US20050211417A1 - Interwoven manifolds for pressure drop reduction in microchannel heat exchangers - Google Patents

Abstract

A microchannel heat exchanger coupled to a heat source and configured for cooling the heat source comprising a first set of fingers for providing fluid at a first temperature to a heat exchange region, wherein fluid in the heat exchange region flows toward a second set of fingers and exits the heat exchanger at a second temperature, wherein each finger is spaced apart from an adjacent finger by an appropriate dimension to minimize pressure drop in the heat exchanger and arranged in parallel. The microchannel heat exchanger includes an interface layer having the heat exchange region. Preferably, a manifold layer includes the first set of fingers and the second set of fingers configured within to cool hot spots in the heat source. Alternatively, the interface layer includes the first set and second set of fingers configured along the heat exchange region.

Description

RELATED APPLICATIONS
• This Patent application is a continuation in part of U.S. patent application Ser. No. 10/439,912, filed May 16, 2003, and entitled “INTERWOVEN MANIFOLDS FOR PRESSURE DROP REDUCTION IN MICROCHANNEL HEAT EXCHANGERS”, hereby incorporated by reference, which claims priority under 35 U.S.C. 119 (e) of the co-pending U.S. Provisional Patent Application Ser. No. 60/423,009, filed Nov. 1, 2002 and entitled “METHODS FOR FLEXIBLE FLUID DELIVERY AND HOTSPOT COOLING BY MICROCHANNEL HEAT SINKS” which is hereby incorporated by reference, as well as co-pending U.S. Provisional Patent Application Ser. No. 60/442,383, filed Jan. 24, 2003 and entitled “OPTIMIZED PLATE FIN HEAT EXCHANGER FOR CPU COOLING” which is also hereby incorporated by reference, and co-pending U.S. Provisional Patent Application Ser. No. 60/455,729, filed Mar. 17, 2003 and entitled “MICROCHANNEL HEAT EXCHANGER APPARATUS WITH POROUS CONFIGURATION AND METHOD OF MANUFACTURING THEREOF”, which is hereby incorporated by reference.
FIELD OF THE INVENTION
• The invention relates to a method and apparatus for cooling a heat producing device in general, and specifically, to an interwoven manifold for pressure drop reduction in a microchannel heat exchanger.
BACKGROUND OF THE INVENTION
• Since their introduction in the early 1980s, microchannel heat sinks have shown much potential for high heat-flux cooling applications and have been used in the industry. However, existing microchannels include conventional parallel channel arrangements which are used are not well suited for cooling heat producing devices which have spatially-varying heat loads. Such heat producing devices have areas which produce more heat than others. These hotter areas are hereby designated as “hot spots” whereas the areas of the heat source which do not produce as much heat are hereby termed, “warm spots”.
• FIG. 1A illustrates a priorart heat exchanger10 which is coupled to anelectronic device99, such as a microprocessor via athermal interface material98. As shown inFIG. 1A, fluid generally flows from asingle inlet port12 and flows along thebottom surface11 in between theparallel microchannels14, as shown by the arrows, and exits through theoutlet port16. Although the heat exchanger10 cools theelectronic device99, the fluid flows from theinlet port12 to theoutlet port16 in a uniform manner. In other words, the fluid flows substantially uniformly along theentire bottom surface11 of theheat exchanger10 and does not supply more fluid to areas in thebottom surface11 which correspond with hot spots in thedevice99. In addition, the temperature of liquid flowing from the inlet generally increases as it flows along thebottom surface11 of the heat exchanger. Therefore, regions of theheat source99 which are downstream or near theoutlet port16 are not supplied with cool fluid, but actually fluid which has already been heated upstream. In effect, the heated fluid actually propagates the heat across theentire bottom surface11 of the heat exchanger and region of theheat source99, whereby fluid near theoutlet port16 is so hot that it becomes ineffective in cooling heat source. In addition, theheat exchanger10 having only oneinlet12 and oneoutlet16 forces fluid to travel along the longparallel microchannels14 in thebottom surface11 for the entire length of theheat exchanger10, thereby creating a large pressure drop.
• FIG. 1B illustrates a side view diagram of a prior artmulti-level heat exchanger20. Fluid enters themulti-level heat exchanger20 through theport22 and travels downward throughmultiple jets28 in themiddle layer26 to thebottom surface27 and outport24. In addition, the fluid traveling along thejets28 may or may not uniformly flow down to thebottom surface27. Nonetheless, although the fluid entering theheat exchanger20 is spread over the length of theheat exchanger20, the design does not provide more fluid to the hotter areas of theheat exchanger20 and heat source that are in need of more fluid flow circulation.
• In addition, conventional heat exchangers are made of materials which have high thermal resistance in the bottom surface, such that the heat exchanger has a coefficient of thermal expansion which matches that of theheat source99. The high thermal resistance of the heat exchanger thereby does not allow sufficient heat exchange with theheat source99. To account for the high thermal resistance, larger channel cross-sectional areas are chosen such that more thermal exchange occurs between theheat exchanger10 and theheat source99. In addition, the dimensions of the channels in the heat exchanger are scaled down and the distance between the channel walls and the hydraulic diameter is made smaller, the thermal resistance of the heat exchanger is reduced. However, a problem with using narrow microchannels is the increase in pressure drop along the channels. The increase in pressure drop places extreme demands on a pump driving the fluid through the heat exchanger. In addition, larger microchannel dimensions also cause a larger pressure drop between the inlet and outlet ports, due to the long distance that one or two phase fluid must travel. Further, boiling of the fluid in a microchannel heat exchanger causes a larger pressure drop for a given flowrate due to the mixing of fluid and vapor as well as the acceleration of the fluid into the vapor phase. Both of these factors increase the pressure drop per unit length. The large pressure drop created within the current microchannel heat exchangers require larger pumps which can handle higher pressures and thereby are not feasible in a microchannel setting.
• What is needed is a microchannel heat exchanger which is configured to achieve proper temperature uniformity in the heat source. What is also needed is a heat exchanger which is configured to achieve proper uniformity in light of hot spots in the heat source. What is also needed is a heat exchanger having a relatively high thermal conductivity to adequately perform thermal exchange with the heat source. What is further needed is a heat exchanger which is configured to achieve a small pressure drop between the inlet and outlet fluid ports.
SUMMARY OF THE INVENTION
• In one aspect of the invention, a heat exchanger comprises an interface layer for cooling a heat source, wherein the interface layer is configured to pass fluid therethrough and the interface layer includes a thickness within a range of about 0.3 millimeters to about 1.0 millimeters, and a manifold layer for circulating fluid to and from the interface layer, the manifold layer having a first set fingers and a second set of fingers, wherein the first set of fingers are disposed in parallel with the second set of fingers and arranged to reduce pressure drop within the heat exchanger. The fluid can be in single phase flow condition. The fluid can be in two phase flow fluid conditions. At least a portion of the fluid can undergo a transition between single and two phase flow conditions in the interface layer. A particular finger in the first set can be spaced apart by an appropriate dimension from a particular finger in the second set to minimize the pressure drop in the heat exchanger. Each of the fingers can have the same length and width dimensions. At least one of the fingers can have a different dimension than the remaining fingers. The fingers can be arranged non-periodically in at least one dimension in the manifold layer. At least one of the fingers can have at least one varying dimension along a length of the manifold layer. The manifold layer can include more than three and less than 10 parallel fingers. The fingers in the first set and second set can be alternately disposed along a dimension of the manifold layer. The manifold layer can be configured to cool at least one interface hot spot region. The heat exchanger can also include at least one first port in communication with the first set of fingers, wherein fluid enters the heat exchanger through the at least one first port. The heat exchanger can also include at least one second port in communication with the second set of fingers, wherein fluid exits the heat exchanger through the at least one second port. The manifold layer can be positioned above the interface layer, wherein fluid flows downward through the first set of fingers and upward though the second set of fingers. The heat exchanger can also include a first port passage in communication with the first port and the first set of fingers, the first port passage configured to channel fluid from the first port to the first set of fingers. The heat exchanger can also include a second port passage in communication with the second port and the second set of fingers, the second port passage configured to channel fluid from the second set of fingers to the second port. The interface layer can be integrally formed with the heat source. The interface layer can be coupled to the heat source. The heat exchanger can also include an intermediate layer for channeling fluid to and from one or more predetermined positions in the interface layer via at least one conduit, the intermediate layer positioned between the interface layer and the manifold layer. The intermediate layer can be coupled to the interface layer and the manifold layer. The intermediate layer can be integrally formed with the interface layer and the manifold layer. The at least one conduit can have at least one varying dimension along the intermediate layer. The interface layer can include a coating thereupon, wherein the coating provides an appropriate thermal conductivity of at least 10 W/m-K. The interface layer can have a thermal conductivity of at least 100 W/m-K. The heat exchanger can also include a plurality of pillars configured in a predetermined pattern along the interface layer. At least one of the plurality of pillars can have an area dimension within the range of and including (10 micron)²and (100 micron)². At least one of the plurality of pillars can have a height dimension within the range of and including 50 microns and 2 millimeters. At least two of the plurality of pillars can be separate from each other by a spacing dimension within the range of and including 10 to 150 microns. The plurality of pillars can include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K. The interface layer can have a roughened surface. The interface layer can include a micro-porous structure disposed thereon. The porous microstructure can have a porosity within the range of and including 50 to 80 percent. The porous microstructure can have an average pore size within the range of and including 10 to 200 microns. The porous microstructure can have a height dimension within the range of and including 0.25 to 2.00 millimeters. The heat exchanger can also include a plurality of microchannels configured in a predetermined pattern along the interface layer. At least one of the plurality of microchannels can have an area dimension within the range of and including (10 micron)²and (100 micron)². At least one of the plurality of microchannels can have a height dimension within the range of and including 50 microns and 2 millimeters. At least two of the plurality of microchannels can be separate from each other by a spacing dimension within the range of and including 10 to 150 microns. At least one of the plurality of microchannels can have a width dimension within the range of and including 10 to 100 microns. The plurality of microchannels can be coupled to the interface layer. The plurality of microchannels can be integrally formed with the interface layer. The plurality of microchannels can be divided into segmented arrays with at least one groove disposed therebetween, wherein the at least one groove is aligned with a corresponding finger. The plurality of microchannels can include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K. An overhang dimension can be within the range of and including 0 to 15 millimeters.
• In another aspect of the present invention, a heat exchanger for cooling a heat source comprises a manifold layer including a first set of fingers in a first configuration, wherein each finger in the first set channels fluid at a first temperature, the manifold layer further including a second set of fingers in a second configuration, wherein each finger in the second set channels fluid at a second temperature, the first set and second set of fingers arranged parallel to each other, and an interface layer including a thickness within a range of about 0.3 to 1.0 millimeters, and configured to receive fluid at the first temperature at a plurality of first locations, wherein each first location is associated with a corresponding finger in the first set, the interface layer passing fluid along a plurality of predetermined paths to a plurality of second locations, wherein each second location is associated with a corresponding finger in the second set. The fluid can be in single phase flow conditions. The fluid can be in two phase flow conditions. At least a portion of the fluid can undergo a transition between single and two phase flow conditions in the interface layer. A particular finger in the first set can be spaced apart by an appropriate dimension from a particular finger in the second set, wherein the appropriate dimension reduces the pressure drop in the heat exchanger. The heat exchanger can also include at least one first port in communication with the first set of fingers, wherein fluid enters the heat exchanger through the at least one first port. The heat exchanger can also include at least one second port in communication with the second set of fingers, wherein fluid exits the heat exchanger through the at least one second port. The manifold layer can be positioned above the interface layer, wherein fluid flows downward through the first set of fingers and upward through the second set of fingers. The interface layer can be integrally formed with the heat source. The interface layer can be coupled to the heat source. The fingers in the first set can be positioned in an alternating configuration with the fingers in the second set. Each of the fingers can have the same length and width dimensions. At least one of the fingers can have a different dimension than the remaining fingers. The fingers can be arranged non-periodically in at least one dimension in the manifold layer. At least one of the fingers can have at least one varying dimension along a length of the manifold layer. The manifold layer can include more than three and less than 10 parallel fingers. The heat exchanger can also include a first port passage in communication with the first port and the first set of fingers, the first port passage configured to channel fluid from the first port to the first set of fingers. The heat exchanger can also include a second port passage in communication with the second port and the second set of fingers, the second port passage configured to channel fluid from the second set of fingers to the second port. The heat exchanger can also include an intermediate layer for channeling fluid to and from one or more predetermined positions in the interface layer via at least one conduit, the intermediate layer positioned between the interface layer and the manifold layer. The conduit can be arranged in a predetermined configuration to channel fluid to one or more interface hot spot regions in the interface layer. The conduit can be arranged in a predetermined configuration to channel fluid from one or more interface hot spot regions in the interface layer. The intermediate layer can be coupled to the interface layer and the manifold layer. The intermediate layer can be integrally formed with the interface layer and the manifold layer. The conduit can have at least one varying dimension in the intermediate layer. The interface layer can include a coating thereupon, wherein the coating provides an appropriate thermal conductivity of at least 10 W/m-K. The interface layer can have a thermal conductivity is at least 10 W/m-K. The heat exchanger can also include a plurality of pillars configured in a predetermined pattern along the interface layer. At least one of the plurality of pillars can have an area dimension within the range of and including (10 micron)²and (100 micron)². At least one of the plurality of pillars can have a height dimension within the range of and including 50 microns and 2 millimeters. At least two of the plurality of pillars can be separate from each other by a spacing dimension within the range of and including 10 to 150 microns. The plurality of pillars can include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K. The interface layer can have a roughened surface. The interface layer can include a micro-porous structure disposed thereon. The porous microstructure can have a porosity within the range of and including 50 to 80 percent. The porous microstructure can have an average pore size within the range of and including 10 to 200 microns. The porous microstructure can have a height dimension within the range of and including 0.25 to 2.00 millimeters. The heat exchanger can also include a plurality of microchannels configured in a predetermined pattern along the interface layer. At least one of the plurality of microchannels can have an area dimension within the range of and including (10 micron)²and (100 micron)². At least one of the plurality of microchannels can have a height dimension within the range of and including 50 microns and 2 millimeters. At least two of the plurality of microchannels can be separate from each other by a spacing dimension within the range of and including 10 to 150 microns. At least one of the plurality of microchannels can have a width dimension within the range of and including 10 to 100 microns. The microchannels can be coupled to the interface layer. The microchannels can be integrally formed with the interface layer. The microchannels can be divided into segments along a dimension of the interface layer, at least one groove disposed in between the divided microchannel segments. The microchannels can be continuous along a dimension of the interface layer. The at least one groove can be aligned with a corresponding finger. The plurality of microchannels can include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 20 W/m-K. An overhang dimension can be within the range of and including 0 to 15 millimeters.
• Other features and advantages of the present invention will become apparent after reviewing the detailed description of the preferred embodiments set forth below.
BRIEF DESCRIPTION OF THE DRAWINGS
• FIG. 1A illustrates a side view of a conventional heat exchanger.
• FIG. 1B illustrates a top view of the conventional heat exchanger.
• FIG. 1C illustrates a side view diagram of a prior art multi-level heat exchanger.
• FIG. 2A illustrates a schematic diagram of a closed loop cooling system incorporating a preferred embodiment of the flexible fluid delivery microchannel heat exchanger of the present invention.
• FIG. 2B illustrates a schematic diagram of a closed loop cooling system incorporating an alternative embodiment of the flexible fluid delivery microchannel heat exchanger of the present invention.
• FIG. 3A illustrates a top view of an alternative manifold layer of the heat exchanger in accordance with the present invention.
• FIG. 3B illustrates an exploded view of an alternative heat exchanger with the alternative manifold layer in accordance with the present invention.
• FIG. 4 illustrates a perspective view of the preferred interwoven manifold layer in accordance with the present invention.
• FIG. 5 illustrates a top view of the preferred interwoven manifold layer with interface layer in accordance with the present invention.
• FIG. 6A illustrates a cross-sectional view of the preferred interwoven manifold layer with interface layer of the present invention along lines A-A.
• FIG. 6B illustrates a cross-sectional view of the preferred interwoven manifold layer with interface layer of the present invention along lines B-B.
• FIG. 6C illustrates a cross-sectional view of the preferred interwoven manifold layer with interface layer of the present invention along lines C-C.
• FIG. 7A illustrates an exploded view of the preferred interwoven manifold layer with interface layer of the present invention.
• FIG. 7B illustrates a perspective view of an alternative embodiment of the interface layer of the present invention.
• FIG. 8A illustrates a top view diagram of an alternate manifold layer in accordance with the present invention.
• FIG. 8B illustrates a top view diagram of the interface layer in accordance with the present invention.
• FIG. 8C illustrates a top view diagram of the interface layer in accordance with the present invention.
• FIG. 9A illustrates a side view diagram of the alternative embodiment of the three tier heat exchanger in accordance with the present invention.
• FIG. 9B illustrates a side view diagram of the alternative embodiment of the two tier heat exchanger in accordance with the present invention.
• FIG. 10 illustrates a perspective view of the interface layer having a micro-pin array in accordance with the present invention.
• FIG. 11 illustrates a cut-away perspective view diagram of the alternate heat exchanger in accordance with the present invention.
• FIG. 12 illustrates a side view diagram of the interface layer of the heat exchanger having a coating material applied thereon in accordance with the present invention.
• FIG. 13 illustrates a flow chart of an alternative method of manufacturing the heat exchanger in accordance with the present invention.
• FIG. 14 illustrates a schematic of an alternate embodiment of the present invention having two heat exchangers coupled to a heat source.
DETAILED DESCRIPTION OF THE PRESENT INVENTION
• Generally, the heat exchanger captures thermal energy generated from a heat source by passing fluid through selective areas of the interface layer which is preferably coupled to the heat source. In particular, the fluid is directed to specific areas in the interface layer to cool the hot spots and areas around the hot spots to generally create temperature uniformity across the heat source while maintaining a small pressure drop within the heat exchanger. As discussed in the different embodiments below, the heat exchanger utilizes a plurality of apertures, channels and/or fingers in the manifold layer as well as conduits in the intermediate layer to direct and circulate fluid to and from selected hot spot areas in the interface layer. Alternatively, the heat exchanger includes several ports which are specifically disposed in predetermined locations to directly deliver fluid to and remove fluid from the hot spots to effectively cool the heat source.
• It is apparent to one skilled in the art that although the microchannel heat exchanger of the present invention is described and discussed in relation to flexible fluid delivery for cooling hot spot locations in a device, the heat exchanger is alternatively used for flexible fluid delivery for heating a cold spot location in a device. It should also be noted that although the present invention is preferably described as a microchannel heat exchanger, the present invention can be used in other applications and is not limited to the discussion herein.
• FIG. 2A illustrates a schematic diagram of a closedloop cooling system30 which includes a preferred flexible fluid delivery microchannel heat exchanger400 in accordance with the present invention. In addition,FIG. 2B illustrates a schematic diagram of a closedloop cooling system30 which includes an alternative flexible fluid deliverymicrochannel heat exchanger200 withmultiple ports108,109 in accordance with the present invention.
• As shown inFIG. 2A, thefluid ports108,109 are coupled tofluid lines38 which are coupled to apump32 andheat condensor30. Thepump32 pumps and circulates fluid within the closedloop30. It is preferred that onefluid port108 is used to supply fluid to theheat exchanger100. In addition, it is preferred that onefluid port109 is used to remove fluid from theheat exchanger100. Preferably a uniform, constant amount of fluid flow enters and exits theheat exchanger100 via therespective fluid ports108,109. Alternatively, different amounts of fluid flow enter and exit through the inlet and outlet port(s)108,109 at a given time. Alternatively, as shown inFIG. 2B, one pump provides fluid to several designatedinlet ports108. Alternatively, multiple pumps (not shown), provide fluid to their respective inlet andoutlet ports108,109. In addition, the dynamic sensing and control module34 is alternatively employed in the system to variate and dynamically control the amount and flow rate of fluid entering and exiting the preferred or alternative heat exchanger in response to varying hot spots or changes in the amount of heat in a hot spot location as well as the locations of the hot spots.
• The preferred embodiment is a three level heat exchanger400 which includes aninterface layer402, at least one intermediate layer404 and at least onemanifold layer406. Thepreferred manifold layer402 and thepreferred interface layer402 are shown inFIG. 7 and theintermediate layer104 is shown inFIG. 3B. Alternatively, as discussed below, the heat exchanger400 is a two level apparatus which includes theinterface layer402 and themanifold layer406, as shown inFIG. 7. As shown inFIGS. 2A and 2B, the heat exchanger400 is coupled to aheat source99, such as an electronic device, including, but not limited to a microchip and integrated circuit, whereby athermal interface material98 is preferably disposed between theheat source99 and theheat exchanger100. Alternatively, the heat exchanger400 is directly coupled to the surface of theheat source99. It is also apparent to one skilled in the art that the heat exchanger400 is alternatively integrally formed into theheat source99, whereby the heat exchanger400 and theheat source99 are formed as one piece. Thus, theinterface layer102 is integrally disposed with theheat source99 and is formed as one piece with the heat source.
• It is preferred that the heat exchanger400 of the present invention is configured to be directly or indirectly in contact with theheat source99 which is rectangular in shape, as shown in the figures. However, it is apparent to one skilled in the art that the heat exchanger400 can have any other shape conforming with the shape of theheat source99. For example, the heat exchanger of the present invention can be configured to have an outer semicircular shape which allows the heat exchanger (not shown) to be in direct or indirect contact with a corresponding semicircular shaped heat source (not shown). In addition, it is preferred that the heat exchanger400 is slightly larger in dimension than the heat source within the range of and including 0.5-5.0 millimeters.
• FIG. 3A illustrates a top view of thealternate manifold layer106 of the present invention. In particular, as shown inFIG. 3B, themanifold layer106 includes four sides as well as atop surface130 and abottom surface132. However, thetop surface130 is removed inFIG. 3A to adequately illustrate and describe the workings of themanifold layer106. As shown inFIG. 3A, themanifold layer106 has a series of channels orpassages1116,118,120,122 as well asports108,109 formed therein. Thefingers1118,120 extend completely through the body of themanifold layer106 in the Z-direction as shown inFIG. 3B. Alternatively, thefingers118 and120 extend partially through themanifold layer106 in the Z-direction and have apertures as shown inFIG. 3A. In addition,passages116 and122 extend partially through themanifold layer106. The remaining areas between the inlet andoutlet passages116,120, designated as107, extend from thetop surface130 to thebottom surface132 and form the body of themanifold layer106.
• As shown inFIG. 3A, the fluid entersmanifold layer106 via theinlet port108 and flows along theinlet channel116 toseveral fingers118 which branch out from thechannel116 in several directions in the X and/or Y directions to apply fluid to selected regions in theinterface layer102. Thefingers118 are arranged in different predetermined directions to deliver fluid to the locations in theinterface layer102 corresponding to the areas at or near the hot spots in the heat source. These locations in theinterface layer102 are hereinafter referred to as interface hot spot regions. The fingers are configured to cool stationary as well as temporally varying interface hot spot regions. As shown inFIG. 3A, thechannels116,122 andfingers118,120 are disposed in the X and/or Y directions in themanifold layer106. Thus, the various directions of thechannels116,122 andfingers1118,120 allow delivery of fluid to cool hot spots in theheat source99 and/or minimize pressure drop within theheat exchanger100. Alternatively,channels116,122 andfingers1118,120 are periodically disposed in themanifold layer106 and exhibit a pattern, as in the preferred embodiment.
• The arrangement as well as the dimensions of thefingers118,120 are determined in light of the hot spots in theheat source99 that are desired to be cooled. The locations of the hot spots as well as the amount of heat produced near or at each hot spot are used to configure themanifold layer106 such that thefingers118,120 are placed above or proximal to the interface hot spot regions in theinterface layer102. Themanifold layer106 preferably allows one phase and/or two-phase fluid to circulate to theinterface layer102 without allowing a substantial pressure drop from occurring within theheat exchanger100 and the system30 (FIG. 2A). The fluid delivery to the interface hot spot regions creates a uniform temperature at the interface hot spot region as well as areas in the heat source adjacent to the interface hot spot regions.
• The dimensions as well as the number ofchannels116 andfingers118 depend on a number of factors. In one embodiment, the inlet andoutlet fingers118,120 have the same width dimensions. Alternatively, the inlet andoutlet fingers118,120 have different width dimensions. The width dimensions of thefingers118,120 are preferably within the range of and including 0.25-0.50 millimeters. In one embodiment, the inlet andoutlet fingers118,120 have the same length and depth dimensions. Alternatively, the inlet andoutlet fingers118,120 have different length and depth dimensions. In another embodiment, the inlet andoutlet fingers118,120 have varying width dimensions along the length of the fingers. The length dimensions of the inlet andoutlet fingers118,120 are within the range of and including 0.5 millimeters to three times the size of the heat source length. In addition, thefingers118,120 have a height or depth dimension within the range and including 0.25-0.50 millimeters. In addition, less than 10 or more than 30 fingers per centimeter are disposed in themanifold layer106. However, it is apparent to one skilled in the art that between 10 and 30 fingers per centimeter in the manifold layer is alternatively contemplated.
• It is contemplated within the present invention to tailor the geometries of thefingers118,120 andchannels116,122 to be in non-periodic arrangement to aid in optimizing hot spot cooling of the heat source. In order to achieve a uniform temperature across theheat source99, the spatial distribution of the heat transfer to the fluid is matched with the spatial distribution of the heat generation. As the fluid flows along the interface layer through themicrochannels110, its temperature increases and as it begins to transform to vapor under two-phase conditions. Thus, the fluid undergoes a significant expansion which results in a large increase in velocity. Generally, the efficiency of the heat transfer from the interface layer to the fluid is improved for high velocity flow. Therefore, it is possible to tailor the efficiency of the heat transfer to the fluid by adjusting the cross-sectional dimensions of the fluid delivery andremoval fingers118,120 andchannels116,122 in theheat exchanger100.
• For example, a particular finger can be designed for a heat source where there is higher heat generation near the inlet. In addition, it may be advantageous to design a larger cross section for the regions of thefingers118,120 andchannels116,122 where a mixture of fluid and vapor is expected. Although not shown, a finger can be designed to start out with a small cross sectional area at the inlet to cause high velocity flow of fluid. The particular finger or channel can also be configured to expand to a larger cross-section at a downstream outlet to cause a lower velocity flow. This design of the finger or channel allows the heat exchanger to minimize pressure drop and optimize hot spot cooling in areas where the fluid increases in volume, acceleration and velocity due to transformation from liquid to vapor in two-phase flow.
• In addition, thefingers118,120 andchannels116,122 can be designed to widen and then narrow again along their length to increase the velocity of the fluid at different places in themicrochannel heat exchanger100. Alternatively, it may be appropriate to vary the finger and channel dimensions from large to small and back again many times over in order to tailor the heat transfer efficiency to the expected heat dissipation distribution across theheat source99. It should be noted that the above discussion of the varying dimensions of the fingers and channels also apply to the other embodiments discussed and is not limited to this embodiment.
• Alternatively, as shown inFIG. 3A, themanifold layer106 includes one or more apertures119 in theinlet fingers118. In the threetier heat exchanger100, the fluid flowing along thefingers118 flows down the apertures119 to theintermediate layer104. Alternatively, in the two-tier heat exchanger100, the fluid flowing along thefingers118 flows down the apertures119 directly to theinterface layer102. In addition, as shown inFIG. 3A. themanifold layer106 includesapertures121 in theoutlet fingers120. In the threetier heat exchanger100, the fluid flowing from theintermediate layer104 flows up theapertures121 into theoutlet fingers120. Alternatively, in the two-tier heat exchanger100, the fluid flowing from theinterface layer102 flows directly up theapertures121 into theoutlet fingers120.
• In the embodiment shown inFIG. 3A, the inlet andoutlet fingers1118,120 are open channels which do not have apertures. Thebottom surface103 of themanifold layer106 abuts against the top surface of theintermediate layer104 in the threetier exchanger100 or abuts against theinterface layer102 in the two tier exchanger. Thus, in the three-tier heat exchanger100, fluid flows freely to and from theintermediate layer104 and themanifold layer106. The fluid is directed to and from the appropriate interface hot spot region by conduits105 theintermediate layer104. It is apparent to one skilled in the art that the conduits105 are directly aligned with the fingers, as described below or positioned elsewhere in the three tier system.
• FIG. 3B illustrates an exploded view of the threetier heat exchanger100 with the alternate manifold layer in accordance with the present invention. Alternatively, theheat exchanger100 is a two layer structure which includes themanifold layer106 and theinterface layer102, whereby fluid passes directly between themanifold layer106 andinterface layer102 without passing through theintermediate layer104. It is apparent to one skilled in the art that the configuration of the manifold, intermediate and interface layers are shown for exemplary purposes and is thereby not limited to the configuration shown.
• As shown inFIG. 3B, theintermediate layer104 includes a plurality of conduits105 which extend therethrough. The inflow conduits105 direct fluid entering from themanifold layer106 to the designated interface hot spot regions in theinterface layer102. Similarly, the apertures105 also channel fluid flow from theinterface layer102 to the exit fluid port(s)109. Thus, theintermediate layer104 also provides fluid delivery from theinterface layer102 to theexit fluid port109 where theexit fluid port108 is in communication with themanifold layer106.
• The conduits105 are positioned in theinterface layer104 in a predetermined pattern based on a number of factors including, but not limited to, the locations of the interface hot spot regions, the amount of fluid flow needed in the interface hot spot region to adequately cool theheat source99 and the temperature of the fluid. The conduits have a width dimension of 100 microns, although other width dimensions are contemplated up to several millimeters. In addition, the conduits105 have other dimensions dependent on at least the above mentioned factors. It is apparent to one skilled in the art that each conduit105 in theintermediate layer104 has a same shape and/or dimension, although it is not necessary. For instance, like the fingers described above, the conduits alternatively have a varying length and/or width dimension. Additionally, the conduits105 may have a constant depth or height dimension through theintermediate layer104. Alternatively, the conduits105 have a varying depth dimension, such as a trapezoidal or a nozzle-shape, through theintermediate layer104. Although the horizontal shape of the conduits105 are shown to be rectangular inFIG. 2C, the conduits105 alternatively have any other shape including, but not limited to, circular (FIG. 3A), curved and elliptical. Alternatively, one or more of the conduits105 are shaped and contour with a portion of or all of the finger or fingers above.
• Theintermediate layer104 is horizontally positioned within theheat exchanger100 with the conduits105 positioned vertically. Alternatively, theintermediate layer104 is positioned in any other direction within theheat exchanger100 including, but not limited to, diagonal and curved forms. Alternatively, the conduits105 are positioned within theintermediate layer104 in a horizontally, diagonally, curved or any other direction. In addition, theintermediate layer104 extends horizontally along the entire length of theheat exchanger100, whereby theintermediate layer104 completely separates theinterface layer102 from themanifold layer106 to force the fluid to be channeled through the conduits105. Alternatively, a portion of theheat exchanger100 does not include theintermediate layer104 between themanifold layer106 and theinterface layer102, whereby fluid is free to flow therebetween. Further, theintermediate layer104 alternatively extends vertically between themanifold layer106 and theinterface layer102 to form separate, distinct intermediate layer regions. Alternatively, theintermediate layer104 does not fully extend from themanifold layer106 tointerface layer102.
• It is preferred that theheat exchanger100 of the present invention is larger in width than theheat source99. In the case where theheat exchanger100 is larger than theheat source99, an overhang dimension exists. The overhang dimension is the farthest distance between one outer wall of theheat source99 and the interior fluid channel wall of theheat exchanger100, such as the inner wall of the inlet port408 (FIG. 4). In the preferred embodiment, the overhang dimension is within the range of and including 0 to 5 millimeters for single phase and 0 to 15 millimeters for two phase fluid.
• FIG. 10 illustrates a perspective view of one embodiment of aninterface layer202′ in accordance with the present invention. As shown inFIG. 10, theinterface layer202′ includes a series ofpillars203 which extend upwards from a top surface of theinterface layer202′. In addition,FIG. 10 illustrates a microporous structure213 disposed on the top surface of theinterface layer202′. It is apparent that theinterface layer202′ can include only the microporous structure213 as well as a combination of the microporous structure with any other interface layer feature (e.g. microchannels, pillars, etc.). In addition, theinterface layer202′ of the present invention preferably has a thickness dimension within the range of and including 0.3 to 0.7 millimeters for single phase fluid and 0.3 to 1.0 millimeters for two phase fluid.
• In the embodiment of the heat exchanger which utilizes a microporous structure213 disposed upon theinterface layer202′, the microporous structure213 has an average pore size within the range of and including 10 to 200 microns for single phase as well as two phase fluid. In addition, the microporous structure213 has a porosity within the range and including 50 to 80 percent for single phase as well as two phase fluid. The height of the microporous structure213 is within the range of and including 0.25 to 2.00 millimeters for single phase as well as two phase fluid.
• In the embodiment which utilizes pillars and/or microchannels along theinterface layer202′, theinterface layer202′ of the present invention has a thickness dimension in the range of and including 0.3 to 0.7 millimeters for single phase fluid and 0.3 to 1.0 millimeters for two phase fluid. In addition, the area of at least one pillar, or microchannel, is in the range of and including (10 micron)²and (100 micron)²for single phase as well as two phase fluid. In addition, the area of the separation distance between at least two of the pillars and/or microchannels is in the range of and including 10 microns to 150 microns for single phase as well as two phase fluid. The width dimension of the microchannels are in the range of and including 10 to 100 microns for single phase as well as two phase fluid. The height dimension of the microchannels and/or pillars is within the range of and including 50 to 800 microns for single phase fluid and 50 microns to 2 millimeters for two phase fluid. It is contemplated by one skilled in the art that other dimension are alternatively contemplated.
• FIG. 3B illustrates a perspective view of theinterface layer102 in accordance with the present invention. As shown inFIG. 3B, theinterface layer102 includes abottom surface103 and a plurality ofmicrochannel walls110, whereby the area in between themicrochannel walls110 channels or directs fluid along a fluid flow path. Thebottom surface103 is flat and has a high thermal conductivity to allow sufficient heat transfer from theheat source99. Alternatively, thebottom surface103 includes troughs and/or crests designed to collect or repel fluid from a particular location. Themicrochannel walls110 are configured in a parallel configuration, as shown inFIG. 3B, whereby fluid preferably flows between themicrochannel walls110 along a fluid path. Alternatively, themicrochannel walls110 have non-parallel configurations.
• It is apparent to one skilled in the art that themicrochannel walls110 are alternatively configured in any other appropriate configuration depending on the factors discussed above. For instance, theinterface layer102 alternatively has grooves in between sections ofmicrochannel walls110, as shown inFIG. 8C. In addition, themicrochannel walls110 have dimensions which minimize the pressure drop or differential within theinterface layer102. It is also apparent that any other features, besidesmicrochannel walls110 are also contemplated, including, but not limited to, pillars (FIG. 10), roughed surfaces, and a micro-porous structure, such as sintered metal and silicon foam (FIG. 10). However, for exemplary purposes, theparallel microchannel walls110 shown inFIG. 3B is used to describe theinterface layer102 in the present invention.
• Themicrochannel walls110 allow the fluid to undergo thermal exchange along the selected hot spot locations of the interface hot spot region to cool theheat source99 in that location. Themicrochannel walls110 have a width dimension within the range of 10-100 microns and a height dimension within the range of 50 microns to two millimeters, depending on the power of theheat source99. Themicrochannel walls110 have a length dimension which ranges between 100 microns and several centimeters, depending on the dimensions of the heat source, as well as the size of the hot spots and the heat flux density from the heat source. Alternatively, any other microchannel wall dimensions are contemplated. Themicrochannel walls110 are spaced apart by a separation dimension range of 50-500 microns, depending on the power of theheat source99, although any other separation dimension range is contemplated.
• Referring back to the assembly inFIG. 3B, the top surface of themanifold layer106 is cut away to illustrate thechannels116,122 andfingers118,120 within the body of themanifold layer106. The locations in theheat source99 that produce more heat are hereby designated as hot spots, whereby the locations in theheat source99 which produce less heat are hereby designated as warm spots. As shown inFIG. 3B, theheat source99 is shown to have a hot spot region, namely at location A, and a warm spot region, namely at location B. The areas of theinterface layer102 which abut the hot and warm spots are accordingly designated interface hot spot regions. As shown inFIG. 3B, theinterface layer102 includes interface hot spot region A, which is positioned above location A and interface hot spot region B, which is positioned above location B.
• As shown inFIGS. 3A and 3B, fluid initially enters theheat exchanger100 through oneinlet port108. The fluid then preferably flows to oneinlet channel116. Alternatively, theheat exchanger100 includes more than oneinlet channel116. As shown inFIGS. 3A and 3B, fluid flowing along theinlet channel116 from theinlet port108 initially branches out tofinger118D. In addition, the fluid which continues along the rest of theinlet channel116 flows toindividual fingers1181B and118C and so on.
• InFIG. 3B, fluid is supplied to interface hot spot region A by flowing to thefinger118A, whereby fluid flows down throughfinger118A to theintermediate layer104. The fluid then flows through theinlet conduit105A positioned below thefinger118A to theinterface layer102, whereby the fluid undergoes thermal exchange with theheat source99. The fluid travels along themicrochannels110 as shown inFIG. 3B, although the fluid may travel in any other direction along theinterface layer102. The heated liquid then travels upward through theconduit105B to theoutlet finger120A. Similarly, fluid flows down in the Z-direction throughfingers118E and118F to theintermediate layer104. The fluid then flows through theinlet conduit105C down in the Z-direction to theinterface layer102. The heated fluid then travels upward in the Z-direction from theinterface layer102 through theoutlet conduit105D to the outlet fingers120E and120F. Theheat exchanger100 removes the heated fluid in themanifold layer106 via theoutlet fingers120, whereby theoutlet fingers120 are in communication with theoutlet channel122. Theoutlet channel122 allows fluid to flow out of the heat exchanger through oneoutlet port109.
• In one embodiment, the inflow and outflow conduits105 are positioned directly or nearly directly above the appropriate interface hot spot regions to directly apply fluid to hot spots in theheat source99. In addition, eachoutlet finger120 is configured to be positioned closest to a respective inlet finger119 for a particular interface hot spot region to minimize pressure drop therebetween. Thus, fluid enters theinterface layer102 via theinlet finger118A and travels the least amount of distance along thebottom surface103 of theinterface layer102 before it exits theinterface layer102 to theoutlet finger120A. It is apparent that the amount of distance which the fluid travels along thebottom surface103 adequately removes heat generated from theheat source99 without generating an unnecessary amount of pressure drop. In addition, as shown inFIGS. 3A and 3B, the corners in thefingers118,120 are curved to reduce pressure drop of the fluid flowing along thefingers118.
• It is apparent to one skilled in the art that the configuration of themanifold layer106 shown inFIGS. 3A and 3B is only for exemplary purposes. The configuration of thechannels116 andfingers118 in themanifold layer106 depend on a number of factors, including but not limited to, the locations of the interface hot spot regions, amount of flow to and from the interface hot spot regions as well as the amount of heat produced by the heat source in the interface hot spot regions. For instance, the preferred configuration of themanifold layer106 includes an interdigitated pattern of parallel inlet and outlet fingers that are arranged along the width of the manifold layer, as shown inFIGS. 4-7A and discussed below. Nonetheless, any other configuration ofchannels116 andfingers118 is contemplated.
• FIG. 4 illustrates a perspective view of thepreferred manifold layer406 in accordance with the heat exchanger of the present invention. Themanifold layer406 inFIG. 4 preferably includes a plurality of interwoven or inter-digitated parallelfluid fingers411,412 which allow one phase and/or two-phase fluid to circulate to theinterface layer402 without allowing a substantial pressure drop from occurring within the heat exchanger400 and the system30 (FIG. 2A). As shown inFIG. 8, theinlet fingers411 are arranged alternately with theoutlet fingers412. However, it is contemplated by one skilled in the art that a certain number of inlet or outlet fingers can be arranged adjacent to one another and is thereby not limited to the alternating configuration shown inFIG. 4. In addition, the fingers are alternatively designed such that a parallel finger branches off from or is linked to another parallel finger. Thus, it is possible to have many more inlet fingers than outlet fingers and vice versa.
• The inlet fingers orpassages411 supply the fluid entering the heat exchanger to theinterface layer402, and the outlet fingers orpassages412 remove the fluid from theinterface layer402 which then exits the heat exchanger400. The preferred configuration of themanifold layer406 allows the fluid to enter theinterface layer402 and travel a very short distance in theinterface layer402 before it enters theoutlet passage412. The substantial decrease in the length that the fluid travels along theinterface layer402 substantially decreases the pressure drop in the heat exchanger400 and the system30 (FIG. 2A).
• As shown inFIGS. 4-5, thepreferred manifold layer406 includes apassage414 which is in communication with twoinlet passages411 and provides fluid thereto. As shown inFIGS. 8-9 themanifold layer406 includes threeoutlet passages412 which are in communication withpassage418. Preferably thepassages414 in themanifold layer406 have a flat bottom surface which channels the fluid to thefingers411,412. Alternatively, thepassage414 has a slight slope which aids in channeling the fluid to selectedfluid passages411. Alternatively, theinlet passage414 includes one or more apertures in its bottom surface which allows a portion of the fluid to flow down to theinterface layer402. Similarly, thepassage418 in the manifold layer has a flat bottom surface which contains the fluid and channels the fluid to theport408. Alternatively, thepassage418 has a slight slope which aids in channeling the fluid to selectedoutlet ports408. In addition, thepassages414,418 have a dimension width of approximately 2 millimeters, although any other width dimensions are alternatively contemplated.
• Thepassages414,418 are in communication withports408,409 whereby the ports are coupled to thefluid lines38 in the system30 (FIG. 2A). Themanifold layer406 preferably includes horizontally configuredfluid ports408,409. Alternatively, themanifold layer406 includes vertically and/or diagonally configuredfluid ports408,409, as discussed below, although not shown inFIG. 4-7. Alternatively, themanifold layer406 does not includepassage414. Thus, fluid is directly supplied to thefingers411 from theports408. Again, themanifold layer411 alternatively does not includepassage418, whereby fluid in thefingers412 directly flows out of the heat exchanger400 throughports408. It is apparent that although twoports408 are shown in communication with thepassages414,418, any other number of ports are alternatively utilized.
• Theinlet passages411 preferably have dimensions which allow fluid to travel to the interface layer without generating a large pressure drop along thepassages411 and the system30 (FIG. 2A). Theinlet passages411 preferably have a width dimension in the range of and including 0.25-5.00 millimeters, although any other width dimensions are alternatively contemplated. In addition, theinlet passages411 preferably have a length dimension in the range of and including 0.5 millimeters to three times the length of the heat source. Alternatively, other length dimensions are contemplated. In addition, as stated above, theinlet passages411 extend down to or slightly above the height of themicrochannels410 such that the fluid is channeled directly to themicrochannels410. Theinlet passages411 preferably have a height dimension in the range of and including 0.25-5.00 millimeters. It is apparent to one skilled in the art that thepassages411 do not extend down to themicrochannels410 and that any other height dimensions are alternatively contemplated. It is apparent to one skilled in the art that although theinlet passages411 have the same dimensions, it is contemplated that theinlet passages411 alternatively have different dimensions. In addition, theinlet passages411 alternatively have varying widths, cross sectional dimensions and/or distances between adjacent fingers. varying dimensions. In particular, thepassage411 has areas with a larger width or depths as well as areas with narrower widths and depths along its length. The varied dimensions allow more fluid to be delivered to predetermined interface hot spot regions in theinterface layer402 through wider portions while restricting flow to warm spot interface hot spot regions through the narrow portions.
• In addition, theoutlet passages412 preferably have dimensions which allow fluid to travel to the interface layer without generating a large pressure drop along thepassages412 as well as the system30 (FIG. 2A). Theoutlet passages412 preferably have a width dimension in the range of and including 0.25-5.00 millimeters, although any other width dimensions are alternatively contemplated. In addition, theoutlet passages412 preferably have a length dimension in the range of and including 0.5 millimeters to three times the length of the heat source. In addition, theoutlet passages412 extend down to the height of themicrochannels410 such that the fluid easily flows upward in theoutlet passages412 after horizontally flowing along themicrochannels410. Theinlet passages411 preferably have a height dimension in the range of and including 0.25-5.00 millimeters, although any other height dimensions are alternatively contemplated. It is apparent to one skilled in the art that althoughoutlet passages412 have the same dimensions, it is contemplated that theoutlet passages412 alternatively have different dimensions. Again, theinlet passage412 alternatively have varying widths, cross sectional dimensions and/or distances between adjacent fingers.
• The inlet andoutlet passages411,412 are preferably segmented and distinct from one another, as shown inFIGS. 4 and 5, whereby fluid among the passages do not mix together. In particular, as shown inFIG. 8, two outlet passages are located along the outside edges of themanifold layer406, and oneoutlet passage412 is located in the middle of themanifold layer406. In addition, twoinlet passages411 are configured on adjacent sides of themiddle outlet passage412. This particular configuration causes fluid entering theinterface layer402 to travel the a short distance in theinterface layer402 before it flows out of theinterface layer402 through theoutlet passage412. However, it is apparent to one skilled in the art that the inlet passages and outlet passages may be positioned in any other appropriate configuration and is thereby not limited to the configuration shown and described in the present disclosure. The number of inlet andoutlet fingers411,412 are more than three within themanifold layer406 but less than 10 per centimeter across themanifold layer406. It is also apparent to one skilled in the art that any other number of inlet passages and outlet passages may be used and thereby is not limited to the number shown and described in the present disclosure.
• Preferably, themanifold layer406 is coupled to the intermediate layer (not shown), whereby the intermediate layer (not shown) is coupled to theinterface layer402 to form a three-tier heat exchanger400. The intermediate layer discussed herein is referred to above in the embodiment shown inFIG. 3B. Themanifold layer406 is alternatively coupled to theinterface layer402 and positioned above theinterface layer402 to form a two-tier heat exchanger400, as shown inFIG. 7A.FIGS. 6A-6C illustrate cross-sectional schematics of thepreferred manifold layer406 coupled to theinterface layer402 in the two tier heat exchanger. Specifically,FIG. 6A illustrates the cross section of the heat exchanger400 along line A-A inFIG. 5. In addition,FIG. 6B illustrates the cross section of the heat exchanger400 along line B-B andFIG. 6C illustrates the cross section of the heat exchanger400 along line C-C inFIG. 5. As stated above, the inlet andoutlet passages411,412 extend from the top surface to the bottom surface of themanifold layer406. When themanifold layer406 and theinterface layer402 are coupled to one another, the inlet andoutlet passages411,412 are at or slightly above the height of themicrochannels410 in theinterface layer402. This configuration causes the fluid from theinlet passages411 to easily flow from thepassages411 through themicrochannels410. In addition, this configuration causes fluid flowing through the microchannels to easily flow upward through theoutlet passages412 after flowing through themicrochannels410.
• In the preferred embodiment, the intermediate layer104 (FIG. 3B) is positioned between themanifold layer406 and theinterface layer402, although not shown in the figures. The intermediate layer104 (FIG. 3B) channels fluid flow to designated interface hot spot regions in theinterface layer402. In addition, the intermediate layer104 (FIG. 3B) is preferably utilized to provide a uniform flow of fluid entering theinterface layer402. Also, theintermediate layer104 is preferably utilized to provide fluid to interface hot spot regions in theinterface layer402 to adequately cool hot spots and create temperature uniformity in theheat source99. Although, the inlet andoutlet passages411,412 are preferably positioned near or above hot spots in theheat source99 to adequately cool the hot spots, although it is not necessary.
• FIG. 7A illustrates an exploded view of thealternate manifold layer406 with the analternative interface layer102 of the present invention. Preferably, theinterface layer102 includes continuous arrangements ofmicrochannel walls110, as shown inFIG. 3B. In general operation, similar to thepreferred manifold layer106 shown inFIG. 3B, fluid enters themanifold layer406 atfluid port408 and travels through thepassage414 and towards the fluid fingers orpassages411. The fluid enters the opening of theinlet fingers411 and preferably flows the length of thefingers411 in the X-direction, as shown by the arrows. In addition, the fluid flows downward in the Z-direction to theinterface layer402 which is positioned below to themanifold layer406. As shown inFIG. 7A, the fluid in theinterface layer402 traverses along the bottom surface in the X and Y directions of theinterface layer402 and performs thermal exchange with theheat source99. The heated fluid exits theinterface layer402 by preferably flowing upward in the Z-direction via theoutlet fingers412, whereby theoutlet fingers412 channel the heated fluid to thepassage418 in themanifold layer406 in the X-direction. The fluid then flows along thepassage418 and exits the heat exchanger by flowing out through theport409.
• The interface layer, as shown inFIG. 7A, includes a series of grooves416 disposed in between sets ofmicrochannels410 which aid in channeling fluid to and from thepassages411,412. In particular, thegrooves416A are located directly beneath theinlet passages411 of thealternate manifold layer406, whereby fluid entering theinterface layer402 via theinlet passages411 is directly channeled to the microchannels adjacent to thegroove416A. Thus, thegrooves416A allow fluid to be directly channeled into specific designated flow paths from theinlet passages411, as shown inFIG. 5. Similarly, theinterface layer402 includesgrooves416B which are located directly beneath theoutlet passages412 in the Z-direction. Thus, fluid flowing horizontally along themicrochannels410 toward the outlet passages are channeled horizontally to thegrooves416B and vertically to theoutlet passage412 above thegrooves416B.
• FIG. 6A illustrates the cross section of the heat exchanger400 withmanifold layer406 andinterface layer402. In particular,FIG. 6A shows theinlet passages411 interwoven with theoutlet passages412, whereby fluid flows down theinlet passages411 and up theoutlet passages412. In addition, as shown inFIG. 6A, the fluid flows horizontally through themicrochannel walls410 which are disposed between the inlet passages and outlet passages and separated by themicrochannels410. Alternatively, the microchannel walls are continuous (FIG. 3B) and are not separated by the grooves. As shown inFIG. 6A, either or both of the inlet andoutlet passages411,412 preferably have acurved surface420 at their ends at the location near the grooves416. Thecurved surface420 directs fluid flowing down thepassage411 towards themicrochannels410 which are located adjacent to thepassage411. Thus, fluid entering theinterface layer102 is more easily directed toward themicrochannels410 instead of flowing directly to thegroove416A. Similarly, thecurved surface420 in theoutlet passages412 assists in directing fluid from themicrochannels410 to theouter passage412.
• In an alternative embodiment, as shown inFIG. 7B, theinterface layer402′ includes theinlet passages411′ andoutlet passages412′ discussed above with respect to the manifold layer406 (FIGS. 8-9). In the alternative embodiment, the fluid is supplied directly to theinterface layer402′ from theport408′. The fluid flows along thepassage414′ towards theinlet passages411′. The fluid then traverses laterally along the sets ofmicrochannels410′ and undergoes heat exchange with the heat source (not shown) and flows to theoutlet passages412′. The fluid then flows along theoutlet passages412′ topassage418′, whereby the fluid exits theinterface layer402′ by via theport409′. Theports408′,409′ are configured in theinterface layer402′ and are alternatively configured in the manifold layer406 (FIG. 7A).
• It is apparent to one skilled in the art that although all of the heat exchangers in the present application are shown to operate horizontally, the heat exchanger alternatively operates in a vertical position. While operating in the vertical position, the heat exchangers are alternatively configured such that each inlet passage is located above an adjacent outlet passage. Therefore, fluid enters the interface layer through the inlet passages and is naturally channeled to an outlet passage. It is also apparent that any other configuration of the manifold layer and interface layer is alternatively used to allow the heat exchanger to operate in a vertical position.
• FIGS. 8A-8C illustrate top view diagrams of another alternate embodiment of the heat exchanger in accordance with the present invention. In particular,FIG. 8A illustrates a top view diagram of analternate manifold layer206 in accordance with the present invention.FIGS. 8B and 8C illustrate a top view of anintermediate layer204 andinterface layer202. In addition,FIG. 9A illustrates a three tier heat exchanger utilizing thealternate manifold layer206, whereasFIG. 9B illustrates a two-tier heat exchanger utilizing thealternate manifold layer206.
• As shown inFIGS. 8A and 9A, themanifold layer206 includes a plurality offluid ports208 configured horizontally and vertically. Alternatively, thefluid ports208 are positioned diagonally or in any other direction with respect to themanifold layer206. Thefluid ports208 are placed in selected locations in themanifold layer206 to effectively deliver fluid to the predetermined interface hot spot regions in theheat exchanger200. The multiplefluid ports208 provide a significant advantage, because fluid can be directly delivered from a fluid port to a particular interface hot spot region without significantly adding to the pressure drop to theheat exchanger200. In addition, thefluid ports208 are also positioned in themanifold layer206 to allow fluid in the interface hot spot regions to travel the least amount of distance to theexit port208 such that the fluid achieves temperature uniformity while maintaining a minimal pressure drop between the inlet andoutlet ports208. Additionally, the use of themanifold layer206 aids in stabilizing two phase flow within theheat exchanger200 while evenly distributing uniform flow across theinterface layer202. It should be noted that more than onemanifold layer206 is alternatively included in theheat exchanger200, whereby onemanifold layer206 routes the fluid into and out-of theheat exchanger200 and another manifold layer (not shown) controls the rate of fluid circulation to theheat exchanger200. Alternatively, all of the plurality ofmanifold layers206 circulate fluid to selected corresponding interface hot spot regions in theinterface layer202.
• Thealternate manifold layer206 has lateral dimensions which closely match the dimensions of theinterface layer202. In addition, themanifold layer206 has the same dimensions of theheat source99. Alternatively, themanifold layer206 is larger than theheat source99. The vertical dimensions of themanifold layer206 are within the range of 0.1 and 10 millimeters. In addition, the apertures in themanifold layer206 which receive thefluid ports208 are within the range between 1 millimeter and the entire width or length of theheat source99.
• FIG. 11 illustrates a broken-perspective view of a threetier heat exchanger200 having thealternate manifold layer200 in accordance with the present invention. As shown inFIG. 11, theheat exchanger200 is divided into separate regions dependent on the amount of heat produced along the body of theheat source99. The divided regions are separated by the verticalintermediate layer204 and/or microchannel wall features210 in theinterface layer202. However, it is apparent to one skilled in the art that the assembly shown inFIG. 11 is not limited to the configuration shown and is for exemplary purposes.
• As shown inFIG. 3, theheat source99 has a hot spot in location A and a warm spot, location B, whereby the hot spot in location A produces more heat than the warm spot in location B. It is apparent that theheat source99 may have more than one hot spot and warm spot at any location at any given time. In the example, since location A is a hot spot and more heat in location A transfers to theinterface layer202 above location A (designated inFIG. 11 as interface hot spot region A), more fluid and/or a higher rate of liquid flow is provided to interface hot spot region A in theheat exchanger200 to adequately cool location A. It is apparent that although interface hot spot region B is shown to be larger than interface hot spot region A, interface hot spot regions A and B, as well as any other interface hot spot regions in theheat exchanger200, can be any size and/or configuration with respect to one another.
• Alternatively, as shown inFIG. 11, the fluid enters the heat exchanger viafluid ports208A is directed to interface hot spot region A by flowing along theintermediate layer204 to the inflow conduits205A. The fluid then flows down the inflow conduits205A in the Z-direction into interface hot spot region A of theinterface layer202. The fluid flows in between the microchannels210A whereby heat from location A transfers to the fluid by conduction through theinterface layer202. The heated fluid flows along theinterface layer202 in interface hot spot region A towardexit port209A where the fluid exits theheat exchanger200. It is apparent to one skilled in the art that any number ofinlet ports208 andexit ports209 are utilized for a particular interface hot spot region or a set of interface hot spot regions. In addition, although theexit port209A is shown near the interface layer202A, theexit port209A is alternatively positioned in any other location vertically, including but not limited to themanifold layer209B.
• Similarly, in the example shown inFIG. 11, theheat source99 has a warm spot in location B which produces less heat than location A of theheat source99. Fluid entering through theport208B is directed to interface hot spot region B by flowing along theintermediate layer204B to theinflow conduits205B. The fluid then flows down theinflow conduits205B in the Z-direction into interface hot spot region B of theinterface layer202. The fluid flows in between themicrochannels210 in the X and Y directions, whereby heat generated by the heat source in location B is transferred into the fluid. The heated fluid flows along the entire interface layer202B in interface hot spot region B upward to exitports209B in the Z-direction via theoutflow conduits205B in theintermediate layer204 whereby the fluid exits theheat exchanger200.
• Alternatively, as shown inFIG. 9A, theheat exchanger200 alternatively includes a vaporpermeable membrane214 positioned above theinterface layer202. The vaporpermeable membrane214 is in sealable contact with the inner side walls of theheat exchanger200. The membrane is configured to have several small apertures which allow vapor produced along theinterface layer202 to pass therethrough to theoutlet port209. Themembrane214 is also configured to be hydrophobic to prevent liquid fluid flowing along theinterface layer202 from passing through the apertures of themembrane214. More details of the vapor permeable membrane114 is discussed in co-pending U.S. application Ser. No. 10/366,128, filed Feb. 12, 2003 and entitled, “VAPOR ESCAPE MICROCHANNEL HEAT EXCHANGER” which is hereby incorporated by reference.
• The microchannel heat exchanger of the present invention alternatively has other configurations not described above. For instance, the heat exchanger alternatively includes a manifold layer which minimizes the pressure drop within the heat exchanger in having separately sealed inlet and outlet apertures which lead to the interface layer. Thus, fluid flows directly to the interface layer through inlet apertures and undergoes thermal exchange in the interface layer. The fluid then exits the interface layer by flowing directly through outlet apertures arranged adjacent to the inlet apertures. This porous configuration of the manifold layer minimizes the amount of distance that the fluid must flow between the inlet and outlet ports as well as maximizes the division of fluid flow among the several apertures leading to the interface layer.
• The details of how theheat exchanger100 as well as the individual layers in theheat exchanger100 are fabricated and manufactured are discussed below. The following discussion applies to the preferred and alternative heat exchangers of the present invention, although theheat exchanger100 inFIG. 3B and individual layers therein are expressly referred to for simplicity. It is also apparent to one skilled in the art that although the fabrication/manufacturing details are described in relation to the present invention, the fabrication and manufacturing details also alternatively apply to conventional heat exchangers as well as two and three-tier heat exchangers utilizing one fluid inlet port and one fluid outlet port as shown inFIGS. 1A-1C.
• Preferably, theinterface layer102 has a coefficient of thermal expansion (CTE) which is approximate or equal to that of theheat source99. Thus, theinterface layer102 preferably expands and contracts accordingly with theheat source99. Alternatively, the material of theinterface layer102 has a CTE which is different than the CTE of the heat source material. Aninterface layer102 made from a material such as Silicon has a CTE that matches that of theheat source99 and has sufficient thermal conductivity to adequately transfer heat from theheat source99 to the fluid. However, other materials are alternatively used in theinterface layer102 which have CTEs that match theheat source99.
• Theinterface layer102 in theheat exchanger100 preferably has a high thermal conductivity for allowing sufficient conduction to pass between theheat source99 and fluid flowing along theinterface layer102 such that theheat source99 does not overheat. Theinterface layer102 is preferably made from a material having a high thermal conductivity of 100 W/m-K. However, it is apparent to one skilled in the art that theinterface layer102 has a thermal conductivity of more or less than 100 W/m-K and is not limited thereto.
• To achieve the preferred high thermal conductivity, the interface layer is preferably made from a semiconductor substrate, such as Silicon. Alternatively, the interface layer is made from any other material including, but not limited to single-crystalline dielectric materials, metals, aluminum, nickel and copper, Kovar, graphite, diamond, composites and any appropriate alloys. An alternative material of theinterface layer102 is a patterned or molded organic mesh.
• As shown inFIG. 12, it is preferred that theinterface layer102 is coated with acoating layer112 to protect the material of theinterface layer102 as well as enhance the thermal exchange properties of theinterface layer102. In particular, thecoating112 provides chemical protection that eliminates certain chemical interactions between the fluid and theinterface layer102. For example, aninterface layer102 made from aluminum may be etched by the fluid coming into contact with it, whereby theinterface layer102 would deteriorate over time. Thecoating112 of a thin layer of Nickel, approximately 25 microns, is thus preferably electroplated over the surface of theinterface layer102 to chemically pacify any potential reactions without significantly altering the thermal properties of theinterface layer102. It is apparent that any other coating material with appropriate layer thickness is contemplated depending on the material(s) in theinterface layer102.
• In addition, thecoating material112 is applied to theinterface layer102 to enhance the thermal conductivity of theinterface layer102 to perform sufficient heat exchange with theheat source99, as shown inFIG. 12. For example, aninterface layer102 having a metallic base covered with plastic can be thermally enhanced with a layer ofNickel coating material112 on top of the plastic. The layer of Nickel has a thickness of at least 25 microns, depending on the dimensions of theinterface layer102 and theheat source99. It is apparent that any other coating material with appropriate layer thickness is contemplated depending on the material(s) in theinterface layer102. Thecoating material112 is alternatively used on material already having high thermal conductivity characteristics, such that the coating material enhances the thermal conductivity of the material. Thecoating material112 is preferably applied to thebottom surface103 as well as themicrochannel walls110 of theinterface layer102, as shown inFIG. 12. Alternatively, thecoating material112 is applied to either of thebottom surface103 ormicrochannel walls110. Thecoating material112 is preferably made from a metal including, but not limited to, Nickel and Aluminum. However, thecoating material112 is alternatively made of any other thermally conductive material.
• Theinterface layer102 is preferably formed by an etching process using a Copper material coated with a thin layer of Nickel to protect theinterface layer102. Alternatively, theinterface layer102 is made from Aluminum, Silicon substrate, plastic or any other appropriate material. Theinterface layer102 being made of materials having poor thermal conductivity are also coated with the appropriate coating material to enhance the thermal conductivity of theinterface layer102. One method of electroforming the interface layer is by applying a seed layer of chromium or other appropriate material along thebottom surface103 of theinterface layer102 and applying electrical connection of appropriate voltage to the seed layer. The electrical connection thereby forms a layer of the thermallyconductive coating material112 on top of theinterface layer102. The electroforming process also forms feature dimensions in a range of 10-100 microns. Theinterface layer102 is formed by an electroforming process, such as patterned electroplating. In addition, the interface layer is alternatively processed by photochemical etching or chemical milling, alone or in combination, with the electroforming process. Standard lithography sets for chemical milling are used to process features in theinterface layer102. Additionally, the aspect ratios and tolerances are enhanceable using laser assisted chemical milling processes.
• Themicrochannel walls110 are preferably made of Silicon. Themicrochannel walls110 are alternatively made of any other materials including, but not limited to, patterned glass, polymer, and a molded polymer mesh. Although it is preferred that themicrochannel walls110 are made from the same material as that of thebottom surface103 of theinterface layer102, themicrochannel walls110 are alternatively made from a different material than that of the rest of theinterface layer102.
• It is preferred that themicrochannel walls110 have thermal conductivity characteristics of at least 10 W/m-K. Alternatively, themicrochannel walls110 have thermal conductivity characteristics of more than 10 W/m-K. It is apparent to one skilled in the art that themicrochannel walls110 alternatively have thermal conductivity characteristics of less than 10 W/m-K, wherebycoating material112 is applied to themicrochannel walls110, as shown inFIG. 12, to increase the thermal conductivity of the wall features110. Formicrochannel walls110 made from materials already having a good thermal conductivity, thecoating112 applied has a thickness of at least 25 microns which also protects the surface of themicrochannel walls110. Formicrochannel walls110 made from material having poor thermal conductivity characteristics, thecoating112 has a thermal conductivity of at least 50 W/m-K and is more than 25 microns thick. It is apparent to one skilled in the art that other types of coating materials as well as thickness dimensions are contemplated.
• To configure themicrochannel walls110 to have an adequate thermal-conductivity of at least 10 W/m-K, thewalls110 are electroformed with the coating material112 (FIG. 12), such as Nickel or other metal, as discussed above. To configure themicrochannel walls110 to have an adequate thermal conductivity of at least 50 W/m-K, thewalls110 are electroplated with Copper on a thin metal film seed layer. Alternatively, themicrochannel walls110 are not coated with the coating material. It is understood that the thermal conductivity characteristics of themicrochannel walls110 and thecoating112, when appropriate, also apply to the pillars203 (FIG. 10) and any appropriate coating applied thereon.
• Themicrochannel walls110 are preferably formed by a hot embossing technique to achieve a high aspect ratio ofchannel walls110 along thebottom surface103 of theinterface layer102. The microchannel wall features110 are alternatively fabricated as Silicon structures deposited on a glass surface, whereby the features are etched on the glass in the desired configuration. Themicrochannel walls110 are alternatively formed by a standard lithography techniques, stamping or forging processes, or any other appropriate method. Themicrochannel walls110 are alternatively made separately from theinterface layer102 and coupled to theinterface layer102 by anodic or epoxy bonding. Alternatively, the microchannel features110 are coupled to theinterface layer102 by conventional electroforming techniques, such as electroplating.
• There are a variety of methods that can be used to fabricate theintermediate layer104. The intermediate layer is preferably made from Silicon. It is apparent to one skilled in the art that any other appropriate material is contemplated including, but not limited to glass, laser-patterned glass, polymers, metals, glass, plastic, molded organic material or any composites thereof. Preferably, theintermediate layer104 is formed using plasma etching techniques. Alternatively, theintermediate layer104 is formed using a chemical etching technique. Other alternative methods include machining, etching, extruding and/or forging a metal into the desired configuration. Theintermediate layer104 is alternatively formed by injection molding of a plastic mesh into the desired configuration. Alternatively, theintermediate layer104 is formed by laser-drilling a glass plate into the desired configuration.
• Themanifold layer106 is manufactured by a variety of methods. It is preferred that themanifold layer106 is fabricated by an injection molding process utilizing plastic, metal, polymer composite or any other appropriate material, whereby each layer is made from the same material. Alternatively, as discussed above, each layer is made from a different material. Themanifold layer106 is alternatively generated using a machined or etched metal technique. It is apparent to one skilled in the art that themanifold layer106 is manufactured utilizing any other appropriate method.
• Theintermediate layer104 is coupled to theinterface layer102 andmanifold layer106 to form theheat exchanger100 using a variety of methods. Theinterface layer102,intermediate layer104 andmanifold layer106 are preferably coupled to one another by an anodic, adhesive or eutectic bonding process. Theintermediate layer104 is alternatively integrated within features of themanifold layer106 andinterface layer102. Theintermediate layer104 is coupled to theinterface layer102 by a chemical bonding process. Theintermediate layer104 is alternatively manufactured by a hot embossing or soft lithography technique, whereby a wire EDM or Silicon master is utilized to stamp theintermediate layer104. Theintermediate layer104 is then alternatively electroplated with metal or another appropriate material to enhance the thermal conductivity of theintermediate layer104, if needed.
• Alternatively, theintermediate layer104 is formed along with the fabrication of themicrochannel walls110 in theinterface layer102 by an injection molding process. Alternatively, theintermediate layer104 is formed with the fabrication of themicrochannel walls110 by any other appropriate method. Other methods of forming the heat exchanger include, but are not limited to soldering, fusion bonding, eutectic Bonding, intermetallic bonding, and any other appropriate technique, depending on the types of materials used in each layer.
• Another alternative method of manufacturing the heat exchanger of the present invention is described inFIG. 13. As discussed in relation toFIG. 13, an alternative method of manufacturing the heat exchanger includes building a hard mask formed from a silicon substrate as the interface layer (step500). The hard mask is made from silicon dioxide or alternatively spin-on-glass. Once the hard mask is formed, a plurality of under-channels are formed in the hard mask, wherein the under-channels form the fluid paths between the microchannel walls110 (step502). The under-channels are formed by any appropriate method, including but not limited to HF etching techniques, chemical milling, soft lithography and xenon difluoride etch. In addition, enough space between each under-channel must be ensured such that under-channels next to one another do not bridge together. Thereafter, spin-on-glass is then applied by any conventional method over the top surface of the hard mask to form the intermediate and manifold layers (step504). Following, the intermediate and manifold layers are hardened by a curing method (step506). Once the intermediate and manifold layers are fully formed and hardened, one or more fluid ports are formed into the hardened layer (step508). The fluid ports are etched or alternatively drilled into the manifold layer. Although specific methods of fabricating theinterface layer102, theintermediate layer104 andmanifold layer106 are discussed herein, other known methods known in art to manufacture theheat exchanger100 are alternatively contemplated.
• FIG. 14 illustrates an alternative embodiment of the heat exchanger of the present invention. As shown inFIG. 6, twoheat exchangers200,200′ are coupled to oneheat source99. In particular, theheat source99, such as an electronic device, is coupled to a circuit board96 and is positioned upright, whereby each side of theheat source99 is potentially exposed. A heat exchanger of the present invention is coupled to one exposed side of theheat source99, whereby bothheat exchangers200,200′ provide maximum cooling of theheat source99. Alternatively, the heat source is coupled to the circuit board horizontally, whereby more than one heat exchanger is stacked on top of the heat source99 (not shown), whereby each heat exchanger is electrically coupled to theheat source99; More details regarding this embodiment are shown and described in co-pending U.S. patent application Ser. No. 10/072,137, filed Feb. 7, 2002, entitled “POWER CONDITIONING MODULE” which is hereby incorporated by reference.
• As shown inFIG. 14, theheat exchanger200 having two layers is coupled to the left side of theheat source99 and theheat exchanger200′ having three layers is coupled to the right side of theheat source99. It is apparent to one skilled in the art that the preferred or alternative heat exchangers are coupled to the sides of theheat source99. It is also apparent to one skilled in the art that the alternative embodiments of theheat exchanger200′ are alternatively coupled to the sides of theheat source99. The alternative embodiment shown inFIG. 14 allows more precise hot spot cooling of theheat source99 by applying fluid to cool hot spots which exist along the thickness of theheat source99. Thus, the embodiment inFIG. 14 applies adequate cooling to hot spots in the center of theheat source99 by exchanging heat from both sides of theheat source99. It is apparent to one skilled in the art that the embodiment shown inFIG. 14 is used with thecooling system30 inFIGS. 2A-2B, although other closed loop systems are contemplated.
• As stated above, theheat source99 may have characteristics in which the locations of one or more of the hot spots change due to different tasks required to be performed by theheat source99. To adequately cool theheat source99, thesystem30 alternatively includes a sensing and control module34 (FIGS. 2A-2B) which dynamically changes the amount of flow and/or flow rate of fluid entering theheat exchanger100 in response to a change in location of the hot spots.
• In particular, as shown inFIG. 14, one ormore sensors124 are placed in each interface hot spot region in theheat exchanger200 and/or alternatively theheat source99 at each potential hot spot location. Alternatively, a plurality of heat sources are uniformly placed in between the heat source and heat exchanger and/or in the heat exchanger itself. The control module38 (FIG. 2A-2B) is also coupled to one or more valves in theloop30 which control the flow of fluid to theheat exchanger100. The one or more valves are positioned within the fluid lines, but are alternatively positioned elsewhere. The plurality ofsensors124 are coupled to the control module34, whereby the control module34 is preferably placed upstream fromheat exchanger100, as shown inFIG. 2. Alternatively, the control module34 is placed at any other location in theclosed loop system30.
• Thesensors124 provide information to the control module34 including, but not limited to, the flow rate of fluid flowing in the interface hot spot region, temperature of theinterface layer102 in the interface hot spot region and/orheat source99 and temperature of the fluid. For example, referring to the schematic inFIG. 14, sensors positioned on theinterface124 provide information to the control module34 that the temperature in a particular interface hot spot region inheat exchanger200 is increasing whereas the temperature in a particular interface hot spot region inheat exchanger200′ is decreasing. In response, the control module34 increases the amount of flow toheat exchanger200 and decreases the amount of flow provided toheat exchanger200′. Alternatively, the control module34 alternatively changes the amount of flow to one or more interface hot spot regions in one or more heat exchangers in response to the information received from thesensors118. Although thesensors118 are shown with the twoheat exchangers200,200′ inFIG. 14, it is apparent that thesensors118 are alternatively coupled with only one heat exchanger.
• The present invention has been described in terms of specific embodiments incorporating details to facilitate the understanding of the principles of construction and operation of the invention. Such reference herein to specific embodiments and details thereof is not intended to limit the scope of the claims appended hereto. It will be apparent to those skilled in the art that modification s may be made in the embodiment chosen for illustration without departing from the spirit and scope of the invention.

Claims (93)

1. A heat exchanger comprising:

a. an interface layer for cooling a heat source, wherein the interface layer is configured to pass fluid therethrough and the interface layer includes a thickness within a range of about 0.3 millimeters to about 1.0 millimeters; and

b. a manifold layer for circulating fluid to and from the interface layer, the manifold layer having a first set fingers and a second set of fingers, wherein the first set of fingers are disposed in parallel with the second set of fingers and arranged to reduce pressure drop within the heat exchanger.

2. The heat exchanger according toclaim 1 wherein the fluid is in single phase flow condition.

3. The heat exchanger according toclaim 1 wherein the fluid is in two phase flow fluid conditions.

4. The heat exchanger according toclaim 1 wherein at least a portion of the fluid undergoes a transition between single and two phase flow conditions in the interface layer.

5. The heat exchanger according toclaim 1 wherein a particular finger in the first set is spaced apart by an appropriate dimension from a particular finger in the second set to minimize the pressure drop in the heat exchanger.

6. The heat exchanger according toclaim 1 wherein each of the fingers have the same length and width dimensions.

7. The heat exchanger according toclaim 1 wherein at least one of the fingers has a different dimension than the remaining fingers.

8. The heat exchanger according toclaim 1 wherein the fingers are arranged non-periodically in at least one dimension in the manifold layer.

9. The heat exchanger according toclaim 1 wherein at least one of the fingers has at least one varying dimension along a length of the manifold layer.

10. The heat exchanger according toclaim 1 wherein the manifold layer includes more than three and less than 10 parallel fingers.

11. The heat exchanger according toclaim 1 wherein the fingers in the first set and second set are alternately disposed along a dimension of the manifold layer.

12. The heat exchanger according toclaim 1 wherein the manifold layer is configured to cool at least one interface hot spot region.

13. The heat exchanger according toclaim 1 further comprising at least one first port in communication with the first set of fingers, wherein fluid enters the heat exchanger through the at least one first port.

14. The heat exchanger according toclaim 13 further comprising at least one second port in communication with the second set of fingers, wherein fluid exits the heat exchanger through the at least one second port.

15. The heat exchanger according toclaim 1 wherein the manifold layer is positioned above the interface layer, wherein fluid flows downward through the first set of fingers and upward though the second set of fingers.

16. The heat exchanger according toclaim 13 further comprising a first port passage in communication with the first port and the first set of fingers, the first port passage configured to channel fluid from the first port to the first set of fingers.

17. The heat exchanger according toclaim 16 further comprising a second port passage in communication with the second port and the second set of fingers, the second port passage configured to channel fluid from the second set of fingers to the second port.

18. The heat exchanger according toclaim 1 wherein the interface layer is integrally formed with the heat source.

19. The heat exchanger according toclaim 1 wherein the interface layer is coupled to the heat source.

20. The heat exchanger according toclaim 1 further comprising an intermediate layer for channeling fluid to and from one or more predetermined positions in the interface layer via at least one conduit, the intermediate layer positioned between the interface layer and the manifold layer.

21. The heat exchanger according toclaim 20 wherein the intermediate layer is coupled to the interface layer and the manifold layer.

22. The heat exchanger according toclaim 20 wherein the intermediate layer is integrally formed with the interface layer and the manifold layer.

23. The heat exchanger according toclaim 20 wherein the at least one conduit has at least one varying dimension along the intermediate layer.

24. The heat exchanger according toclaim 1 wherein the interface layer includes a coating thereupon, wherein the coating provides an appropriate thermal conductivity of at least 10 W/m-K.

25. The heat exchanger according toclaim 1 wherein the interface layer has a thermal conductivity of at least 100 W/m-K.

26. The heat exchanger according toclaim 1 further comprising a plurality of pillars configured in a predetermined pattern along the interface layer.

27. The heat exchanger according toclaim 26 wherein at least one of the plurality of pillars has an area dimension within the range of and including (10 micron)²and (100 micron)².

28. The heat exchanger according toclaim 26 wherein at least one of the plurality of pillars has a height dimension within the range of and including 50 microns and 2 millimeters.

29. The heat exchanger according toclaim 26 wherein at least two of the plurality of pillars are separate from each other by a spacing dimension within the range of and including 10 to 150 microns.

30. The heat exchanger according toclaim 26 wherein the plurality of pillars include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K.

31. The heat exchanger according toclaim 1 wherein the interface layer has a roughened surface.

32. The heat exchanger according toclaim 1 wherein the interface layer includes a micro-porous structure disposed thereon.

33. The heat exchanger according toclaim 32 wherein the porous microstructure has a porosity within the range of and including 50 to 80 percent.

34. The heat exchanger according toclaim 32 wherein the porous microstructure has an average pore size within the range of and including 10 to 200 microns.

35. The heat exchanger according toclaim 32 wherein the porous microstructure has a height dimension within the range of and including 0.25 to 2.00 millimeters.

36. The heat exchanger according toclaim 1 further comprises a plurality of microchannels configured in a predetermined pattern along the interface layer.

37. The heat exchanger according toclaim 36 wherein at least one of the plurality of microchannels has an area dimension within the range of and including (10 micron)²and (100 micron)².

38. The heat exchanger according toclaim 36 wherein at least one of the plurality of microchannels has a height dimension within the range of and including 50 microns and 2 millimeters.

39. The heat exchanger according toclaim 36 wherein at least two of the plurality of microchannels are separate from each other by a spacing dimension within the range of and including 10 to 150 microns.

40. The heat exchanger according toclaim 36 wherein at least one of the plurality of microchannels has a width dimension within the range of and including 10 to 100 microns.

41. The heat exchanger according toclaim 36 wherein the plurality of microchannels are coupled to the interface layer.

42. The heat exchanger according toclaim 36 wherein the plurality of microchannels are integrally formed with the interface layer.

43. The heat exchanger according toclaim 36 wherein the plurality of microchannels are divided into segmented arrays with at least one groove disposed therebetween, wherein the at least one groove is aligned with a corresponding finger.

44. The heat exchanger according toclaim 36 wherein the plurality of microchannels include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K.

45. The heat exchanger according toclaim 1 wherein an overhang dimension is within the range of and including 0 to 15 millimeters.

46. A heat exchanger for cooling a heat source comprising:

a. a manifold layer including a first set of fingers in a first configuration, wherein each finger in the first set channels fluid at a first temperature, the manifold layer further including a second set of fingers in a second configuration, wherein each finger in the second set channels fluid at a second temperature, the first set and second set of fingers arranged parallel to each other; and

b. an interface layer including a thickness within a range of about 0.3 to 1.0 millimeters, and configured to receive fluid at the first temperature at a plurality of first locations, wherein each first location is associated with a corresponding finger in the first set, the interface layer passing fluid along a plurality of predetermined paths to a plurality of second locations, wherein each second location is associated with a corresponding finger in the second set.

47. The heat exchanger according toclaim 46 wherein the fluid is in single phase flow conditions.

48. The heat exchanger according toclaim 46 wherein the fluid is in two phase flow conditions.

49. The heat exchanger according toclaim 46 wherein at least a portion of the fluid undergoes a transition between single and two phase flow conditions in the interface layer.

50. The heat exchanger according toclaim 46 wherein a particular finger in the first set is spaced apart by an appropriate dimension from a particular finger in the second set, wherein the appropriate dimension reduces the pressure drop in the heat exchanger.

51. The heat exchanger according toclaim 46 further comprising at least one first port in communication with the first set of fingers, wherein fluid enters the heat exchanger through the at least one first port.

52. The heat exchanger according toclaim 51 further comprising at least one second port in communication with the second set of fingers, wherein fluid exits the heat exchanger through the at least one second port.

53. The heat exchanger according toclaim 46 wherein the manifold layer is positioned above the interface layer, wherein fluid flows downward through the first set of fingers and upward through the second set of fingers.

54. The heat exchanger according toclaim 46 wherein the interface layer is integrally formed with the heat source.

55. The heat exchanger according toclaim 46 wherein the interface layer is coupled to the heat source.

56. The heat exchanger according toclaim 46 wherein the fingers in the first set are positioned in an alternating configuration with the fingers in the second set.

57. The heat exchanger according toclaim 46 wherein each of the fingers have the same length and width dimensions.

58. The heat exchanger according toclaim 46 wherein at least one of the fingers has a different dimension than the remaining fingers.

59. The heat exchanger according toclaim 46 wherein the fingers are arranged non-periodically in at least one dimension in the manifold layer.

60. The heat exchanger according toclaim 46 wherein at least one of the fingers has at least one varying dimension along a length of the manifold layer.

61. The heat exchanger according toclaim 46 wherein the manifold layer includes more than three and less than 10 parallel fingers.

62. The heat exchanger according toclaim 52 further comprising a first port passage in communication with the first port and the first set of fingers, the first port passage configured to channel fluid from the first port to the first set of fingers.

63. The heat exchanger according toclaim 62 further comprising a second port passage in communication with the second port and the second set of fingers, the second port passage configured to channel fluid from the second set of fingers to the second port.

64. The heat exchanger according toclaim 46 further comprising an intermediate layer for channeling fluid to and from one or more predetermined positions in the interface layer via at least one conduit, the intermediate layer positioned between the interface layer and the manifold layer.

65. The heat exchanger according toclaim 64 wherein the conduit is arranged in a predetermined configuration to channel fluid to one or more interface hot spot regions in the interface layer.

66. The heat exchanger according toclaim 64 wherein the conduit is arranged in a predetermined configuration to channel fluid from one or more interface hot spot regions in the interface layer.

67. The heat exchanger according toclaim 64 wherein the intermediate layer is coupled to the interface layer and the manifold layer.

68. The heat exchanger according toclaim 64 wherein the intermediate layer is integrally formed with the interface layer and the manifold layer.

69. The heat exchanger according toclaim 64 wherein the conduit has at least one varying dimension in the intermediate layer.

70. The heat exchanger according toclaim 46 wherein the interface layer includes a coating thereupon, wherein the coating provides an appropriate thermal conductivity of at least 10 W/m-K.

71. The heat exchanger according toclaim 46 wherein the interface layer has a thermal conductivity is at least 100 W/m-K.

72. The heat exchanger according toclaim 46 further comprising a plurality of pillars configured in a predetermined pattern along the interface layer.

73. The heat exchanger according toclaim 72 wherein at least one of the plurality of pillars has an area dimension within the range of and including (10 micron)²and (100 micron)².

74. The heat exchanger according toclaim 72 wherein at least one of the plurality of pillars has a height dimension within the range of and including 50 microns and 2 millimeters.

75. The heat exchanger according toclaim 72 wherein at least two of the plurality of pillars are separate from each other by a spacing dimension within the range of and including 10 to 150 microns.

76. The heat exchanger according toclaim 72 wherein the plurality of pillars include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K.

77. The heat exchanger according toclaim 46 wherein the interface layer has a roughened surface.

78. The heat exchanger according toclaim 46 wherein the interface layer includes a microporous structure disposed thereon.

79. The heat exchanger according toclaim 78 wherein the porous microstructure has a porosity within the range of and including 50 to 80 percent.

80. The heat exchanger according toclaim 78 wherein the porous microstructure has an average pore size within the range of and including 10 to 200 microns.

81. The heat exchanger according toclaim 78 wherein the porous microstructure has a height dimension within the range of and including 0.25 to 2.00 millimeters.

82. The heat exchanger according toclaim 46 further comprises a plurality of microchannels configured in a predetermined pattern along the interface layer.

83. The heat exchanger according toclaim 82 wherein at least one of the plurality of microchannels has an area dimension within the range of and including (10 micron)²and (100 micron)².

84. The heat exchanger according toclaim 82 wherein at least one of the plurality of microchannels has a height dimension within the range of and including 50 microns and 2 millimeters.

85. The heat exchanger according toclaim 82 wherein at least two of the plurality of microchannels are separate from each other by a spacing dimension within the range of and including 10 to 150 microns.

86. The heat exchanger according toclaim 82 wherein at least one of the plurality of microchannels has a width dimension within the range of and including 10 to 100 microns.

87. The heat exchanger according toclaim 82 wherein the microchannels are coupled to the interface layer.

88. The heat exchanger according toclaim 82 wherein the microchannels are integrally formed with the interface layer.

89. The heat exchanger according toclaim 82 wherein the microchannels are divided into segments along a dimension of the interface layer, at least one groove disposed in between the divided microchannel segments.

90. The heat exchanger according toclaim 82 wherein the microchannels are continuous along a dimension of the interface layer.

91. The heat exchanger according toclaim 89 wherein the at least one groove is aligned with a corresponding finger.

92. The heat exchanger according toclaim 82 wherein the plurality of microchannels include a coating thereupon, wherein the coating has an appropriate thermal conductivity of at least 10 W/m-K.

93. The heat exchanger according toclaim 46 wherein an overhang dimension is within the range of and including 0 to 15 millimeters.

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