US20140083653A1

US20140083653A1 - Vapor-Based Heat Transfer Apparatus

Info

Publication number: US20140083653A1
Application number: US13/742,582
Authority: US
Inventors: Roger S. Kempers; Simon J. Kerslake; Lucius C. Akalanne; Todd R. Salamon
Original assignee: Individual
Current assignee: Individual
Priority date: 2012-09-26
Filing date: 2013-01-16
Publication date: 2014-03-27
Also published as: EP2713132A1

Abstract

A vapor-based heat transfer apparatus comprising a hollow structure and a working liquid within the hollow structure, wherein the structure is made of a thermally conductive polymer. In some embodiments the apparatus comprises a vapor chamber. In some other embodiments, the apparatus comprises a vapor chamber, heat pipe and a heat sink.

Description

CROSS-REFERENCE TO RELATED APPLICATION

This application claims the benefit of European Patent Application No. 12306167.3, filed by Kempers, et al., on Sep. 26, 2012, entitled “Vapor-Based Heat Transfer Apparatus,” commonly assigned with this application and incorporated herein by reference.

TECHNICAL FIELD

This application is directed, in general, to heat transport components and particularly those employing two-phase heat transport loops.

BACKGROUND

Vapor chambers and heat sinks are used in structures employed for cooling electronically operated devices. Typically a vapor chamber is a closed structure having an empty space inside within which a liquid is provided. Vapor chambers are typically passive, two-phase (liquid-vapor) heat transport loops that are used to spread heat from relatively small, high heat-flux sources to a region of larger area where the heat can be transferred elsewhere at a significantly lower heat-flux. Heat sinks are widely known in the related art. In a typical heat sink in operation, heat is conducted from the base of the heat sink to an array of extended surfaces (so-called fins) where it is ultimately transferred to the surrounding air.

SUMMARY

One aspect provides a vapor-based heat transfer apparatus. In one embodiment, the apparatus includes: (1) a hollow structure made of a thermally conductive polymer and (2) a working liquid within the hollow structure.

BRIEF DESCRIPTION

Reference is now made to the following descriptions taken in conjunction with the accompanying drawings, in which:

FIGS. 1A and 1B are exemplary schematic representations of a vapor chamber according to some embodiments of the disclosure wherein the vapor chamber is shown assembled to a heat sink and heat source;

FIGS. 2A and 2B are exemplary schematic representations of a vapor chamber and heat sink according to some embodiments of the disclosure wherein the vapor chamber is shown assembled to a heat source;

FIG. 3 is an exemplary schematic representation another embodiment of the disclosure wherein the vapor chamber is shown assembled to a heat source;

FIGS. 4A, 4B and 4C are exemplary schematic representations of a portion of a vapor chamber heat sink according to some embodiments of the disclosure wherein the vapor chamber is shown assembled to a heat source;

FIGS. 5A and 5B are exemplary schematic representations of another embodiment of the disclosure wherein the vapor chamber is shown assembled to a heat source;

FIG. 6 is an exemplary schematic representation of another embodiment of the disclosure wherein the vapor chamber is shown assembled to a heat source; and

FIGS. 7A and 7B are exemplary schematic representations of another embodiment of the disclosure wherein the vapor chamber is shown assembled to a heat source.

DETAILED DESCRIPTION

In a typical vapor chamber heat is conducted from a heat source to a heat sink through an evacuated chamber containing a working fluid such that the internal pressure of the chamber is at the saturated vapor pressure of the working fluid. In operation, the working fluid evaporates or boils as a consequence of receiving heat from the heat source and then re-condenses on the colder (typically upper) regions of the chamber at a nearly identical temperature (i.e., the corresponding saturation temperature). The condensate liquid is caused to flow back, often assisted by gravity, in proximity of the heat source inside the chamber. Typically a wicking structure is incorporated into the evaporator (vapor-generating) side of the vapor chamber which may serve to enhance the liquid flow back to the heat source for re-evaporation. The net effect is efficient heat transport from the evaporator section of the vapor chamber to the condenser section of the vapor chamber; this is due to the convective transport of the vapor, and results in a very large effective vapor chamber thermal conductivity, often 10 to 100 times that of copper.
Typically the low heat flux side of vapor chambers are coupled to a heat sink to more effectively reject the heat to a surrounding fluid medium (usually air) via convection (either natural or forced).
As it is known, electronic components are experiencing continued increase in device density which in turn typically gives rise to an increase in heat generation within the equipment they are used. This increase in heat generation requires more efficient cooling systems.
One way vapor chambers and heat sink effectiveness may be increased is by making the devices larger in size, which may have the effect of both lowering the heat sink thermal resistance and increasing the surface area for conduction or convection at the free surfaces. However, this may result in larger and heavier devices, which is a significant drawback. Another approach may be to use a higher conductivity metal (e.g., copper, gold or silver), however typically, higher-conductivity materials correspond to both higher density (increased weight) and greater cost.
It is therefore desired to provide a vapor-based heat transfer apparatus which while present improved effectiveness (i.e., have a lower thermal resistance) have, as much as possible, a light weight. The vapor-based heat transfer apparatus may be a vapor chamber or a vapor chamber heat sink, or a heat pipe.
Some embodiments of the present disclosure relate to a vapor-based heat transfer apparatus using a thermally conductive polymer as the solid enclosure thereof. The inventors have realized that the heat spreading and corresponding high thermal effectiveness of these devices are primarily due to the vaporization and condensation of the working fluid occurring internally. Therefore, the thermal conductivity of the outer enclosure may play a relatively minor role on the overall system performance. Furthermore, by using a relatively thin and thermally conductive polymer, good thermal performance can still be achieved while minimizing weight (e.g., as opposed to using metals).
Herein, a thermally conductive polymer is to be understood as a polymer matrix loaded with conductive particle filler materials to improve the overall bulk thermal conductivity of the base polymer. Examples of such thermally conductive polymers include but are not limited to polymers such as liquid crystalline polymers (LCP), polyamides, polycarbonate, polypropylene, polyphthalamide, polyphenylene sulfides or thermoplastic elastomers. Filler particles may include, but are not limited to, a range of metal or ceramic particles such as aluminum oxide, boron nitride, silver or variations of carbon-based graphite or graphene particles. It is to be noted that within the context of the present disclosure, the term “particle” may—in addition to its common meaning relating to small pieces, bodies or the like—be understood to encompass fibers.
Accordingly, some embodiments of the disclosure feature a vapor-based heat transfer apparatus including a hollow structure and a working liquid within the hollow structure, wherein the structure is made of a thermally conductive polymer. According to some specific embodiments the apparatus includes a vapor chamber. According to some specific embodiments, the apparatus includes a vapor chamber and a heat sink such that the at least a portion of the heat sink includes a conductive polymer material.
In the following, examples of embodiments are provided related to vapor chambers and/or vapor chamber and heat sinks. This however is only exemplary. Indeed, those skilled in the art will realize that embodiments of the invention are not limited to only vapor chambers or vapor chambers and heat sinks and that other vapor-based heat transfer apparatus such as for example polymer heat pipes may also be considered within the scope of the present disclosure.
Referring to FIGS. 1A and 1B exemplary schematic representations of a vapor chamber according to some embodiments of the disclosure are provided where the vapor chamber is shown assembled together with a heat sink. The assembly 100 of FIG. 1A includes a vapor chamber 110 and a heat sink 120. The vapor chamber 110 includes a structure including walls 111, 112, 113 and 114 (111-114). The walls 111-114 define an enclosed space 115 which is hollow. Inside the hollow space 115 a working liquid 116 is provided. The working liquid may be for example water, acetone, methanol, ammonia or any number of refrigerants or liquid salts or liquid metals, depending on desired operating characteristics. According to the embodiments of the disclosure, the vapor chamber 110 is made of thermally conductive polymer.
The heat sink 120 includes an array of extending bodies, or fins, 121 which serve for transporting heat away from the vapor chamber and dissipating the heat in the surrounding ambient environment, which may be air. In the illustrative example of FIGS. 1A and 1B the vapor chamber is further shown to be in assembled position over a heat source 130 (an electronic device which in operation generates heat and which is intended to be cooled off).
FIG. 1B illustrates in further detail, a portion represented by reference R—of the assembly of FIG. 1A in heat transferring operation. In FIG. 1B, like elements have been given like reference numerals as those of FIG. 1A.
Referring to FIG. 1B, the heat source 130 is shown in thermal contact with the vapor chamber 110. In operation, heat is transferred from the heat source 130 to the vapor chamber 110 through the wall 111 of the vapor chamber as schematically shown by arrows A.
The heat received by the vapor chamber 110 causes the liquid 116 inside the vapor chamber to evaporate and the vapor may then move toward another (e.g., upper) wall 113 of the vapor chamber 110 as schematically shown by arrows B. Upon arrival at the wall 130, the vapor condenses on the surface 117 of the wall 113 and is converted back to liquid. Heat is thereby transferred from the wall 113 of the vapor chamber to the heat sink 120 as shown by arrows C which in turn is dissipated to the ambient environment using fins 121. After condensation, the liquid returns back to the side adjacent to the heat source 130 to undergo another evaporation-condensation cycle as described above.
As the material of the vapor chamber is made of a thermally conductive polymer, heat is effectively and satisfactorily transferred from the heat source to the vapor chamber and also from the vapor chamber to the heat sink. In this manner, the thermal effectiveness of the devices is ensured by the vaporization and condensation of the working fluid occurring inside the vapor chamber while the weight of the device is maintained low as compared to known solutions where metal is typically used.
Furthermore, by using a relatively thin thermally conductive polymer, a good thermal performance may be achieved while weight is still further minimized.
Another significant advantage of the solution proposed herein over the known solutions is the possibility of constructing the vapor chamber or extended vapor chamber heat sink (as will be described further below) using an injection molded high-conductivity plastic. It is to be noted that the use of plastics in conventional-design vapor chambers or vapor chamber and heat sinks is generally considered as an option that would significantly undermine the performance of the resulting device (due to the relatively low thermal conductivity of even the optimum conductive plastics). Therefore, it may be possible that a person skilled in the related art, following a typically predominant general opinion would discard the use of plastics for such constructions. In contrast, in the present disclosure the contribution of the solid phase thermal conductivity has little effect on the thermal performance of the vapor chamber or the vapor chamber and heat sink as a whole due to the highly effective heat transport of the vapor chamber region.
Although the level of heat transfer may vary from low heat flux regions (e.g., the condenser section) to high heat flux regions (e.g., near the heat source), it may be possible to select design parameters and materials such that the overall heat transfer response of the device meets the specific requirements of a particular application.
In this regard it may be said that in low heat transfer regions a reasonably thermally conductive polymer material may be suitable for heat transfer, as the thermal resistance across such a material would not generate too large of a temperature drop due to the low heat flux. On the other hand, in the high heat flux regions, the use of some metal may be appropriate to contribute to improving the heat transfer.
Therefore, estimation may be made to determine what a reasonable range of polymer thermal conductivities would be for the device to provide a desired heat transfer response. For example, in a device with a condenser area being 20 times that of the evaporator area, a thermally conductive polymer that presents a thermal conductivity of 1/20^thof that of a metal (e.g., copper) would have a similar temperature drop across both the evaporator and condenser walls.
The vapor chamber may preferably include a wick structure 119 to enhance liquid flow to the vicinity of the heat source 130 and may contribute to further assisting the evaporation and boiling of the liquid.
FIGS. 2A and 2B are exemplary schematic representations of a vapor chamber heat sink according to some embodiments of the disclosure. In the example of FIGS. 2A and 2B, like elements have been given like reference numeral as those of FIGS. 1A and 1B. Here also, FIG. 2B shows in further detail a portion R of the assembly of FIG. 2A.
The structure and the mode of operation of the assembly shown in FIGS. 2A and 2B are in many aspects similar to those of the example of FIGS. 1A and 1B, with a difference that in the example of FIGS. 2A and 2B, the vapor chamber 110 is integrated into the base 120 a of the heat sink 120. As shown in FIGS. 2A and 2B, the fins 121 of the heat sink 120 are hollow, thereby providing additional internal space 115A for the vapor and therefore additional surface for liquid condensation thereby improving heat transfer. This embodiment therefore has the advantage of allowing for an enhanced spreading of the heat, which may include the body of the vapor chamber 110 (similar to the example of FIGS. 1A and 1B) as well as the entire domain of extended surfaces of the fins 121 of the heat sink 120.
Therefore while the working fluid is evaporated in vicinity of the heat source 130, the working fluid 116 is allowed to re-condense in the full (or any available) length and height of each fin (or pin or any other extended surface used for heat dissipation). Furthermore, this approach allows for effectively removing or at least reducing the contribution of fin thermal resistance (which can be considerable) to the total resistance of the heat sink and making the entire heat sink a contiguous vapor chamber.
As this solution effectively creates a hollow heat sink, the entire inner core of the overall structure becomes a single vapor chamber capable of operating at a near isothermal condition due to the evaporation and subsequent condensation of the working fluid from hot regions to cold regions in the chamber. This effect would improve considerably the heat spreading not only through the base of the heat sink but also into the fins thereby dramatically increasing the overall effectiveness of the heat sink while significantly reducing its weight (as compared to known solutions).
From the standpoint of thermal effectiveness, the inner walls of this vapor chamber or vapor chamber heat sink may be made thin, for example less than about 1 mm, to limit their possible contribution to the thermal resistance of the device and to allow adequate internal space for the condensate to flow.
It is to be noted that the solution according to the embodiments of FIGS. 2A and 2B is in some aspects contrary to a conventional conduction heat sink (or indeed a conventional vapor chamber heat sink) where in such conventional solutions an incentive lies in providing thicker fins to reduce contribution of fin thermal resistance.
Similar to what was mentioned in relation to the embodiment of FIGS. 1A and 1B, this embodiment may also allow for the construction of the vapor chamber and the vapor chamber and heat sink using an injection molded high-conductivity plastic and thus encompasses similar advantages. The embodiment of FIGS. 2A and 2B also allows for a number of novel construction embodiments, at least some of which are described in the following.
The use of an injection molded plastic to create a vapor chambers or extended vapor chamber heat sink would allow for the construction of thin walls that would otherwise be impossible or at least very difficult to form by other high-volume processes such as metal casting or extrusion. Additionally, injection molding may allow for at least certain parts of the complex extended vapor chamber side of the heat sink to be created as one piece, thereby decreasing the otherwise more intensive construction process of conventional vapor chamber heat sinks. For example, the extended fins and the top portion of the vapor chamber may be made in one piece. The base of the vapor chamber adjacent to the heat source may be another piece and the two pieces may then be easily bonded together.
Depending on the type of the thermally conductive polymer employed in the construction of the chamber, small amounts of working fluid may be absorbed into the polymer material. Similarly, under the low pressure conditions the chemical interactions within the polymer could result in out-gassing of non-condensable gasses that may inhibit or degrade the performance of the device. Both of these phenomena may be overcome by employing a layered construction approach as shown in the embodiment of FIG. 3.
FIG. 3 is in many aspects of structure and operation similar to FIG. 2B in both of which only a portion R of the assembly of the vapor chamber, heat sink and the heat source is shown. In FIG. 3 like elements have been given like reference numerals as those of FIG. 2B. However, FIG. 3 further illustrates the presence of a layer 140 which is intended to block the absorption of the fluid as well as the out-gassing of the gasses as described above. According to the embodiment of FIG. 3, the overall polymer enclosure or at least a part thereof, including the inner walls of the vapor chamber 110 and those of the fins 121, is lined with a thin hermetic layer 140 adapted to act as an impermeable barrier to mass transport to or from the polymer enclosure. This layer may be applied through electroplating or chemical vapor deposition or other known techniques.
As an alternative solution for providing such blocking effect, use may be made of pure polymer or epoxy layer on either the outside or inside of the vapor chamber to improve its hermeticity.
In some of the embodiment where the fins of the heat sink also act as condensation walls (e.g., FIG. 2A or 2B), vapor may condense on the fins' inner walls. During the condensation process, liquid droplets may be formed on said inner walls that could potentially bridge the gap between the inner walls in this region and could result in an accumulation of liquid in this space. This situation is schematically illustrated in FIG. 4A. In FIGS. 4A, 4B and 4C, a portion of a fin 121 is shown where the fin 121 has a hollow inner space 115A in accordance with the embodiments described with reference to FIGS. 2A, 2B and 3. The fin 121 has walls 122 and 123. As shown in FIG. 4A, liquid bridges 124 are formed between the inner surfaces of the walls 122 and 123. Such accumulation of droplets may be undesirable as it may block the passage of vapor to other regions of the fins or the return of the liquid back to the liquid base adjacent to the heat source (not shown) or it may increase thermal resistance within the fins 121. To overcome this situation, use may be made of known surface treatments which provide a certain level of hydrophobicity to the regions concerned thereby promoting the flow of liquid droplets from the surface and minimizing the thermal resistance associated with a condensation film on the inner surface of the walls 122, 123. By using such surface treatment, the droplets would not accumulate on the inner surfaces of the walls and may leave such surfaces before an accumulation is produced as shown in FIG. 4B. Alternatively, depending on the specific design requirements, a hydrophilic surface may be used thereby causing the droplets to adhere along a relatively extended inner surface of the walls 122, 123, thereby limiting their propensity to form liquid bridges on the opposite wall as illustrated in FIG. 4C. An example of a hydrophobic material is Teflon® and one for a hydrophilic material is glass.
Briefly, hydrophobicity or hydrophilicity typically depends on the solid/liquid combination and the surface structure of the solid (i.e., the presence of microstructures to encourage hydrophobicity). More specifically, hydrophilic surfaces have the property that water has an affinity for the surface, thus water will readily wet and spread onto a hydrophilic surface. Hydrophobic surfaces, in contrast, are such that water does not have a significant affinity for the surface, and will instead minimize its surface contact area with the surface by forming droplets. Hydrophilicity and hydrophobicity are controlled by the inherent surface energies associated with the interaction of the solid, liquid and vapor phases. Knowledge of the relative magnitudes of the various solid/liquid, solid/vapor and liquid/vapor surface energies allows one to determine if a fluid and solid will interact in a hydrophilic or hydrophobic, e.g., wetting or non-wetting, manner. Surface roughness applied to a hydrophilic/hydrophobic surface will typically enhance its character, e.g., a hydrophilic surface may become super-hydrophilic, and a hydrophobic surface may become super-hydrophobic.
Since vapor chambers typically operate at pressures different from atmospheric pressure, pillars, ribs or other internal solid structures (hereinafter referred to as support elements) may, in various embodiments, be incorporated into the internal structure of the vapor chamber or the vapor chamber and the heat sink to ensure that the heat sink and/or the vapor chamber remain rigid and structurally sound while allowing for the thickness of the enclosure to be reduced for thermal optimization. FIG. 5A shows an exemplary schematic representation of an assembly of a vapor chamber 110, a heat sink 120 and a heat source 130. The embodiment shown in FIG. 5A is in many structural and operational aspects similar to that of FIG. 2A, 2B or 3 and like elements therein have been given like reference numerals as FIGS. 2A, 2B and 3. However, FIG. 5A further illustrates the use of support elements 150 inside the vapor chamber 110 and/or the fins 121 to enhance rigidity as discussed above.
In some embodiments, additional structural elements may be provided inside the fins 121 designed to direct or enhance the liquid condensate flow returning back to the liquid base in the vapor chamber (e.g., to the wick structure and/or heat source). Advantageously such additional elements may be the same as the support elements as described above. Therefore, in some embodiments, the support elements 150 may be used for both purposes described above, namely that of providing structural rigidity to the overall structure and that of directing the condensed liquid back to the vapor chamber.
FIG. 5B shows a fin 121 in a cross-sectional view along the cross-section represented by broken line A-A in FIG. 5A. As shown in FIG. 5B, support elements 150 may be positioned inside the fins 121 to direct the liquid drops 160. Preferably the support elements may be provided in a shape and/or position to assist the flow of the drops 160 back to the vapor chamber 110. For example in FIG. 5B, the support elements are provided with a certain slope that, when fin is positioned vertically, direct the liquid drops 160 downward as shown by arrows in FIG. 5B.
In some embodiments the thermally conductive polymer used in the vapor chamber or the vapor chamber heat sink may include metal inserts incorporated or over-molded into the polymer structure at the location where the heat source is brought into thermal contact with the vapor chamber. This embodiment may help to improve heat transfer from the heat sink into the vapor chamber and the wick structure (if a wick structure is used). Furthermore, such metal insert may allow for more robust heat source attachment embodiments, such as the use of threaded holes or studs or the direct soldering or welding of such devices directly to the vapor chamber or heat sink. In addition, a metal wick structure may, in one embodiment, be soldered directly to such metal inserts to improve heat transfer into the wick inside of the vapor chamber.
If a wick structure is used, which may often be the case, the wick structure itself may be one of several existing technologies depending on the design requirements and liquid transport needs of the vapor chamber or vapor chamber heat sink. Some non-limiting examples of wick structure include porous sintered metal wicks, layers of woven metal wire screen mesh or a grooved wick. For smaller vapor chambers or heat sinks, grooved wicks may be an attractive embodiment and may be incorporated directly into the heated base of the vapor chamber during the process of molding the plastic.
In some embodiments a hybrid wick structure may be used. FIG. 6 shows an exemplary schematic representation of a portion of a vapor chamber R within which a hybrid wick structure is used. In FIG. 6, like elements have been given like reference numerals as those of FIGS. 1A and 1B. The hybrid wick structure 119 includes a first portion made of porous structure 119 a which may be made of a sintered metal or a screen mesh wick. The hybrid wick structure further includes a second portion with grooves 119 b such that the groove are embedded in the body of the vapor chamber wall 111 or in the base of the heat sink (not shown).
According to still a further embodiment, the wick structure itself may be made of sintered plastic material. This embodiment is made possible due to the use of a thermally conductive polymer as material for the vapor chamber as discussed above. FIGS. 7A and 7B show a schematic representation of a portion of a vapor chamber R within which sintered plastic is used to form the wick structure. In FIGS. 7A and 7B, like elements have been given like reference numerals as those of FIGS. 1A and 1B. According to this embodiment, particles 170 a of the thermally conductive polymer are provided inside the vapor chamber 110. The particles 170 a are then heated to a temperature below their melting point or glass transition temperature. Atomic diffusion bonds the particles together forming a continuous (sintered) solid porous structure as shown in FIG. 7B by reference numeral 170 b which represents the particles of FIG. 7A but in porous structure form.
The initial particle size may be determined based on the required porosity and capillary requirements of the overall vapor chamber or vapor chamber heat sink. The sintered polymer wick 170 b may be manufactured in-situ of the vapor chamber heat sink and may further be sintered directly to the inner wall 111 of the vapor chamber (or the vapor chamber and heat sink) to improve heat transfer from the outer heat source 130 into the wick 170 b.
The overall assembly of the vapor chamber or the vapor chamber and heat sink may be made using known processes. For example, to create an enclosed chamber of a given design (be it a simple flat vapor chamber design or a more complex extended vapor chamber heat sink) the injection molded conductive polymer may be assembled from a minimum of two separately molded pieces. To provide an effective seal between these components, mechanical assembly using fasteners and a gasket material (such as an O-ring or a wet installed sealant or adhesive) may be used. Another alternative approach afforded by the use of a polymeric enclosure may be to use a compatible epoxy or adhesive to chemically bond the components together. Finally, a variety of plastic welding embodiments may also be amenable to joining these components.
The various embodiments disclosed herein can provide a significant increase in vapor chamber and vapor chamber heat sink effectiveness (performance) and decrease in weight as compared to known designs, resulting in increased reliability and functionality for the hardware employing such solution.
Those skilled in the art to which this application relates will appreciate that other and further additions, deletions, substitutions and modifications may be made to the described embodiments.

Claims

What is claimed is:

1. A vapor-based heat transfer apparatus, comprising:

a hollow structure made of a thermally conductive polymer; and

a working liquid within said hollow structure.

2. The apparatus as recited in claim 1 wherein said thermally conductive polymer is a high conductivity plastic.

3. The apparatus as recited in claim 1 wherein said hollow structure comprises inner walls covered, at least in part, with a hermetic layer.

4. The apparatus as recited in claim 1 wherein said hollow structure comprises inner walls covered, at least in part, with a pure polymer material or an epoxy layer.

5. The apparatus as recited in claim 1, further comprising one or more extended structures configured to dissipate heat from said apparatus to an ambient environment, said extended structure having a hollow interior space at least in a portion thereof and comprising an inner surface within said interior space, said surface presenting a hydrophobic property.

6. The apparatus as recited in claim 1, further comprising one or more extended structures configured to dissipate heat from said apparatus to an ambient environment, said extended structure having a hollow interior space at least in a portion thereof and comprising an inner surface within said interior space, said surface presenting a hydrophilic property.

7. The apparatus as recited in claim 1, further comprising an internal element configured to provide rigidity to said structure of said apparatus.

8. The apparatus as recited in claim 1, further comprising an internal element configured to direct a direction of said flow of said liquid condensate.

9. The apparatus as recited in claim 1 wherein said thermally conductive material comprises at least one metal insert.

10. The apparatus as recited in claim 9, further comprising a wick structure soldered or bonded to said at least one metal insert.

11. The apparatus as recited in claim 10 wherein said wick structure comprises:

a first portion made of a porous structure; and

a second portion having grooves.

12. The apparatus as recited in claim 1, further comprising a wick structure made of plastic material particles.

13. The apparatus as recited in claim 1 wherein said hollow structure is operable to act as a vapor chamber.

14. The apparatus as recited in claim 1, further comprising:

a vapor chamber; and

a heat sink, at least a portion said heat sink comprising a conductive polymer material.

15. The apparatus as recited in claim 1, further comprising a heat pipe.