Patent Publication Number: US-2023138653-A1

Title: Evaporator assemblies, vapor chambers, and methods for fabricating vapor chambers

Description:
TECHNICAL FIELD 
     The present specification generally relates to vapor chambers and, more particularly, to vapor chambers having low thermal resistance and high heat dissipation. 
     BACKGROUND 
     Heat generating devices, such as motors, power electronic devices, and microprocessors, generate significant heat that should be removed to ensure that the heat generating devices operate below their maximum operating temperature. As power demands increase and the size of heat generating components decreases, it becomes challenging to remove heat flux from the heat generating devices. 
     Accordingly, a need exists for alternative cooling devices for removing heat flux from heat generating devices. 
     SUMMARY 
     In one embodiment, an evaporator assembly for a vapor chamber includes an evaporator surface, an array of posts extending from the evaporator surface, and an array of vapor vents within the evaporator surface. Each vapor vent of the array of vapor vents is configured as a depression within the evaporator surface. The evaporator assembly further includes a porous layer disposed on the evaporator surface, the array of posts, and the array of vapor vents. 
     In another embodiment, an assembly includes an evaporator assembly and a condenser plate. The evaporator assembly includes an evaporator surface, an array of posts extending from the evaporator surface, and an array of vapor vents within the evaporator surface. Each vapor vent of the array of vapor vents is configured as a depression within the evaporator surface. The evaporator assembly further includes a porous layer disposed on the evaporator surface, the array of posts, and the array of vapor vents. The condenser plate includes a condenser surface, wherein the condenser surface is bonded to a top surface of the array of posts such that the evaporator assembly and the condenser plate define a vapor chamber. 
     In yet another embodiment, a method of fabricating a vapor chamber includes forming an array of posts and an array of vents in an evaporator surface, applying a metal powder including metal particles to the evaporator surface, the array of posts, and the array of vents, sintering the metal powder to form a porous layer, and bonding a condenser surface of a condenser plate to a top surface of the array of posts. 
     These and additional features provided by the embodiments described herein will be more fully understood in view of the following detailed description, in conjunction with the drawings. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The embodiments set forth in the drawings are illustrative and exemplary in nature and not intended to limit the subject matter defined by the claims. The following detailed description of the illustrative embodiments can be understood when read in conjunction with the following drawings, where like structure is indicated with like reference numerals and in which: 
         FIG.  1 A  schematically depicts a top perspective view of an example evaporator assembly having an evaporator surface with an array of posts and array of vents according to one or more embodiments described and illustrated herein; 
         FIG.  1 B  schematically depicts a top perspective view of an example post of the evaporator assembly of  FIG.  1 A ; 
         FIG.  2    schematically depicts a bottom perspective view of an example condenser plate having a condenser surface according to one or more embodiments described and illustrated herein; 
         FIG.  3    schematically depict a cross-sectional view of a vapor chamber according to one or more embodiments described and illustrated herein; 
         FIG.  4    schematically depicts an example evaporator surface having an array of posts and an array of vapor vents wherein a distance between adjacent posts and a distance between adjacent vapor vents vary across the evaporator surface according to one or more embodiments described and illustrated herein; 
         FIG.  5    schematically depicts an example evaporator surface having an array of posts and an array of vapor vents wherein a size of individual posts and a size of individual vapor vents vary across the evaporator surface according to one or more embodiments described and illustrated herein; 
         FIG.  6    graphically depicts plots of total thermal resistance as a variation of power for four different vapor chamber designs according to one or more embodiments described and illustrated herein; 
         FIG.  7    graphically depicts plots of heater temperature as a variation of power for the four different vapor chamber designs of  FIG.  6    according to one or more embodiments described and illustrated herein; 
         FIG.  8    graphically depicts plots of through plane thermal resistance as a variation of power for the Thur different vapor chamber designs of  FIG.  6    according to one or more embodiments described and illustrated herein; and 
         FIG.  9    graphically depicts a flowchart of an example method for fabricating a vapor chamber according to one or more embodiments described and illustrated herein. 
     
    
    
     DETAILED DESCRIPTION 
     Referring generally to the appended figures, embodiments of the present disclosure are directed to cooling devices configured as a vapor chamber for removing heat flux from a heat generating device, such as an electronic device. Electronic devices, such as microprocessors and power electronic switching devices (“power electronic devices”), generate significant heat that should be removed to maintain the electronic devices below their maximum operating temperature. Electronic devices that operate above their maximum operating temperature are at risk of failure. Cooling devices may be used to remove heat flux to keep the electronic device (or other heat generating device, such as a motor) below its maximum operating temperature. 
     In electrified vehicles, wide band gap (WBG) devices such as silicon carbide may replace traditional silicon-based power semiconductors due to their low power loss and high efficiency characteristics. In addition, WBG devices dissipate higher heat fluxes (e.g., greater than 1 kW/cm 2 ) and operate at high temperature exceeding 473 K. The high temperature operation of WBG devices provide larger thermal budget to design a lower cost and compact cooling systems such as air cooling. To achieve a compact and high-performance air-cooling system, the heat spreading from the heat source to the heat sink plays a key role. 
     A vapor chamber is a cooling device that removes heat flux h a phase change of a cooling fluid from a liquid to a gas. Typically vapor chambers are a closed system whereby liquid cooling fluid is present on an evaporator surface that receives heat flux from the heat generating device. This liquid cooling fluid raising in temperature until its boiling point is reached when it evaporates into gas and moves toward a condenser surface. The condenser surface is cooler than the evaporator surface such that it lowers the temperature of the gas so that it condenses into a liquid that moves back toward the evaporator surface. In some cases, a wicking structure may be provided to move the liquid cooling fluid toward the evaporator surface by capillary action. Traditionally, vapor chamber heat spreaders are used to efficiently spread the heat; however, their performance is limited up to a heat flux of less than about 500 W/cm 2  over a 1 cm×1 cm area. 
     A significant problem with vapor chambers is the phenomenon of dry out. Dry out occurs when the power of the heat generating device raises the temperature to such a degree that liquid cooling fluid cannot return to the evaporator surface quickly enough to cool the heat generating device. In effect, the evaporator surface “dries out” because no liquid cooling fluid is present. The causes the temperature of the heat generating device to raise above its maximum operating temperature. 
     Embodiments of the present disclosure provide a more efficient vapor chambers that significantly raise the dry out temperature of the vapor chamber and thus significantly raise the maximum operating power of the heat generating device. In embodiments an array of porous posts connect an evaporator surface with a condenser surface to provide a wicking path for returning condensed, liquid cooling fluid to the evaporator surface from the condenser surface. Further, an array of vapor vents are disposed within the evaporator surface that provide additional nucleation sites and therefore more efficient evaporation of the cooling fluid. The combination of the array of posts and the array of vapor vents enables heat generating devices to operate at elevated temperatures with minimized risk of dry out, such as, without limitation, operating power greater than 600 W. Additionally, the vapor chambers described herein provide low thermal resistance. Particularly, tested vapor chambers of the embodiments described herein dissipate the highest heat flux of 589 W/cm 2  and provide the lowest total thermal resistance of 0.28 K/W among all vapor chamber designs that were evaluated. 
     Various embodiments of evaporator assemblies, power electronic assemblies, and methods for fabricating a vapor chamber are described in detail below. 
     Referring now to  FIG.  1 A , an example evaporator assembly  110  that may be used in conjunction with a condenser plate for forming a vapor chamber is schematically illustrated. The evaporator assembly  110  is configured as an evaporator plate having an evaporator surface  111  and a heat receiving surface  117 . The evaporator assembly  110  is fabricated from a thermally conductive material, such as, without limitation, copper. The heat receiving surface  117  receives a heat receiving device (not shown), such as a power electronic device. The power electronic device may be a power switching device, such as a power metal-oxide-semiconductor field-effect transistor (MOSFET), power transistor, power insulated-gate bi-polar transistor (IGBT), and the like. The power electronic device may be a WBG device comprising, without limitation, silicon carbide. It should be understood that embodiments are not limited by any electronic device or heat generating device. 
     The example evaporator assembly  110  includes a perimeter surface  116  that surrounds the evaporator surface  116 . As described in more detail below, the perimeter surface  116  may be coupled to a perimeter surface of a condenser plate to form a vapor chamber. The evaporator assembly  110  further include an input port  118  for providing cooling fluid to the vapor chamber. The input port  118  may include a valve to close the vapor chamber during operation, thereby providing a closed system. 
     The evaporator surface  111  is offset from the perimeter surface  116  in a negative system vertical direction (i.e., negative z-axis direction) so that a vapor chamber may be formed when the evaporator assembly  110  is coupled to a condenser plate. In the example embodiment, the evaporator assembly  110  further includes a porous perimeter ledge  115  that is configured to receive a porous condenser surface of a condenser plate. It should be understood that in other embodiments, no perimeter ledge is provided. Rather, an entire perimeter wall is porous without a ledge present. 
     The example evaporator assembly  110  comprises an array of posts  112  that extend from the evaporator surface  111 . As described in more detail below, the array of posts  112  provide a wicking path for condensed cooling fluid to return to the evaporator surface  111 . The array of posts  112  are defined by a plurality of rows and a plurality of columns. The individual posts  112  of adjacent rows are offset from one another in the x-axis direction by an offset distance d 1 . The individual posts  112  of adjacent columns are offset from one another in the y-axis direction by an offset distance d 2 . The values for distances d 1  and d 2  are not limited by this disclosure and may depend on the overall dimensions of the cooling device. 
     The posts  112  are illustrated as being cylindrical in shape. However, embodiments are not limited thereto. For example, the posts  112  may be configured as rectangular pillars, or any other shape in cross section. Embodiments are further not limited by the size of the posts. In the cylindrical embodiment, as non-limiting examples, the diameter of the posts  112  may be 0.5 mm to 3 mm, 1 mm to 1.5 mm, or 1 mm. It should be understood that the diameter may be other values depending on the overall size of the cooling device. Further, the height of the array of posts  112  is not limited by this disclosure. Non-limiting heights include 0.5 mm to 5 mm, 1 mm to 4 min, 1.5 mm to 3 mm, or 2.5 mm. It should be understood that other heights may be utilized. 
     The evaporator surface  111  further includes an array of vapor vents  114  that are depressions within the evaporator surface  111  in the negative z-axis direction. As described in more detail below, the array of vapor vents  114  increase the efficiency of the vapor chamber and enable dissipation of high heat flux without dry out. Dimensions and shape of the vapor vents  114  are not limited by this disclosure. In the illustrated embodiment, the individual vapor vents  114  are circular in shape. However, embodiments are not limited to vapor vents  114  having a circular shape as other shapes are possible, such as rectangular, elliptical, triangular, or arbitrarily shaped. As non-limiting examples, the diameter of the individual vapor vents  114  may be 0.25 mm to 2 mm, 0.5 mm to 1.5 mm, or 1 mm. Other diameters may be utilized depending on the overall size of the cooling device. Non-limiting depths of the individual vapor vents  114  include 0.1 mm to 1 mm, 0.25 mm to 0.75 mm, or 0.5 mm. It should be understood that other depths may be used. 
     The individual vapor vents  114  of adjacent rows are offset from one another in the x-axis direction by an offset distance d 3 . The individual vapor vents  114  of adjacent columns are offset from one another in the y-axis direction by an offset distance d 4 . The values for distances d 3  and d 4  are not limited by this disclosure and may depend on the overall dimensions of the cooling device. The array of posts  112  and the array of vapor vents  114  are interlaced between each other. Accordingly, the array of posts  112  and the array of vapor vents  114  define a structure array, wherein each row of the structure array comprises alternating individual posts and individual vapor vents and each column of the structure array comprises alternating individual posts and individual vapor vents. Each individual vapor vent  114  is surrounded by four individual posts  112 . 
     The evaporator assembly  110  further includes a porous layer  119  disposed on the evaporator surface  111 , the array of posts  112 , and the array of vapor vents  114 . The porous layer  119  has a plurality of pores that act as a wicking structure to bring liquid cooling fluid back to the evaporator surface  111 . The thickness of the porous layer  119  defines the dimensions of the array of posts  112  and the array of vapor vents  114  described above. 
     Referring now to  FIG.  1 B , a close-up view of a post is depicted. Individual posts  112  of the array of posts  112  may be configured a pin  113  (e.g., a pin fin) that is coated with a porous layer  119 . Thus, the posts  112  are defined by a core that is a solid pin  113  and an outer, porous layer. The pins may be formed by any known or yet-to-be-developed process such as, without limitation, machining or chemical etching. For example, the array of posts  112  comprise an array of smaller dimeter pin fins and the porous layer  119  surrounding the array of pin  113  sets the overall diameter of the array of posts  112 . As a non-limiting example, each pin  113  may have a diameter of 0.5 mm, and the thickness of the porous layer  119  may be 0.5 mm to set a diameter of 1 mm for each post  112 . The thickness of the porous layer  119  is not limited by this disclosure. As non-limiting example, the thickness of the porous layer  119  may be 0.2 mm to 1 mm, 0.25 mm to 1 mm, or 0.5 mm. It should be understood that other thicknesses may be utilized. 
     In some embodiments, the porous layer  119  may be fabricated by applying a powder comprising metal particles, such as copper particles. The size of the metal particles dictates the size of the pores within the porous layer  119 . As a non-limiting example, the metal particles may have a diameter of 60 to 120 μm. After application of the powder of metal particles, the metal particles are sintered to form the porous layer  119  by raising the temperature of the evaporator assembly  110  above the sintering temperature of the metal particles (e.g., within a range of 750° C. and 1000° C. for copper particles). 
       FIG.  2    illustrates a condenser plate  120  having a condenser surface  122  and a cooling surface  125 . The condenser surface  122  may be surrounded by a condenser perimeter surface  124  that is configured to be coupled or otherwise contact the perimeter surface  116  of the evaporator  110 . Condenser surface  122  is defined by a porous layer that extends from the condenser perimeter surface  124 . The condenser surface  122  may also be formed by sintering metal particles (e.g., copper particles) as described above. The condenser surface  122  has a width, height, and depth to fit within the perimeter surface  116  of the evaporator assembly  110 . 
     To form the vapor chamber, the condenser surface  122  is positioned on the top of the array of posts  112  and the porous perimeter ledge  115 , if provided. After placement of the condenser plate  120  on the evaporator assembly  110 , the two components are then bonded together, such as by diffusion bonding. The bonding of these two components define a vapor chamber that may then be filled with the cooling fluid. 
     Referring now to  FIG.  3   , a cross-sectional view of an example assembly  100  including a cooling device  101  comprising a vapor chamber  128 , a heat generating device  130 , and a heat sink  140 . It is noted that  FIG.  3    is a simplified view for illustrative purposes only. Particularly, a row including only two posts  112  and three vapor vents  114  is shown. It should be understood that the rows of the cooling devices  101  disclosed herein may include many additions posts  112  and vapor vents.  114 . 
     As shown by  FIG.  3   , the posts  112  comprise a pin fin  113  surrounded by the porous layer  119 . As stated above, the pin fins  113  may be formed by machining the evaporator surface  111  or by chemical etching. Having posts  112  with a solid pin fin  113  core may reduce the thermal resistance between the condenser plate  120  and the evaporator assembly  110  over having the posts fabricated from only the porous layer, further improving the performance of the vapor chamber. 
     After the vapor chamber  128  is sealed by bonding the condenser plate  120  to the evaporator assembly  110 , cooling fluid is introduced to the vapor chamber  128  by the inlet port  118  ( FIG.  1 A ). During operation, the heat generating device  130 , which may be a power electronic device, for example, generates heat flux. Liquid cooling fluid present on the evaporator surface  111  and within the porous layer  119  receives the heat flux and rises in temperature to above its boiling point. The liquid cooling fluid begins to boil and change phase from liquid to vapor. The pores within the porous layer  119  provide nucleation sites for efficient boiling. The vapor cooling fluid rises up toward the condenser surface  122 , as shown by arrows A. 
     The heat sink  140  is attached to the cooling surface  125  of the condenser plate  120 . The heat sink  140  may be any cooling device, such as a finned heat sink, a thermal spreader, a liquid cooling device, and the like. The heat sink  140  removes heat flux from the condenser plate  120  to cool the vapor cooling fluid such that it condenses back into a liquid. The porous condenser surface  122  and the porous posts  112  wick the condensed liquid cooling fluid back toward the evaporator surface  111  as indicated by arrows B, where it is once again heated and turned into a vapor. 
     The vapor vents  114  reduces the resistance for the vapor to escape the evaporator surface  111 . The vapor vents  114  provide an easier location for nucleation bubbles to escape the porous layer  119  at the evaporator surface  111 . Thus, the vapor vents  114  allow the vapor to vent toward the condenser surface  122 . 
     The size, shape, and/or density of the posts  112  and/or the vapor vents  114  may be varied across the evaporator surface  111  to address local hotspots. For example, the size, shape, and/or density of the posts  112  and/or vapor vents  114  directly above the heat generating device  130  may be different than the size, shape, and/or density of the posts  112  and/or vapor vents  114  away from the heat generating device  130 . The size, shape and/or density of the posts  112  and/or vapor vents  114  may vary across the evaporator surface  111  in any manner. 
       FIG.  4    illustrates a partial view of an example evaporator surface  211  wherein centrally located adjacent posts  212  have a spacing dpi and centrally located adjacent vents  214  have a spacing dv 1 . However, adjacent posts  212  further toward the perimeter of the evaporator surface  211  have a spacing dp 2  and adjacent vapor vents  214  further toward the perimeter of the evaporator surface  211  have a spacing dv 2 . In the illustrated example, dp 1  is greater than dp 2  and dv 1  is greater than dv 2 . As an example, the density of the posts  212  and the vapor vents  214  may be directly above the heat generating device than areas outside of the heat generating device. 
       FIG.  5    illustrates a partial view of an example evaporator surface  311  wherein a size of the posts  312  and vapor vents  314  vary. Centrally adjacent located posts  312  have a diameter dia p1  and centrally located adjacent vapor vents  314  have a diameter dia v1 . However, adjacent posts  312  further toward the perimeter of the evaporator surface  311  have a diameter dia p2  and adjacent vapor vents  314  further toward the perimeter of the evaporator surface have a diameter dia v2 . In the illustrated example, dia p1  is greater than dia p2  and dia v1  is greater than dia v2 . It should be understood that in other embodiments, dia p1  is less than dia p2  and dia v1  is less than dia v2 . 
     To assess the performance of the vapor chamber, two set of experiments were conducted. One experiment measure total thermal resistance of the vapor chamber in an air-cooling test, and the second experiment extracted the through-plane thermal resistance of the vapor chamber itself. A vapor chamber having machined posts with a porous layer that had a diameter of about 1.5 mm and a height of 2.4 mm and vapor vents having a diameter of 1 mm and 0.5 mm deep as shown in  FIG.  1 A  was fabricated. Three comparative example vapor chambers were also fabricated. A first comparative vapor chamber included a monolayer evaporator surface with no posts or vents. A second comparative vapor chamber included posts made out of only porous material (no solid pin fins) that were 1.5 mm in diameter and 2.4 mm in height and no vents. A third comparative vapor chamber included posts made of a pin fin that was 0.5 mm in diameter and 2.4 mm in height surrounded a porous layer to define posts having a diameter of 1 mm and a height of 2.4 mm. The third comparative vapor chamber did not include vents. 
     The variation in the thermal resistance and heater temperature with input power is shown in  FIGS.  6  and  7   , respectively. Trace  401  is the first comparative example, trace  402  is the second comparative example, trace  403  is the third comparative example, and trace  404  is the vapor chamber with posts and vents. As seen from  FIG.  6   , the trend in the thermal resistance of each vapor chamber is quite similar, i.e., the thermal resistance is higher at lower powers (&lt;100 W), drops once the onset of nucleate boiling (ONB) is reached, and is near constant in the nucleate boiling region. Below an input power of 100 W, the first comparative example (i.e., the monolayer vapor chamber) has lower thermal resistance than the second comparative example (i.e., the sintered post vapor chamber) and the third comparative example (i.e., the machined post vapor chamber). However, in the boiling region for input power&gt;300 W, the thermal resistance of the first comparative example is higher compared to the post-based designs. 
     The thermal resistance of the machined post vapor chamber (trace  403 ) is slightly lower than the sintered post design (trace  402 ) over the entire power range. For example, the thermal resistance of the machined post vapor chamber (trace  403 ) at an input power of 110 W is about 6% lower than the sintered post vapor chamber (trace  402 ), while it is 11% lower at a high input power of 450 W. 
     Among all the vapor chamber designs, the machined post plus vents vapor chamber (trace  404 ) in accordance with the present disclosure has the lowest thermal resistance for the entire range of input power. Unlike the behavior of the other vapor chambers, the thermal resistance of the machined post plus vents vapor chamber (trace  404 ) does not plateau in the boiling region but instead keeps decreasing until the maximum capacity of the power supply is reached. 
     Furthermore, the monolayer vapor chamber (trace  401 ) reaches dry out (DO) at an input power of 467 W, which was observed as a linear rise in the transient heater temperature without reaching steady state. Note that the rest of the vapor chamber designs did not exhibit this dry out phenomena. The maximum power dissipated by the sintered post (trace  402 ) and machined post designs (trace  403 ) were 450 W and 447 W respectively. The tests were stopped since the heater temperature exceeded the maximum allowable temperature of 478° C. For the machined post plus vent vapor chamber (trace  404 ), the input power supply reached its maximum capacity and therefore the testing was discontinued. 
     The variation of the heater temperature with input power is shown in  FIG.  7   . The sintered post (trace  502 ) and machined post (trace  503 ) vapor chambers show a linear rise in temperature with power until the ONB power of about 100 W is reached. Unlike the sintered post and machined post vapor chambers, the ONB point for the monolayer (trace  501 ) and machined post plus vents (trace  504 ) vapor chamber is not distinctly observed from  FIG.  7   . Furthermore, the rate of increase in the heater temperature of the machined post plus vents vapor chamber begins to decrease between 300 W and 400 W (as seen in trace  504 ), followed by a linear rise in the heater temperature thereafter. The machined post plus vents vapor chamber can dissipate significantly higher power compared to others for the same heater temperature. For example, at a heater temperature of 473° C., the machined post plus vents vapor chamber dissipates 30% more power compared to the monolayer vapor chamber (trace  501 ). 
     The variation of the through plane thermal resistances of the vapor chambers as a function of input power, is shown in  FIG.  8   . The monolayer vapor chamber (trace  601 ) generally has the highest thermal resistance compared to the post-based designs. The thermal resistance of the sintered (trace  602 ) and machined post (trace  603 ) vapor chamber are slightly higher than the monolayer thermal resistance in the low power region&lt;50 W. At an input power of about 98 W and 93 W, the ONB is observed for the sintered (trace  602 ) and machined post (trace  603 ) vapor chambers, respectively. At the ONB power, the through plane thermal resistance of both the vapor chambers drops dramatically by approximately half of its value. 
     The machined post plus vents vapor chamber (trace  604 ) has the lowest through plane thermal resistance for the entire range of power. For example, the through plane thermal resistance of the machined post plus vents vapor chamber at an input power of 110 W and 559 W is 0.18 K/W and 0.27 K/W, respectively. At powers higher than the ONB power, the thermal resistance of all vapor chambers rises linearly with input power. Among all vapor chambers tested, only the monolayer vapor chamber (trace  601 ) reached dry out (DO) at an input power of 457 W. The maximum power dissipated by the remaining vapor chamber designs were limited by the maximum current capacity of power supply (˜10 A), and testing was terminated in these cases. The maximum power dissipated by the machined post plus vents vapor chamber (trace  604 ) was 589 W. 
     Referring now to  FIG.  9   , an example method of fabricating a vapor chamber is illustrated by flowchart  700 . At block  702 , an array of posts and an array of vents are formed in an evaporator surface of an evaporator plate. The array of posts and the array of vents may be fabricated by machining, for example. As another example, the array of posts and the array of vents may be fabricated by chemical etching. For example, where the evaporator surface is made from copper, a mask may be applied to the evaporator surface and a chemical etchant, such as ferric chloride may be applied to form the desired array of posts and the array of vents. 
     At block  704 , a metal powder comprising metal particles is applied to the evaporator surface, the array of posts, and the array of vents. The metal particles may include copper particles for example. At block  706 , the metal powder is sintered to form a porous layer around the evaporator surface, the array of posts, and the array of vents. The porous layer provides both enhanced nucleation sites as well as a wicking structure to return liquid cooling fluid to the evaporator surface and the array of vents. 
     At block  708 , a porous condenser surface of a condenser plate is positioned on a top surface of the array of posts. This defines a vapor chamber between the condenser surface and the evaporator surface. Finally, at block  710 , the condenser surface is bonded to the top surface of the array of posts. As a non-limiting example, the condenser surface is bonded to the top surface of the array of posts is performed by diffusion bonding. 
     It should now be understood that embodiments of the present disclosure are directed to vapor chambers having an evaporator surface with an array of posts and an array of vapor vents. Each post includes a solid core that is surrounded by a porous layer. The solid core, which may be provided by a pin fin, lowers thermal resistance between the condenser surface and the evaporator surface. The array of vents provide an easier escape path for vapor as well as additional nucleation sites for vapor. The vapor chambers described herein have a low thermal resistance and a high dry out temperature. The vapor chambers herein may be utilized to cool power electronic device, such as wide band gap power electronic devices that produce significant heat flux, used in inverter circuits of electric or hybrid electric vehicles. 
     While particular embodiments have been illustrated and described herein, it should be understood that various other changes and modifications may be made without departing from the spirit and scope of the claimed subject matter. Moreover, although various aspects of the claimed subject matter have been described herein, such aspects need not be utilized in combination. It is therefore intended that the appended claims cover all such changes and modifications that are within the scope of the claimed subject matter.