EP3561428B1 - Wärmeleitrohr mit kapillarpumpensystem mit verbesserter funktionsweise - Google Patents

Wärmeleitrohr mit kapillarpumpensystem mit verbesserter funktionsweise Download PDF

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Publication number
EP3561428B1
EP3561428B1 EP19168582.5A EP19168582A EP3561428B1 EP 3561428 B1 EP3561428 B1 EP 3561428B1 EP 19168582 A EP19168582 A EP 19168582A EP 3561428 B1 EP3561428 B1 EP 3561428B1
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EP
European Patent Office
Prior art keywords
plates
heat pipe
dividing
groove
dividing plates
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English (en)
French (fr)
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EP3561428A1 (de
Inventor
Jean-Antoine Gruss
Mathieu Mariotto
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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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    • 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
    • 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

Definitions

  • the present invention relates to an improved functioning capillary pumped heat pipe.
  • the invention belongs to the field of heat exchange devices, in particular heat pipes, more particularly capillary pumped heat pipes. Specifically, the present invention relates to a heat pipe according to the preamble of claim 1, as disclosed in document US 2005 / 0022978A1 .
  • 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 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 the 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.
  • the depth to width ratio is of the order of 1.
  • the bottom of the grooves has rounded corners, which does not make it possible to have good capillary action in the corners.
  • Another technique uses mechanical machining, with this technique also the depth to width ratio is not substantially greater than 1.
  • Another technique uses chemical etching. But it does not make it possible to have a significant depth to width ratio either. In addition, the corners of the bottom of the grooves are rounded.
  • the document US 7 051 793 describes a heat pipe comprising one or more zones for the circulation of fluid in vapor form and on either side of these zones porous zones for 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 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 define grooves extending the entire length of the heat pipe channel and having a small width compared to its depth.
  • the heat pipe comprises at least three intermediate plates, two first plates each having an opening of small transverse dimension and a second plate having an opening of large dimension transversely to the length of the heat pipe.
  • the second plate defines with the first two plates two grooves.
  • the width and depth of the capillary channels are set, respectively, by the thickness of the second plate and the difference between the transverse dimensions of the openings of the first and second plates.
  • the bottom of the grooves advantageously has corners delimited by flat surfaces.
  • a small groove width is chosen, which allows a high capillary pressure.
  • the capillary pumping effect is then improved, the result of which is that the limiting power that the heat pipe can carry is increased.
  • the heat pipe comprises several channels, each channel being delimited by a series of openings made in the plates, each channel advantageously comprising at least one groove.
  • the grooves are delimited by stacked plates.
  • the depth and the width of the grooves are obtained separately, so the limitations of the depth to width ratio do not arise which arise for example in the case of production by extrusion or chemical etching.
  • Each face of the groove in the direction of the stack is defined by a different plate of the plate defining the bottom of the groove in the direction of the plane.
  • the present invention therefore relates to a capillary pumped heat pipe comprising a first end intended to be heated and a second end intended to be cooled, and a sealed enclosure extending between the first end and the second end, the enclosure comprising a stack of plates, said stack comprising two closure plates, and intermediate plates between the closure plates, each intermediate plate comprising at least one opening, the edges of which partly define a channel.
  • the openings of at least three intermediate plates are dimensioned so that they define at least one groove extending between the first end and the second end of the heat pipe, said groove having a width in a direction of the stack less than or equal at depth in the direction of the plane of the plates.
  • the ratio between the depth and the width of the groove is advantageously between 1 and 80.
  • Each intermediate plate may have p openings so that the stack of plates delimits p channels.
  • one is disposed between the other two intermediate plates and is in mechanical contact with the other two intermediate plates.
  • At least one edge of the opening of the intermediate plate arranged between the two other intermediate plates may form the bottom of at least one groove, and the edges of the openings of the other two intermediate plates delimiting the groove are corrugated or sawtooth. .
  • the channel may have two side faces, said three intermediate plates defining a groove in each side face.
  • the intermediate plates may comprise n first intermediate plates and n + 1 second intermediate plates, the n first intermediate plates each comprising at least one opening of width L1, the n + 1 second intermediate plates each comprising at least one opening of width L2, the width L1 being greater than width L2, and each first intermediate plate being received between two second intermediate plates, each pair of first successive intermediate plates defining with a second intermediate plate disposed between the first intermediate plates of said pair two facing grooves.
  • the capillary pumped heat pipe may include heat exchange means at the first end and / or second end.
  • the heat exchange means at the second end may include one or more fins in thermal contact with at least one of the closure plates.
  • the heat exchange means may include a fluid circuit in thermal contact with at least one of the end plates, said circuit being formed by a plate structured so as to delimit channels, said channels being closed by said closure plate and a additional closure plate, the heat exchange means also comprising means for supplying heat transfer fluid to said fluid circuit.
  • At least one of the end plates has a surface greater than that of the intermediate plates in a direction transverse to the stack so as to form thermal diffusers.
  • 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 in which 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 heat source. SC.
  • the first end is designated as the evaporator, and the second end 4 is for example intended to be placed at a cold source SF.
  • the second end is called the condenser.
  • the heat source is for example an electrical or electronic component, a heat storage device, an exothermic chemical reactor.
  • the heat sinks of the fins in forced convection, cold plates in mono or two-phase flow, cold storage, an endothermic chemical reaction ...
  • 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 exchange with the heat source and the source. cold.
  • the heat pipe is in contact with the heat 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 in a direction Y orthogonal to the X axis.
  • the grooves 10 are formed in the side walls 8.1, 8.2 of the channel 8.
  • the side walls are considered with respect to the longitudinal direction X and are located in planes intersecting the planes of the faces 7.1, 7.2 with the largest surface area of the heat pipe.
  • the heat pipe enclosure comprises a stack E of plates delimiting the channel 8 and the grooves 10.
  • Stack E 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 comprises intermediate plates 14, 16 arranged between the end plates 12.
  • the intermediate plates comprise first intermediate plates 14 and second intermediate plates 16, the second intermediate plates 16 alternate with the first intermediate plates 14.
  • Each first intermediate plate 14 has a thickness e1, and comprises an opening 18 extending in the X direction and in the Y direction.
  • the opening 18 has a rectangular shape having a dimension I1 in the X direction and a dimension L1 in the Y direction.
  • Each second spacer plate 16 has a thickness e2 and has an opening 20 extending in the X direction and in the Y direction.
  • the opening 20 has a rectangular shape and has a dimension I2 in the X direction and a dimension L2 in the Y direction.
  • the L1 dimension is smaller than the L2 dimension.
  • the stack of two first plates on either side of a second plate delimits two grooves 10 as can be seen on the figures. figure 1B and 3 .
  • Each first plate participates in defining grooves 10.
  • the grooves have a thickness equal to the thickness e2 of the second plate 16 and a depth equal to (L1-L2) / 2, considering that the grooves 10 on either side of the X axis have the same depth and that the openings are centered relative to the edges of the plates.
  • the openings are made by punching, cutting, for example with a laser or with a water jet.
  • Capillary pressure is the pressure difference between the vapor phase and the liquid phase near the meniscus.
  • the menisci M represented in the grooves 10 at the level of the evaporator, and on the figure 3B at the condenser.
  • 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 section through which the liquid passes through the grooves is increased, which reduces pressure drops and pushes back the capillary limit.
  • the bottom of the grooves has substantially right angles which is favorable. capillary action, unlike the rounded corners of the grooves obtained by extrusion or etching for example.
  • 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 liquid is evaporated in the evaporator and the vapor generated circulates in the central channel towards the condenser.
  • the vapor condenses.
  • the liquid circulates in the grooves towards the evaporator.
  • the curvature of the meniscus at the evaporator causes a difference in capillary pressure between the evaporator and the condenser, favoring the liquid flow towards the evaporator and the vapor flow towards the condenser.
  • the radius of curvature of the meniscus is reduced at the evaporator, which increases the capillary pressure and therefore the pumping of liquid to the evaporator.
  • the technique of manufacturing by stacking plates makes it possible to obtain a high depth / width ratio of the grooves, which makes it possible to increase the liquid passage section of the grooves and therefore to reduce the loss of liquid pressure.
  • the width of the grooves is between 0.05 mm and 6 mm, and can reach 0.05 mm. It should be noted that in the case of heat pipe of the state of the art obtained by extrusion, the width of the grooves is at least of the order of 0.2 mm for small diameters of the heat pipe, for example with a smaller internal diameter. to 10 mm, and approximately of the order of 0.5 mm for the largest diameters
  • the depth of the grooves is between 1 mm and 4 mm, and is very advantageously equal to 3 mm.
  • the depth / width ratio of the grooves can reach at least 20, or even more with grooves of 0.05 mm in width.
  • the depth / width ratio is of the order of 1.
  • the distance between the evaporator and the condenser can vary from a few centimeters to a few meters.
  • 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 material (s) used for the manufacture of the heat pipe are chosen according to the constraints of mass, assembly, the required strength, etc.
  • the technique of joining the sheets depends on the material.
  • 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.
  • the heat pipe C3 comprises several channels 108 arranged one beside the other.
  • the heat pipe C3 comprises two closure plates 112, a plurality of stacked plates, the intermediate plates 114 and 116 have as many openings as there are channels.
  • all of the second spacer plates 116 have the widest openings so that the side edges of the openings form the bottom of the grooves and all of the first spacer plates 114 have the narrowest openings, so that the sides first plates form the lateral flanks of the grooves.
  • spacer plates 114 could have wider openings and narrower openings as well as plates 116.
  • the C3 heat pipe increases the heat flow transmitted and / or the exchange surface.
  • the different channels could not have the same number of grooves and / or the same distribution of the grooves.
  • 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, in particular in the evaporator zone, which makes it possible to increase the evaporative exchange coefficient.
  • 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.
  • the bottom of the grooves is straight.
  • it can also be corrugated.
  • the edges 320.1 of the openings are sawtooth.
  • the grooves 310 are also sawtooth in the XY plane. As with the corrugated grooves, the condensation and evaporation exchange coefficients are increased.
  • the channel has a section other than rectangular, it is for example trapezoidal.
  • the heat pipe has a parallelepipedal shape.
  • the surface of the plates can vary. It is conceivable that the surface of the plates decreases in the Z direction, as shown in the figure. figure 11 .
  • the width of the intermediate plates is variable along the direction X, for example to produce a condenser of more large surface area than the evaporator as shown schematically on the figure 12 showing a first intermediate plate 414.
  • the openings are shaped so as to cover the entire surface, they are not parallel.
  • only one of the side faces of the channel has grooves.
  • a different number of grooves can also be envisaged between the two side faces.
  • the grooves 610 in one side face are offset with respect to the grooves in the other side face as shown schematically on the figure. figure 20 .
  • This exemplary embodiment makes it possible to use the same type of sheet to form all the intermediate plates, for this it is sufficient to alternately turn each plate head to tail.
  • the grooves do not have the same depth in the same channel and / or from one channel to another.
  • thermal diffusers or “spreader” in English terminology extending parallel to the XY plane.
  • the thermal diffusers are integral with the closure plates and extend symmetrically on either side of the channel. These diffusers have the effect of spreading the heat flow over a larger area and increasing the overall efficiency of the thermal system.
  • only one of the two closure plates has diffusers and / or diffusers are provided only on one side of the XZ plane and / or the diffusers have different surfaces on either side of the XZ plane. It can be envisaged that the size of the diffuser (s) be reduced, for example in the X direction.
  • the heat pipe C6 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 C6 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 is provided on its outer surfaces with fins A1 forming a radiator making it possible to evacuate the heat.
  • the radiator is for example in natural convection or in forced convection.
  • the fins are provided on the two large surface faces of the condenser. Alternatively, fins on a single surface could be considered.
  • 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.
  • a cooling circuit is integrated directly into the heat pipe C7 as shown in the figure. figure 16 .
  • the heat pipe comprises a cooling circuit 524 in which a heat transfer fluid circulates.
  • the cooling circuit is in direct contact with the condenser.
  • the cooling circuit 524 is formed by an additional plate 526, in which are formed grooves 528 defining the side walls of the circuit, and the closure plate 512 and an additional closure plate 530 form the walls d end of the cooling circuit.
  • the additional closure plate 530 has two orifices 532 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 heat source at the evaporator.
  • Each heat pipe has an evaporator length of 50 mm, an adiabatic zone length of 100 mm, a condenser length of 110 mm
  • Each heat pipe is made of copper.
  • the temperature in the adiabatic zone of the heat pipe is 60 ° C; ie the average vapor temperature of the heat pipe.
  • the heat pipe according to the invention is more efficient than the heat pipe of the state of the art, whatever the inclination of the heat pipe.
  • the heat pipe according to the invention is more efficient than the heat pipe of the state of the art, whatever the temperature of the heat pipe.
  • Plates of a given material are cut to the desired outer shape for the heat pipe.
  • the openings are made in all the intermediate plates.
  • the openings are made for example by punching, laser cutting, by water jet cutting or by through chemical etching ... openings of different dimensions are made in the different plates so that once assembled grooves are formed.
  • closure plates are placed 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 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 (s) of the heat pipe.

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  • Sustainable Development (AREA)
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  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (12)

  1. Wärmerohr mit Kapillarpumpwirkung, enthaltend einen Kanal und mindestens eine in den Kanal mündenden Nut, wobei das Wärmerohr ein erstes Ende (4), das erwärmt werden soll, und ein zweites Ende (6), das gekühlt werden soll, und eine dichte Hülle (2) aufweist, die sich zwischen dem ersten Ende (4) und dem zweiten Ende (6) erstreckt, wobei die Hülle eine Stapelung von Platten aufweist, wobei die Stapelung zwei Verschlussplatten (12) und Zwischenplatten (14, 16, 216, 214) zwischen den Verschlussplatten (12) aufweist, wobei jede Zwischenplatte (14, 16, 216, 214) mindestens eine Öffnung aufweist, deren Ränder teilweise einen Kanal (8) begrenzen, und wobei die Öffnungen von mindestens drei Zwischenplatten (14, 16, 216, 214) so bemessen sind, dass sie mindestens eine Nut (10, 210) begrenzen, die sich zwischen dem ersten Ende (4) und dem zweiten Ende (6) des Wärmerohrs erstreckt, wobei die Nut (10, 210) eine Breite in einer Richtung der Stapelung aufweist, die kleiner oder gleich der Tiefe in der Richtung der Ebene der Platten (14, 16, 216, 214) ist,
    wobei das Wärmerohr dadurch gekennzeichnet ist, dass von den drei Zwischenplatten (14, 16) eine zwischen den beiden weiteren Zwischenplatten angeordnet ist und in mechanischem Kontakt mit den beiden weiteren Zwischenplatten steht und wobei mindestens ein Rand der Öffnung der zwischen den beiden weiteren Zwischenplatten (214) angeordneten Zwischenplatte (216) den Nutgrund mindestens einer Nut (210) in Richtung der Ebene bildet, wobei jede Seite der Nut in Richtung der Stapelung durch eine andere Zwischenplatte definiert ist als die Zwischenplatte, die den Nutgrund der Nut in Richtung der Ebene definiert.
  2. Wärmerohr mit Kapillarpumpwirkung nach Anspruch 1,
    wobei das Verhältnis zwischen der Tiefe und der Breite der Nut (10) zwischen 1 und 80 liegt.
  3. Wärmerohr mit Kapillarpumpwirkung nach Anspruch 1 oder 2,
    wobei jede Zwischenplatte p Öffnungen aufweist, so dass die Plattenstapelung p Kanäle begrenzt.
  4. Wärmerohr mit Kapillarpumpwirkung nach einem der Ansprüche 1 bis 3, wobei die Ränder (220.1) der Öffnungen der beiden weiteren Zwischenplatten (214), die die Nut (210) begrenzen, gewellt oder sägezahnförmig sind.
  5. Wärmerohr mit Kapillarpumpwirkung nach einem der vorstehenden Ansprüche,
    wobei der Kanal (10) zwei Seitenflächen (8.1, 8.2) aufweist, wobei die drei Zwischenplatten in jeder Seitenfläche (8.1, 8.2) eine Nut (10) begrenzen.
  6. Wärmerohr mit Kapillarpumpwirkung nach einem der Ansprüche 1 bis 5, wobei die Zwischenplatten n erste Zwischenplatten (14) und n + 1 zweite Zwischenplatten (16) umfassen, wobei die n ersten Zwischenplatten (14) jeweils mindestens eine Öffnung der Breite L1 und die n + 1 zweiten Zwischenplatten (16) jeweils mindestens eine Öffnung der Breite L2 aufweisen, wobei die Breite L1 größer als die Breite L2 ist und jede erste Zwischenplatte (14) zwischen zwei zweiten Zwischenplatten (16) aufgenommen ist, wobei jedes Paar aufeinanderfolgender erster Zwischenplatten (16) mit einer zweiten Zwischenplatte (16), die zwischen den ersten Zwischenplatten (14) des Paars angeordnet ist, zwei einander gegenüberliegende Nuten (10) definiert.
  7. Wärmerohr mit Kapillarpumpwirkung nach einem der Ansprüche 1 bis 6, enthaltend Wärmeaustauschmittel im Bereich des ersten Endes und/oder des zweiten Endes.
  8. Wärmerohr mit Kapillarpumpwirkung nach Anspruch 7,
    wobei die Wärmeaustauschmittel im Bereich des zweiten Endes eine oder mehrere Rippen (A1) in thermischem Kontakt mit mindestens einer der Verschlussplatten aufweisen.
  9. Wärmeleitung mit Kapillarpumpwirkung nach Anspruch 7 oder 8,
    wobei die Wärmeaustauschmittel (524) einen Fluidkreislauf in thermischem Kontakt mit mindestens einer der Endplatten umfassen, wobei der Kreislauf aus einer strukturierten Platte (526) gebildet ist, so dass Kanäle (528) begrenzt werden, wobei die Kanäle (528) durch die Verschlussplatte und eine zusätzliche Verschlussplatte (530) verschlossen sind, wobei die Wärmeaustauschmittel ferner Mittel (532) zur Versorgung des Fluidkreislaufs mit Wärmeüberträgerfluid umfassen.
  10. Wärmerohr mit Kapillarpumpwirkung nach einem der Ansprüche 1 bis 9, wobei mindestens eine der Endplatten eine größere Oberfläche als die Zwischenplatten in einer Richtung quer zur Stapelung aufweist, so dass Wärmediffusoren (120) gebildet werden.
  11. Verfahren zur Herstellung eines Wärmerohrs mit Kapillarpumpwirkung nach einem der vorstehenden Ansprüche, wobei das Verfahren ausgehend von Platten mit gegebenen Außenabmessungen umfasst:
    - Ausbilden mindestens einer Öffnung in jeder der Platten,
    - Stapeln der Platten, so dass die Öffnungen einen Kanal begrenzen und mindestens drei Zwischenplatten mindestens eine Nut begrenzen, die sich zwischen dem ersten Ende und dem zweiten Ende erstreckt, wobei die Stapelung so erfolgt, dass von den drei Zwischenplatten (14, 16) eine zwischen den beiden weiteren Zwischenplatten angeordnet ist und in mechanischem Kontakt mit den beiden weiteren Zwischenplatten steht, und dass mindestens ein Rand der Öffnung der zwischen den beiden weiteren Zwischenplatten (214) angeordneten Zwischenplatte (216) den Nutgrund mindestens einer Nut (210) in Richtung der Ebene bildet, wobei jede Seite der Nut in Richtung der Stapelung durch eine andere Zwischenplatte definiert ist als die Zwischenplatte, die den Nutgrund der Nut in Richtung der Ebene definiert,
    - Anordnen von Verschlussplatten an den Enden der Stapelung in Richtung der Stapelung,
    - Verfestigen der genannten Platten, so dass eine dichte Hülle begrenzt wird,
    - teilweises Füllen des Kanals mit einem Fluid in flüssiger Form und dichtem Verschließen des Kanals.
  12. Herstellungsverfahren nach Anspruch 11,
    wobei die Platten einen Kern aus Aluminiumlegierung und an ihren Außenflächen eine eutektische Aluminiumlegierung mit einem niedrigeren Schmelzpunkt als dem der Kern-Aluminiumlegierung aufweisen und wobei das Verfestigen durch eutektisches Löten erhalten wird.
EP19168582.5A 2018-04-11 2019-04-11 Wärmeleitrohr mit kapillarpumpensystem mit verbesserter funktionsweise Active EP3561428B1 (de)

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FR1853173A FR3080171A1 (fr) 2018-04-11 2018-04-11 Caloduc a pompage capillaire a fonctionnement ameliore

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CN111757634B (zh) * 2019-03-29 2023-11-14 台达电子工业股份有限公司 热传递装置
CN113301777B (zh) * 2021-04-26 2022-12-02 江西新菲新材料有限公司 均热板及均热板的制备方法、电子设备
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.

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US7051793B1 (en) * 1998-04-20 2006-05-30 Jurgen Schulz-Harder Cooler for electrical components
US6843308B1 (en) * 2000-12-01 2005-01-18 Atmostat Etudes Et Recherches Heat exchanger device using a two-phase active fluid, and a method of manufacturing such a device
JP5455503B2 (ja) * 2009-08-11 2014-03-26 モレックス インコーポレイテド 熱輸送ユニット、電子機器

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FR3080171A1 (fr) 2019-10-18

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