface faces of the condenser. As a variant, fins could be envisaged on a single face.
  • the fins have flat plates perpendicular to the faces of the condenser. Any other form is possible.
  • the fins are extruded fins, skived fins, pin fins, molded fins, fins fixed by knurling, fins produced by 3D printing, or any other fin obtained by a technique for producing extension of surface well known to those skilled in the art.
  • One or more finned radiators as described above can be implemented in a single-channel or multi-channel heat pipe straight or having any other shape.
  • a cooling circuit is integrated directly into the heat pipe C13 as shown in the figure. figure 26 .
  • the heat pipe comprises a cooling circuit 32 in which a heat transfer fluid is intended to circulate.
  • the cooling circuit is in direct contact with the condenser.
  • the cooling circuit 32 is formed by an additional plate 36, in which are formed grooves 38 defining the side walls of the circuit, and the closure plate 12 and an additional closure plate 40 form the walls d end of the cooling circuit.
  • the closure plate 12 has two orifices 42 each opening at one end of the circuit and allowing the circulation of the heat transfer fluid.
  • the heat transfer fluid can be a liquid or a gas.
  • it is a two-phase circuit.
  • Such a circuit can also be used to form the hot source at the level of the evaporator.
  • Each heat pipe has an evaporator length of 200 mm, an adiabatic zone length of 600 mm, a condenser length of 200 mm (total length 1m).
  • Each heat pipe is made of aluminum alloy.
  • the working temperature in the adiabatic zone of the heat pipe is 60 ° C; i.e. the mean vapor temperature of the heat pipe.
  • the working fluid is ammonia.
  • the heat pipe according to the invention has the following characteristics:
  • the heat pipe has a section of 13.2mm x 13.2mm and wings formed by the closure plates of 30mm in the Y direction.
  • the heat pipe section is shown in Figure 16 .
  • the heat pipe of the state of the art has an external size close to that of the heat pipe according to the invention above and has a mass of 300 g.
  • the heat pipe according to the invention has, with identical dimensions, a limit power of 4 to 6 times greater than that of a heat pipe of the state of the art, for a slightly greater mass.
  • the heat pipe according to the invention only requires two levels of grooves, i.e. four grooves.
  • This heat pipe will for example be of identical width less thick, it is shown in figure 33 .
  • the heat pipe of the figure 33 has a section of 13.2 mm x 4.9 mm and wings formed by the closure plates of 30 mm in the Y direction, and a mass of 210 g.
  • the cylindrical heat pipe of the state of the art has a section of 13.2 mm ⁇ 13.2 mm and wings formed by the closure plates of 30 mm, and a mass of 300 g.
  • a gain in empty weight of 30% and a gain of 68% in the thickness of the heat pipe can be obtained by virtue of the invention compared with the cylindrical heat pipes with reentrant grooves of the state of the art.
  • the thermal resistances of the fluxes between the hot and / or cold sources are more advantageous in the heat pipes depending on that in the cylindrical heat pipes with reentrant grooves.
  • the cylindrical heat pipes with reentrant grooves of the state of the art have a more marked reduction in the transmission cross section of the flux by conduction (constriction of the heat flux by conduction) which is unfavorable to thermal resistances.
  • the thermal path is more complex and longer with the heat pipes of the state of the art.
  • heat pipes according to the invention such as that of the figure 1 , arranged in the form of a lattice, the heat pipes C1 and C1 'crossing at right angles in the example shown.
  • the heat pipes C1 are bent so as to deploy in two perpendicular planes.
  • the heat pipes C1 extend along the axis a1 and the heat pipes extend along the axis a2.
  • the heat pipes may or may not be fluidly connected.
  • the heat pipes in the same plane can communicate with each other thanks to openings made in the intermediate plates, as shown on the figure. figure 23 .
  • the example in which the heat pipes are not fluidly connected to one another has the advantage of offering redundancy in the event that one of the heat pipes is faulty.
  • a closing plate of a heat pipe C1 also forms the closing plate of a heat pipe C1 ′.
  • the tooling for maintaining pressure during brazing is preferably flat and will rest on the outside of the two closure plates.
  • the sheets cover the entire surface before brazing. It is nevertheless possible to open the sheets before assembly in order to lighten the assembly.
  • the stack is brazed flat in a vacuum oven
  • the inter-heat pipe spaces are perforated.
  • this trellis is hollowed out.
  • FIG 31 we can see a variant of the figure 29 comprising mechanical reinforcements formed by a metal veil 44.
  • a metal veil 44 As a variant, several sails can be implemented, for example one on each side of the heat pipe mesh.
  • a metal veil is a very thin metal sheet, typically of the order of 0.2 mm, which is for example glued to the heat pipes.
  • FIG 32 we can see a variant of the figure 29 comprising a heat exchange circuit 46 for removing heat from a single-phase circuit, or the condenser of a two-phase cooling circuit. The heat is then removed by radiation through the network of heat pipes C1 and C1 '.
  • a crossed heat pipe system can be made in one piece, ie the interfaces between the intersecting heat pipes are formed by a plate common to the intersecting heat pipes, and not by two plates in contact with one another. with the other.
  • the thermal interface resistances at the node of the trellis are appreciably reduced.
  • the trellis can be self-supporting, which can make it possible not to have to implement an additional support structure.
  • the heat pipes can form a lattice in which the heat pipes cross at a non-right angle.
  • the angle may vary over the entire surface of the trellis.
  • the spacing between the heat pipes can be variable.
  • the mesh can include heat pipes of different sizes.
  • the heat pipe according to the invention can be made of different materials such as, for example, an aluminum alloy, copper or stainless steel.
  • the technique of joining the sheets depends on the material.
  • vacuum brazing with clad plates for example, in the case of aluminum alloy plates, vacuum brazing with clad plates, salt bath brazing, inert gas brazing, ultrasonic welding, laser welding, laser welding, or welding can be used. friction-kneading (Friction Stir Welding), gluing ...
  • the material (s) used for the manufacture of the heat pipe are chosen according to the constraints of mass, assembly, required robustness ...
  • the assembly of aluminum alloy plates is obtained by eutectic brazing.
  • Aluminum alloy plates are used in known manner, one or both faces of which is or are coated with an aluminum alloy with a lower melting point.
  • an alloy sheet of the AA3xxxx series with the core is used, with a coating with a eutectic alloy of the AA4xxxx series comprising silicon with a lower melting point.
  • Coating is typically done by a roll-bond technique.
  • the total thickness of the plates is typically 0.05mm to 5mm, with a coating typically of 5% to 10% of the total thickness on one or both sides.
  • the brazing is preferably carried out under pressure by means of a mechanical holding system, which maintains the stack under pressure during the brazing in a vacuum furnace.
  • Cutouts and / or folds are required in the manufacturing process to lighten and / or shape the structure. They are preferably made after assembly. It should be noted that the cutting of the windows in the plates, for example the central windows, is carried out before assembly.
  • Plates of a given material are cut to the desired outer shape for the heat pipe.
  • the first, second and third intermediate plates are structured, for example by punching, machining, cutting laser, by water jet cutting or through chemical etching ... in order to create specific windows in the different plates, so that once assembled a reentrant grooved heat pipe is formed.
  • the plates are then stacked in a given order, for example by alternating a second intermediate plate and a third intermediate plate between two first intermediate plates; closure plates are arranged at the ends of the stack to close the channel or channels.
  • cooling channels are provided on one or both sides of the stack.
  • the plates are assembled, the assembly technique being chosen as a function of the material (s) of the plates, for example welding, brazing, gluing, etc., the assembly of the plates is sealed.
  • the material or materials of the plates is or are chosen according to the working fluid, which is itself chosen according to the thermalization specifications of the system to be produced.
  • the heat pipe is then filled.
  • a filling orifice was made in one of the opening plates during the manufacture of the plates.
  • the fluid is chosen according to the operating conditions of the heat pipe (operating temperature, etc.) and the compatibility with the material or materials of the heat pipe.
  • the thermal performance in terms of maximum transportable power of heat pipes with reentrant grooves is improved compared to heat pipes with reentrant grooves of the state of the art, i.e. cylindrical heat pipes with reentrant grooves.
  • heat pipes with reentrant grooves of the state of the art i.e. cylindrical heat pipes with reentrant grooves.
  • the second intermediate plates can be omitted, which reduces the number of parts used.
  • the plates have increased strength.

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  • Sustainable Development (AREA)
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  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (15)

  1. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen, die sich wenigstens entlang einer ersten Längsrichtung (X) erstrecken, umfassend ein erstes Längsende (4), das dazu ausgelegt ist, geheizt zu werden, und ein zweites Längsende (6), das dazu ausgelegt ist, gekühlt zu werden, eine dichte Hülle (2), die sich zwischen dem ersten Ende (4) und dem zweiten Ende (6) erstreckt, wobei die Hülle einen Stapel von Platten entlang einer zweiten Richtung (Z) umfasst, wobei der Stapel zwei Abschlussplatten (12) umfasst, und wenigstens ein Modul von wenigstens zwei Zwischenplatten (14, 16, 17, 214, 216, 217, 314, 316, 317) zwischen den Abschlussplatten (12), wobei das Wärmerohr dadurch gekennzeichnet ist, dass die Zwischenplatten wenigstens eine erste Zwischenplatte (14, 214, 314) umfassen, umfassend wenigstens ein zentrales Fenster (18, 118, 318), dessen Ränder teilweise einen Dampfkanal (8) begrenzen, der sich entlang der ersten Richtung (X) erstreckt, in dem der Dampf zirkulieren soll, und auf jeder Seite des wenigstens einen zentralen Fensters (18, 118, 318) entlang einer dritten Richtung (Y) orthogonal zu der ersten (X) und zu der zweiten (Z) Richtung eine Struktur, deren Ränder teilweise einen Flüssigkeitskanal begrenzen, wobei wenigstens eine andere Zwischenplatte wenigstens ein Fenster umfasst, dessen Ränder teilweise den Dampfkanal (8) begrenzen, und wobei das Wärmerohr wenigstens zwei Austauschzonen (10.1, 110.1, 310.1) umfasst, die zwischen der wenigstens einen Zwischenplatte und der wenigstens einen anderen Zwischenplatte begrenzt sind, die den Dampfkanal und den Flüssigkeitskanal verbinden.
  2. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach Anspruch 1, bei dem die wenigstens eine andere Zwischenplatte die wenigstens erste Zwischenplatte (314) ist, und bei dem die Strukturen Aussparungen (319) sind, die in wenigstens einer der Flächen der ersten Zwischenplatten (314) realisiert sind, wobei in dem Stapel die Aussparungen (319) einander gegenüber liegen, und wobei die Austauschzonen (310.1) begrenzt sind durch zwei Ränder von zwei Aussparungen (319) der zwei ersten Zwischenplatten (314), die einander gegenüber liegen, wobei die ersten Zwischenplatten vorzugsweise Aussparungen in ihren zwei Flächen umfassen.
  3. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach Anspruch 2, bei dem eine zweite Zwischenplatte (316) zwischen zwei ersten Zwischenplatten (314) im Bereich von äußeren Rändern der ersten Zwischenplatten (316) eingefügt ist, deren Dicke die Abmessung in der Stapelungsrichtung der Austauschzonen (310.1) begrenzt, und/oder bei dem die Aussparungen einen Boden und wenigstens einen Rand umfassen, der den Boden mit der Austauschzone verbindet, wobei der Rand vom Dampfkanal beabstandend geneigt ist, oder wobei der Rand an dem Boden mittels einer Anschlußkehle angeschlossen ist.
  4. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach Anspruch 1, bei dem die andere Platte eine dritte Zwischenplatte (217) ist, deren Fenster den gleichen Querschnitt wie das zentrale Fenster der ersten Zwischenplatte (214) derart hat, dass zwei von seinen lateralen Rändern in der dritten Richtung (Y) zusammen mit der ersten Zwischenplatte (214) Austauschzonen (210.1) begrenzen, wobei eine zweite Zwischenplatte (216) vorzugsweise zwischen der ersten Zwischenplatte (214) und der dritten Zwischenplatte (217) im Bereich von äußeren Rändern der ersten und der dritten Zwischenplatte eingefügt ist, deren Dicke die Abmessung in der Stapelungsrichtung der Austauschzonen begrenzt.
  5. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach Anspruch 1, bei dem die andere Zwischenplatte eine erste Zwischenplatte (14) ist, bei dem die Strukturen Fenster (19) sind, wobei das Wärmerohr eine zweite Zwischenplatte (16) umfasst, die zwischen den zwei ersten Zwischenplatten (14) im Bereich von äußeren Rändern der ersten Zwischenplatten (14) eingefügt ist, deren Dicke die Abmessung in der Stapelungsrichtung der Austauschzonen (10.1) begrenzt, und wobei das Wärmerohr eine dritte Zwischenplatte (17) umfasst, deren Fenster den gleichen Querschnitt hat wie die zentralen Fenster (18) der ersten Zwischenplatten (14), in Kontakt mit einer der ersten Zwischenplatten (14) und die lateralen Fenster (19) auf beiden Seiten des zentralen Fensters (18) in der zweiten Richtung (Z) verschließend.
  6. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach einem der Ansprüche 1 bis 5, umfassend n Module aufeinander, wobei n eine ganze Zahl > 1 ist, die einen einzigen Dampfkanal und n Flüssigkeitskanäle auf jeder Seite des Flüssigkeitskanals und n Austauschzonen definieren, von denen jede den Dampfkanal mit einem Flüssigkeitskanal verbindet.
  7. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach einem der Ansprüche 1 bis 6, bei dem die Strukturen in einer Ebene orthogonal zu der zweiten Richtung eine Trapezform aufweisen, und/oder bei dem die zentralen Fenster der Zwischenplatten einen Pfosten umfassen, der sich in der ersten Richtung derart erstreckt, dass der Dampfkanal eine Wand umfasst, die sich über die gesamte Höhe des Stapels und in der ersten Richtung erstreckt.
  8. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach Anspruch 4 oder 5, bei dem das Fenster von wenigstens einer dritten Zwischenplatte wenigstens einen Querpfosten umfasst, der sich in der dritten Richtung erstreckt.
  9. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach einem der Ansprüche 1 bis 8, umfassend mehrere Dampfkanäle, von denen jeder durch Austauschzonen mit Flüssigkeitskanälen verbunden ist.
  10. Wärmerohr mit Kapillarpumpung nach einem der Ansprüche 1 bis 9, bei dem wenigstens eine der Endplatten eine Oberfläche aufweist, die größer ist als jene der Zwischenplatten in einer Richtung quer zum Stapel derart, dass thermische Diffusoren gebildet werden.
  11. Wärmerohr mit Kapillarpumpung mit Wiedereintrittsrillen nach einem der Ansprüche 1 bis 10, umfassend Wärmeaustauschmittel im Bereich des ersten Endes und/oder des zweiten Endes, wobei die Wärmeaustauschmittel im Bereich des zweiten Endes vorzugsweise einen oder mehrere Flügel in thermischem Kontakt mit wenigstens einer der Abschlussplatten umfassen.
  12. Wärmerohr mit Kapillarpumpung nach Anspruch 11, bei dem die Wärmeaustauschmittel einen Fluidkreislauf (32) in thermischem Kontakt mit wenigstens einer der Abschlussplatten (12) umfassen, wobei der Kreislauf gebildet ist durch eine Platte (36), die derart strukturiert ist, dass sie Kanäle (38) begrenzt, wobei die Kanäle (38) durch die Abschlussplatte (12) und eine zusätzliche Abschlussplatte (40) geschlossen sind, wobei die Wärmeaustauschmittel ferner Mittel zur Versorgung des Fluidkreislaufs mit einem Wärmeträgerfluid umfassen.
  13. Wärmeaustauschsystem, umfassend mehrere Wärmerohre nach einem der Ansprüche 1 bis 11, bei dem die Wärmerohre in mehreren Ebenen angeordnet sind, wobei sich die Wärmerohre von zwei aufeinander folgenden Ebenen kreuzen, und wobei die Wärmerohre von zwei aufeinander folgenden Ebenen sich ein und dieselbe Endplatte teilen, wobei wenigstens ein Wärmerohr einer Schicht vorzugsweise hydraulisch mit wenigstens einem Wärmerohr der gleichen Schicht verbunden ist.
  14. Wärmeaustauschsystem nach Anspruch 13, umfassend einen einphasigen oder zweiphasigen Wärmeaustauschkreis.
  15. Verfahren zur Herstellung eines Wärmerohrs mit Kapillarpumpung nach Anspruch 1, umfassend ausgehend von wenigstens zwei Platten mit gegebenen äußeren Abmessungen:
    - Realisieren wenigstens eines zentralen Fensters in wenigstens zwei Platten,
    - Strukturieren jeder Seite des wenigstens einen zentralen Fensters in wenigstens einer der Platten, um laterale Fenster oder laterale Aussparungen zu bilden,
    - Stapeln der Platten derart, dass die zentralen Fenster einen Dampfkanal begrenzen, dass die lateralen Fenster oder Aussparungen Flüssigkeitskanäle auf beiden Seiten des Dampfkanals bilden, und derart, dass Austauschzonen den Dampfkanal und die Flüssigkeitskanäle verbinden;
    - Platzieren von Abschlussplatten an den Enden des Stapels in der Stapelungsrichtung,
    - Verbinden der Platten derart, dass ein dichtes Gehäuse begrenzt wird, wobei die Platten vorzugsweise im Kern eine Aluminiumlegierung umfassen und auf ihren äußeren Flächen eine eutektische Aluminiumlegierung mit einem Schmelzpunkt, der tiefer ist als jener der Aluminiumlegierung im Kern, und wobei die Verbindung durch eutektisches Löten erzielt wird,
    - partielles Füllen des Kanals mit einem Fluid in flüssiger Form und dichtes Schließen des Kanals.
EP19168586.6A 2018-04-11 2019-04-11 Verbessertes wärmerohr mit kapillarstrukturen mit wiedereintrittsrillen Active EP3553445B8 (de)

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FR3128280B1 (fr) * 2021-10-18 2023-10-06 Commissariat Energie Atomique Caloduc de type à pompage capillaire avec rainures réentrantes à conductivité thermique augmentée.
FR3128278B1 (fr) * 2021-10-18 2023-10-06 Commissariat Energie Atomique Module pour la fabrication d’un caloduc a pompe capillaire a rainures réentrantes
FR3128279B1 (fr) 2021-10-18 2023-10-06 Commissariat Energie Atomique Caloduc de type à pompage capillaire avec rainures réentrantes à limites d’ébullition et capillaire augmentées.
FR3128281B1 (fr) 2021-10-18 2023-10-06 Commissariat Energie Atomique Caloduc de type à pompage capillaire avec rainures réentrantes à gestion de liquide améliorée.
FR3138687B1 (fr) * 2022-08-03 2024-07-12 Calyos Sa Echangeur de chaleur
FR3138943A1 (fr) 2022-08-17 2024-02-23 Commissariat A L'energie Atomique Et Aux Energies Alternatives Caloduc à section transversale non cylindrique, comprenant un évaporateur à structure d’interface vapeur/liquide améliorée afin d’augmenter la limite d’ébullition.
FR3138942B1 (fr) 2022-08-17 2024-08-16 Commissariat Energie Atomique Caloduc de type à pompage capillaire, à rainures réentrantes intégrant au moins un substrat poreux à l’évaporateur.
FR3138941B1 (fr) 2022-08-17 2024-11-01 Commissariat Energie Atomique Caloduc de type à pompage capillaire, à rainures réentrantes transversales à l’axe longitudinal du caloduc.

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FR2776763B1 (fr) * 1998-03-30 2000-07-21 Atmostat Etudes Et Rech Dispositif d'echanges thermiques a fluide biphasique actif et procede de fabrication d'un tel dispositif
FR2776764B1 (fr) * 1998-03-30 2000-06-30 Atmostat Etudes Et Rech Dispositif d'echanges thermiques a fluide biphasique actif et procede de fabrication d'un tel dispositif
KR100912538B1 (ko) * 2007-12-04 2009-08-18 한국전자통신연구원 평판형 마이크로 열이송 장치
KR20120065575A (ko) * 2010-12-13 2012-06-21 한국전자통신연구원 압출로 제작되는 박막형 히트파이프

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