# Patent

## Title
Heat sink module

## Abstract

A heat sink module for cooling a heat providing surface can include an inlet chamber and an outlet chamber formed within the heat sink module. The outlet chamber can have an open portion that can be enclosed by the heat providing surface when the heat sink module is installed on the heat providing surface. The heat sink module can include a dividing member disposed between the inlet chamber and the outlet chamber. The dividing member can include a first plurality of orifices extending from a top surface of the dividing member to a bottom surface of the dividing member. The first plurality of orifices can be configured to deliver a plurality of jet streams of coolant into the outlet chamber and against the heat providing surface when the heat sink module is installed on the heat providing surface and when pressurized coolant is provided to the inlet chamber.

## Background
CROSS-REFERENCE TO RELATED APPLICATIONS
This application claims the benefit of U.S. Provisional Patent Application No. 62/069,301 filed Oct. 27, 2014; U.S. Provisional Patent Application No. 62/072,421 filed Oct. 29, 2014; and U.S. Provisional Patent Application No. 62/099,200 filed Jan. 1, 2015, each of which is hereby incorporated by reference in its entirety as if fully set forth in this description.


FIELD
This disclosure relates to methods, apparatuses, components, and assemblies for cooling one or more heat sources, such as one or more mechanical, electrical, or electromechanical devices that produce or transfer heat.
BACKGROUND
Maintaining electronic devices, such as microprocessors in data centers, within safe operating temperature ranges is a challenging problem that is only increasing in importance and difficulty as semiconductor technology continues to progress and as popularity of cloud storage continues to grow. State of the art microprocessors can easily produce more than 40 watts of thermal energy per square centimeter of microchip surface area, and power electronics can attain heat densities three times that level.
In addition to the need to manage such high heat densities, there is also a need to do so in an efficient manner, in terms of energy expended to cool these heat sources. According to the Department of Energy, nearly three percent of electricity used in the United States is devoted to powering data centers or computer facilities. Approximately half of this electricity goes toward power conditioning and cooling. Increasing the efficiency of cooling systems would lead to dramatic savings in energy nationwide. More efficient cooling is also needed in transportation systems due to the rapidly increasing adoption of hybrid and electric vehicles that rely on complex electrical systems, including electric motors and batteries that produce significant amounts of heat. More efficient cooling of these electronic systems would translate to increased driving range and utility of the vehicles.
Attempts to cool modern microprocessors using conventional air-cooling techniques have resulted in cooling systems with large heat sinks and large, power-consuming fans. In a common arrangement, a large heat sink is mounted on the microprocessor, and a large fan is mounted within a housing of the computer such that the fan draws cool room air into the housing and forces warm air out of the housing. But fans can be noisy, especially when many computers are provided in a common location, such as a data center, and each computer has one or more fans operating at high speeds. In addition, each metallic heat sink adds mass and cost to the computer and places mechanical stress on the microprocessor to which it is mounted. This stress can damage the microprocessor during transportation and handling and can fatigue the electrical connections (e.g. soldered connections) that connect the microprocessor to the motherboard of the computer. Operating speeds of next generation microprocessors will continue to increase, as will heat fluxes associated therewith, where heat flux is defined as heat load per unit area. Conventional air-cooling systems will soon be incapable of efficiently and effectively cooling these next generation microprocessors.
Currently, the majority of computer systems in residential and commercial settings are cooled using forced air cooling systems in which room air is forced, by one or more fans, over a series of extended metal surfaces (i.e. fins) coupled to microchips or other electronic components, such as power supplies. Cooling fans typically operate at high speeds and can be quite noisy. As the air passes over the electronic components, the air, which is at a lower temperature than the surfaces of the electronic components, absorbs heat from the electronic components, thereby cooling the components. These air-cooled systems are inherently limited in terms of performance and efficiency due to the low volumetric heat capacity of air, which is much lower than the volumetric heat capacity of water and other liquids. Because air has such a low heat capacity, high air flow rates are required to ensure adequate cooling of even relatively small heat loads. For instance, an air flow rate of 5 to 10 cubic feet per minute (“cfm”) is needed to cool a 100-watt heat load. For heat sources such as microprocessors, which as mentioned above can easily produce more than 40 watts per square centimeter, very high volumetric air flow rates are required to remove heat from the microprocessor to prevent overheating and intervention by a thermal protection mechanism that will reduce the processor speed to decrease its temperature. For an installation of one rack of servers, which is commonly used in computer rooms of small businesses and schools, two air conditioning units sized for a typical U.S. home are required to cool the computer room. Typical data centers, which can have several hundred racks of servers, must be equipped with special computer room air conditioning (“CRAC”) units that are large and expensive and must be professionally installed, often requiring substantial physical modifications to the facility to accommodate the CRAC, including installation of custom air ducting.
Air-cooled systems are not only inefficient at removing heat from electronics, but they also cause the electronics they cool to operate less efficiently. A typical microprocessor operates less efficiently as its junction temperature increases. FIG. 64 shows a plot of CPU power consumption in watts versus junction temperature. The bottom curve shows static power consumption of the microprocessor and the top curves show total power consumption for switching speeds of 1.6 GHz and 2.4 GHz, respectively. Total power consumption includes both static power consumption and dynamic power consumption, which varies with switching frequency. As shown in FIG. 64, as the temperature of the microprocessor increases, it consumes more power to provide the same performance. In air-cooled systems, it is common for fully utilized microprocessors to operate at or near their maximum rated temperature, resulting in poor operating efficiency. In the example shown in FIG. 64, the microprocessor uses over 35% more power when operating at 370K than when operating at 320K.
Pumped liquid cooling systems have been used to provide improved thermal performance over conventional air-cooling systems. Pumped liquid cooling systems typically include a heat sink that is attached to the microprocessor or other circuit to be cooled, a liquid-to-air heat exchanger, a single phase liquid pump, and connection tubing. A thermally conductive liquid coolant is circulated through the system by the pump. As the liquid passes through channels in the heat sink, heat from the hot processor is transferred to the heat sink and to the cooler liquid. The heat sink is typically designed to maximize heat transfer by maximizing the surface area of the channels through which the liquid passes. For example, micro-channel heat sinks utilize very fine fin channels through which cooling fluid flows. The hot liquid exiting the heat sink is then circulated through the liquid-to-air heat exchanger before circulating back to the liquid pump for another cycle. Use of such closed liquid cooling systems is beginning to migrate from high performance computers to personal computers. However, even the best pumped liquid cooling systems are limited in their ability to maintain low device temperatures without the use of refrigeration and will not be able to satisfy the cooling demands of next-generation microprocessors. Without further innovation in the area of heat removal systems the development of next-generation microprocessors and other electronic devices will be hampered.
As noted above, liquid cooling systems commonly rely on flowing single-phase water through channels in finned heat sinks. The heat sinks are often indirectly coupled to a heat source via a metal base plate, thermal paste (e.g. solder thermal interface material (“STIM”) or polymer thermal interface material (“PTIM”)), and/or a direct bond adhesive. While this approach can be more effective than air-cooling, the intervening materials between the water and the heat source (e.g. microprocessor) induce significant thermal resistance, which reduces the overall efficiency of the cooling system. In addition to higher thermal resistance, the intervening materials add to the cost and time of manufacture and assembly, constitute additional points of failure, and create potential disposal issues. Finally, the intervening materials render the system unable to adapt to local hot spots on a heat source. Consequently, the entire liquid cooling system must be designed to accommodate the maximum anticipated heat load of one or more localized hot spots on the surface of the heat source, resulting in additional cost and complexity.
Further improvements have been made to liquid-cooled systems by using coolants other than water. Unlike water, dielectric coolants can be placed in direct contact with electronic devices and not harm them. Use of such dielectric coolants can eliminate a significant amount of thermal interface material from the system. However, some dielectric coolants have a lower heat capacity than water, so more aggressive cooling techniques may be required to achieve a desired performance.
Immersion cooling is an aggressive form of liquid cooling where an entire electronic device is submerged in a vat of dielectric coolant. Unfortunately, immersion cooling requires vats that are large, costly, and heavy, especially when filled with a dielectric coolant. Typically, a room must be specially engineered to accommodate an immersion cooling vat, and containment systems may need to be designed and installed in the room as a precaution against vat failure. Immersion cooling can require large volumes of costly dielectric coolants. Another downside of immersion cooling is that certain coolants may act as solvents and, over time, remove certain identifying information (e.g. printed serial numbers or model numbers) from electronic components on a motherboard, which can make servicing the computer more difficult.
Another liquid cooling approach involves atomized sprays, in which atomized liquid coolant is sprayed directly on a surface through air or vapor. As a result, small droplets impinge on the heated surface forming a thin film of liquid directly on the computer chips. Heat is then transferred from the heated surface to the liquid either by sensible heating of the bulk liquid or by boiling off of a fraction of the liquid (i.e. latent heating). Although high heat removal rates can be achieved, a limiting heat flux is reached when the bulk liquid warms (e.g. through sensible heating) to its boiling point at any location on the surface being cooled. At this location, the surface will eventually dry out, at which point the surface temperature will rise very quickly, and the device may be damaged. This method of heat removal is known as spray cooling or spray evaporative cooling and is a very efficient method of removing high heat fluxes from small surfaces. Unfortunately, the margin for error in spray cooling systems is very narrow and the onset of dry out is a constant concern that can have costly consequences.
Spray cooling is limited by several factors. First, spray cooling requires a significant working volume to enable atomized sprays to form. Second, atomizing the liquid requires a significant amount of pressure upstream of the atomizer to generate an appropriate pressure drop at the atomizer-air interface to enable atomized sprays to form. Maintaining this amount of pressure within the system consumes a significant amount of energy. Third, high flow rates of atomized sprays are required to prevent dry out or critical heat flux from being attained. Critical heat flux is a condition where evaporation of coolant from the surface to be cooled 12 prevents atomized liquid from reaching the surface and cooling the surface. In the end, it has proven difficult to design a practical and compact spray cooling system, despite the large amount of time and effort that has been expended to do so.
Another liquid cooling approach involves direct jet impingement, where streams of liquid are projected through a liquid medium and impinge directly on a surface to be cooled 12. While impinging jets are known to have notable heat transfer performance, impinging jet systems have problems of scalability. To achieve high heat transfer over a large area, arrays of jets must be used. The use of arrays in conventional direct jet impingement systems, however, is problematic. Opposing surface flows of fluid from neighboring jet streams emitted from the array of jets can induce stagnant regions on the surface to be cooled 12. Stagnation regions prevent cooler fluid from mixing with warmer fluid in the stagnation regions, leading to bubble growth and dry out at the surface being cooled as the warmer fluid experiences phase change. Thus, the interaction of jet streams can lead to inefficient cooling caused by liquid build-up on the heated surface, creating regions of poor heat transfer and non-uniform heat transfer across the surface being cooled. In the regions of poor heat transfer, the surface temperatures can rise significantly above the average surface temperature, causing the surface temperature in these regions to “run away,” leading to catastrophic failure of the device being cooled.
Conventional jet impingement systems use nozzles that are part of a large, flat nozzle plate. As fluid from jet streams impinging on the surface being cooled flow outward from the center of the surface, the fluid can have sufficient momentum to completely deflect the outermost jets, preventing them from impinging on the heated surface near the edge of the surface. As a result of these factors, conventional impinging jet systems are limited in size. In addition, existing nozzle plates can be costly and complex to manufacture.
In view of the foregoing discussion, efficient, scalable methods and apparatuses are needed for cooling surfaces of devices, such as next-generation microprocessors and electronic circuitry, capable of producing high heat fluxes.



BRIEF DESCRIPTIONS OF DRAWINGS
FIG. 1 shows a front perspective view of a cooling apparatus installed on a row of server racks in a data center.
FIG. 2A shows a rear view of the cooling apparatus of FIG. 1.
FIG. 2B shows a detailed view of a portion of the cooling apparatus of FIG. 2A, where the pump, reservoir, heat exchanger, inlet manifold of the primary cooling loop, and sections of flexible tubing are visible.
FIG. 3 shows a left side view of the cooling apparatus of FIG. 1, where the pump, reservoir, heat exchanger, pressure regulator, first bypass, and a portion of the primary cooling loop are visible.
FIG. 4 shows an inlet manifold and an outlet manifold of the cooling apparatus and sections of flexible tubing with quick-connect fittings connecting parallel cooling lines to the inlet and outlet manifolds.
FIG. 5 shows a top perspective view of a server with its lid removed and a portion of a cooling apparatus installed within the server, the cooling apparatus having a two heat sink modules mounted on vertically-arranged heat-generating components within the server, the heat sink modules arranged in a series configuration and fluidly connected with sections of flexible tubing to transport coolant from an outlet port of a first heat sink module to an inlet port of a second heat sink module.
FIG. 6 shows a top view of a server with its lid removed and a portion of a cooling apparatus installed within the server, the cooling apparatus including two heat sink modules mounted on horizontally-oriented microprocessors within the server, the heat sink modules arranged in a series configuration and fluidly connected with a section of flexible tubing to transport coolant from an outlet port of a first heat sink module to an inlet port of a second heat sink module.
FIG. 7 shows a cooling assembly including a heat sink module, a first section of flexible tubing fluidly connected to an inlet port of the heat sink module, and a second section of flexible tubing fluidly connected to an outlet port of the heat sink module.
FIG. 8 shows a plot of power consumption versus time for a computer room with forty active dual-processor servers initially cooled by a CRAC and then cooled by the CRAC and the cooling apparatus described herein, where the cooling apparatus described herein provides substantial reductions in power consumption despite being installed on just ten of the forty servers in the computer room.
FIG. 9 shows a front perspective view of a redundant cooling apparatus installed on eight racks of servers in a data center where the redundant cooling apparatus includes two fully independent primary cooling loops.
FIG. 10 shows a rear view of the redundant cooling apparatus of FIG. 9.
FIG. 11A shows a schematic of a cooling apparatus having one heat sink module mounted on a heat-generating surface and fluidly connected to a primary cooling loop.
FIG. 11B shows the schematic of FIG. 11A with a primary cooling loop identified by dashed lines.
FIG. 11C shows the schematic of FIG. 11A with a first bypass identified by dashed lines.
FIG. 11D shows the schematic of FIG. 11A with a second bypass identified by dashed lines.
FIG. 12A shows a schematic of a cooling apparatus having one heat sink module mounted on a heat source and a pressure regulator located downstream of the heat exchanger in the first bypass.
FIG. 12B shows a schematic of a cooling apparatus having two pumps arranged in parallel for redundancy in case one pump fails.
FIG. 12C shows a schematic of a cooling apparatus having a three-way valve at a junction between the primary cooling loop and the bypass.
FIG. 12D shows a schematic of a cooling apparatus having a three-way valve at the junction between the primary cooling loop and the bypass, where the bypass contains a heat exchanger.
FIG. 12E shows a schematic of a cooling apparatus including a first bypass and a primary cooling loop where the primary cooling loop includes a heat sink module with an internal bypass having a pressure regulator.
FIG. 12F shows a schematic of a cooling apparatus having a primary cooling loop and one bypass.
FIG. 12G shows a schematic of a cooling apparatus where the primary cooling loop includes a heat sink module with an internal bypass having a pressure regulator.
FIG. 12H shows a schematic of a cooling apparatus including a pump, reservoir, and a heat sink module that is configured to mount on a heat source or be mounted in thermal communication with a heat source.
FIG. 12I shows a schematic of a cooling apparatus including a pump and a heat sink module that is configured to mount on a heat source or be mounted in thermal communication with a heat source.
FIG. 12J shows a schematic of a cooling apparatus with a primary cooling loop, a first bypass, and a second bypass, where the primary cooling loop includes a first pump, and the first bypass includes a second pump.
FIG. 12K shows a schematic of a cooling apparatus with a primary cooling loop, a first bypass, and a second bypass, where the primary cooling loop includes a first pump, and the second bypass includes a second pump.
FIG. 12L shows a schematic of a cooling apparatus with a primary cooling loop, a first bypass, and a second bypass, where the primary cooling loop includes a first pump, the first bypass includes a second pump, and the second bypass includes a third pump.
FIG. 12M shows a schematic of a cooling apparatus with a primary cooling loop, a first bypass, and a second bypass, where the first bypass includes a first heat exchanger, and the second bypass includes a second heat exchanger.
FIG. 12N shows a schematic of a cooling apparatus having a primary cooling loop, a first bypass, and a second bypass, where the first bypass and second bypass merge upstream of a reservoir.
FIG. 12O shows a schematic of a cooling apparatus having a primary cooling loop, a first bypass, and a second bypass, where the first bypass and second bypass merge upstream of a reservoir and upstream of a heat exchanger.
FIG. 12P shows a schematic of a cooling apparatus having a primary cooling loop with redundant pumps, a first bypass, and a second bypass, where the second bypass is connected to a heat exchanger that can be a rooftop dry cooler.
FIG. 12Q shows a schematic of a cooling apparatus having a primary cooling loop and a bypass, where the bypass is connected to a heat exchanger that can be a rooftop dry cooler.
FIG. 12R shows a schematic of a cooling apparatus having a primary cooling loop having a pump, a reservoir, and a heat sink module mounted on a surface to be cooled.
FIG. 12S shows a schematic of a cooling apparatus having a primary cooling loop, a first bypass, and a second bypass, where the first bypass includes a first heat exchanger, and where the primary cooling loop includes two series-connected heat sink modules with a second heat exchanger fluidly connected between the heat sink modules to, for example, avoid formation of slug flow in the primary cooling loop between the heat sink modules.
FIG. 12T shows a schematic of a cooling apparatus configured to cool two racks of servers, the cooling apparatus including an inlet manifold and an outlet manifold for each rack of servers, where a plurality of heat sink modules are fluidly connected in series and parallel arrangements between each inlet and outlet manifold to cool hot spots within the servers.
FIG. 13 shows a schematic of a cooling apparatus including a filter located between the reservoir and a pump inlet in the primary cooling loop.
FIG. 14 shows a schematic of a cooling apparatus having three heat sink modules arranged in a series configuration on three surfaces to be cooled.
FIG. 15 shows a portion of a primary cooling loop of a cooling apparatus, where the cooling loop includes three series-connected heat sink modules mounted on three surfaces to be cooled and connected by sections of flexible tubing where a single-phase liquid coolant is provided to a first heat sink module, and due to heat transfer occurring within the first module, two-phase bubbly flow is transported from the first module to the second module, and due to heat transfer occurring within the second module, higher quality two-phase bubbly flow is transported from the second module to the third module, and due to heat transfer occurring within the third module, even higher quality two-phase bubbly flow is transported out of the third module.
FIG. 16 shows a schematic of a cooling apparatus with a primary cooling loop that includes three parallel cooling lines where each parallel cooling line includes three heat sink modules fluidly connected in series.
FIG. 17 shows a schematic of a redundant cooling apparatus having a redundant heat sink module mounted on a surface to be cooled.
FIG. 18 shows a schematic of a redundant cooling apparatus with a first primary cooling loop that includes two parallel cooling lines where each parallel cooling line is fluidly connected to three redundant heat sink modules arranged in series, and a second primary cooling loop that includes two parallel cooling lines where each parallel cooling line is fluidly connected to three redundant heat sink modules arranged in series.
FIG. 19 shows a top view of a redundant cooling apparatus installed in a data center having twenty racks of servers, the redundant cooling system being connected to heat exchangers located inside of the room where the data center is located.
FIG. 20 shows a top view of a redundant cooling apparatus installed in a data center having twenty racks of servers, the redundant cooling system being connected to heat exchangers located outside of the room where the data center is located.
FIG. 21 shows a top perspective view of a heat sink module for cooling a heat source.
FIG. 22 shows a top view of heat sink module of FIG. 21, the heat sink module including a first compression fitting installed on an inlet port of the heat sink module, a second compression fitting installed on an outlet port of the heat sink module, and a plurality of fasteners arranged near a perimeter of the heat sink module and according to a mounting pattern for mounting the heat sink module to a heat-providing surface.
FIG. 23 shows a bottom perspective view of the heat sink module of FIG. 21 showing an inlet port, outlet port, outlet chamber, mounting holes, dividing member, and a plurality of orifices in the dividing member, as well as a sealing member installed within a continuous channel circumscribing the outlet chamber of the heat sink module.
FIG. 24 shows a bottom view of the heat sink module of FIG. 21.
FIG. 25 shows a side cross-sectional view of the heat sink module of FIG. 24 taken along section B-B and showing an inlet port, inlet passage, inlet chamber, a plurality of orifices, and outlet chamber within the heat sink module.
FIG. 26 shows a side cross-sectional view of the heat sink module of FIG. 24 taken along section B-B with the heat sink module being mounted on a thermally conductive base member and showing central axes of the plurality of orifices and bubble formation within the outlet chamber proximate the surface of the thermally conductive base member.
FIG. 27 shows a side cross-sectional view of the heat sink module of FIG. 24 taken along section B-B with the heat sink module mounted on a computer processor located on a motherboard and showing central axes of the plurality of orifices.
FIG. 28 shows a side cross-sectional view of the heat sink module of FIG. 24 taken along section B-B with the heat sink module mounted on a thermally conductive base member that is attached to a microprocessor by a layer of thermal interface material, the microprocessor being electrically connected to a motherboard.
FIG. 29 shows a side cross-sectional view of the heat sink module of FIG. 24 taken along section A-A and showing an inlet port, outlet port, outlet passage, outlet chamber, and a plurality of orifices within the heat sink module.
FIG. 30 shows a side cross-sectional view of the heat sink module of FIG. 24 taken along section A-A, with the heat sink module mounted on a thermally conductive base member and showing central axes of the plurality of orifices and bubbles forming within the outlet chamber proximate the surface of the conductive base member and exiting the module through the outlet port as part of a two-phase bubbly flow.
FIG. 31 shows a top cross-sectional view of the heat sink module of FIG. 21 taken along section C-C shown in FIG. 25, the cross-section passing horizontally through a dividing member of the heat sink module to expose an array of orifices within the heat sink module, the orifices arranged according to staggered columns and staggered rows.
FIG. 32 shows a top view of a surface to be cooled within an outlet chamber of a heat sink module of FIG. 21 taken along section D-D shown in FIG. 30, where an array of jet streams originating from the plurality of orifices of the heat sink module are impinging non-perpendicularly on the surface to be cooled, thereby creating a directional flow of coolant from left to right across the surface to be cooled, the directional flow traveling toward an outlet port of the heat sink module.
FIG. 33 shows a bottom view of a heat sink module having a first plurality of orifices and a second plurality of orifices, the second plurality of orifices being configured to deliver a plurality of anti-pooling jet streams into the outlet chamber.
FIG. 34 shows a side cross-sectional view of the heat sink module of FIG. 33 taken along section B-B, the side view showing an inlet port, inlet passage, inlet chamber, plurality of orifices, outlet chamber, and anti-pooling orifice within the heat sink module.
FIG. 35 shows a detailed view of a portion of the heat sink module of FIG. 34 highlighting the anti-pooling orifice that extends from the inlet chamber to a rear wall of the outlet chamber.
FIG. 36 shows a side cross-sectional view of the heat sink module of FIG. 33 taken along section B-B, with the heat sink module mounted on a thermally conductive base member and showing central axes of the plurality of orifices and the anti-pooling orifice.
FIG. 37 shows a side cross-sectional view of the heat sink module of FIG. 33 taken along section A-A and showing an outlet port, outlet passage, inlet chamber, outlet chamber, plurality of orifices, and anti-pooling orifice.
FIG. 38 shows a side cross-sectional view of the heat sink module of FIG. 33 taken along section A-A, with the heat sink module mounted on a thermally conductive base member and showing central axes of the plurality of orifices and the anti-pooling orifice.
FIG. 39 shows a top view of a heat sink module having a plurality of anti-pooling orifices.
FIG. 40 shows a side cross-sectional view of the heat sink module of FIG. 39 taken along section B-B and showing the location of section C-C passing through the inlet chamber and the location of section D-D passing through the outlet chamber.
FIG. 41 shows a front view of the heat sink module of FIG. 39.
FIG. 42 shows a left side view of the heat sink module of FIG. 39 showing the outlet and inlet ports having an angle of a with respect to a mounting surface of the heat sink module.
FIG. 43 shows a top view of the heat sink module of FIG. 39 taken along section C-C shown in FIG. 42, the top view showing the inlet port, inlet passage, inlet chamber, top surface of the dividing member, plurality of orifices, and plurality of anti-pooling orifices.
FIG. 44 shows a bottom view of the heat sink module of FIG. 39 taken along section D-D shown in FIG. 42, the bottom view showing the outlet port, outlet passage, outlet chamber, bottom surface of the dividing member, plurality of orifices, and plurality of anti-pooling orifices.
FIG. 45 shows a bottom view of a heat sink module having a plurality of boiling-inducing members within an outlet chamber.
FIG. 46 shows a side cross-sectional view of the heat sink module of FIG. 45 taken along section B-B, the side view showing an inlet port, inlet passage, inlet chamber, plurality of orifices, dividing member, and plurality of boiling-inducing members.
FIG. 47 shows a side cross-sectional view of the heat sink module of FIG. 45 taken along section B-B with the heat sink module mounted on a thermally conductive base member and showing central axes of the plurality of orifices.
FIG. 48 shows a detailed view of a portion of the heat sink module shown in FIG. 46, the detailed view showing three boiling inducing members extending from a bottom surface of the dividing member into the outlet chamber and an orifice extending from the inlet chamber to the outlet chamber.
FIG. 49 shows a side cross-sectional view of the heat sink module of FIG. 45 taken along section A-A, the side view showing an outlet port, outlet passage, outlet chamber, inlet chamber, plurality of orifices, plurality of boiling-inducing member, and dividing member.
FIG. 50 shows a side cross-sectional view of the heat sink module of FIG. 45 taken along section A-A, the heat sink module being mounted on a thermally conductive base member and showing central axes of the plurality of orifices.
FIG. 51A shows a top perspective view of a redundant heat sink module having a first independent flow path and a second independent flow path.
FIG. 51B shows a top view of the redundant heat sink module of FIG. 51A, where the first independent flow path and the second independent flow path are represented by dashed lines, where the first independent flow path passes through a first region near a middle of the module, and where the second independent flow path passes through a second region beyond the perimeter of the first region.
FIG. 51C shows a top view of the redundant heat sink module of FIG. 51A with connectors installed on the inlet and outlet ports.
FIG. 51D shows a bottom view of the redundant heat sink module of FIG. 51A, where the first independent flow path includes an array of orifices arranged in a first region located near a middle of the module, and where the second independent flow path includes an array of orifices arranged in a second region beyond the perimeter of the first region.
FIG. 51E shows a top view of the heat sink module of FIG. 51A.
FIG. 51F shows a side cross-sectional view of the redundant heat sink module of FIG. 51A taken along section A-A shown in FIG. 51E.
FIG. 51G shows a side cross-section view of the redundant heat sink module of FIG. 51A taken along section B-B shown in FIG. 51E.
FIG. 51H shows a side view of the redundant heat sink module of FIG. 51A.
FIG. 51I shows a cross-sectional view of the redundant heat sink module of FIG. 51A taken along section C-C shown in FIG. 51H.
FIG. 51J shows a top view of the redundant heat sink module of FIG. 51A.
FIG. 51K shows a side cross-sectional view of the redundant heat sink module of FIG. 51A taken along section D-D shown in FIG. 51J.
FIG. 51L shows a top view of the redundant heat sink module of FIG. 51A.
FIG. 51M shows a side cross-section view of the redundant heat sink module of FIG. 51A taken along section E-E of FIG. 51L.
FIG. 52A shows two redundant heat sink modules mounted on a thermally conductive base member, where two sink modules are provided for redundancy and/or increased heat transfer capability.
FIG. 52B shows two heat sink modules mounted on a thermally conductive base member, where two sink modules are provided for redundancy and/or increased heat transfer capability.
FIG. 53 shows a top perspective view of a redundant heat sink module having side-by-side independent flow paths, a first independent flow path having an inlet port and an outlet port, and a second independent flow path having an inlet port and an outlet port.
FIG. 54 shows a bottom perspective view of a redundant heat sink mounted to a planar, thermally conductive base member with a plurality of fasteners.
FIG. 55 shows a top perspective view of a thermally conductive base member having a top surface and an array of boiling-inducing members extending from the top surface.
FIG. 56 shows a top perspective view of a motherboard for a server including microprocessors and a plurality of vertically arranged memory modules that are parallel and offset, where a heat sink module can be mounted on top of each microprocessor.
FIG. 57 shows a top perspective view of a server including a plurality of vertically arranged memory modules that are parallel and offset.
FIG. 58 shows two-phase flow regimes, including (a) bubbly flow with a first number density of bubbles, (b) bubbly flow with a second number density of bubbles that is greater than the first number density, (c) slug flow, (d) churn flow, and (e) annular flow.
FIG. 59A shows a flow regime map for a steam-water system and shows ρliquid*jliquid2 on the x-axis and ρvapor*jvapor2 on the y-axis.
FIG. 59B shows two-phase flow regimes, including bubbly flow, plotted on void fraction versus mass flux axes.
FIG. 60 shows a flow boiling curve where heat transfer rate is plotted as a function of excess temperature.
FIG. 61 shows a boiling curve for water at 1 atm showing an onset of nucleate boiling, an inflection point, the point of critical heat flux, and the Leidenfrost point.
FIG. 62 shows possible orifice configurations for a heat sink module, including (a) a regular rectangular jet array, (b) a regular hexagonal jet array, and (c) a circular jet array.
FIG. 63 shows a top view of a heated surface covered by coolant, the coolant having regions of vapor coolant and wetted regions of liquid coolant in contact with the heated surface, where a contact line length is measured as a sum of all curves where liquid coolant, vapor coolant, and the heated surface are in mutual contact on the heated surface.
FIG. 64 shows a plot of CPU power consumption versus junction temperature for processor switching speeds of 1.6 GHz and 2.4 GHz.
FIG. 65 shows a heat sink module with an insertable orifice plate installed within a module body.
FIG. 66 shows a side cross-sectional view of a server having a first microprocessor, a second microprocessor, a first finned heat sink arranged on top of the first microprocessor, a second finned heat sink arranged on top of the second microprocessor, and a cooling system, where the cooling system includes a heat sink module attached to a thermally conductive member that extends from the first finned heat sink to the second heat sink module.
FIG. 67 shows a side cross-sectional view of a server having a first microprocessor, a second microprocessor, and a cooling system, where the cooling system includes a heat sink module attached to a thermally conductive member that extends from the first microprocessor to the second microprocessor.
FIG. 68 shows a schematic of a cooling apparatus having a primary cooling loop, a bypass, and an independent heat rejection loop.
FIG. 69 shows a schematic of a cooling apparatus having a first cooling loop, a second cooling loop, and an independent heat rejection loop.
FIG. 70 shows a schematic of a cooling apparatus having a redundant heat sink module mounted on a heat source, the cooling apparatus having a first cooling loop and a second cooling loop, both fluidly connected to a common reservoir.
FIG. 71 shows a schematic of a cooling apparatus having a primary cooling loop with a pump, heat exchanger, heat sink module, reservoir, and bypass, the bypass having a pressure regulator.
FIG. 72 shows a schematic of a cooling apparatus having a primary cooling loop with redundant pumps and check valves, reservoir, heat exchanger, heat sink module, and bypass, the bypass having a pressure regulator used to control the pressure differential between the inlet and outlet ports of the heat sink module.
FIG. 73 shows a cross-sectional view of a first heat sink module fluidly connected to a second heat sink module by a section of flexible tubing, where single-phase flow becomes two-phase bubbly flow within an outlet chamber of the first heat sink module due to heat transferred from a first surface to be cooled to the flow, where flexible tubing transports the two-phase bubbly flow from an outlet port of the first heat sink module to an inlet port of a second heat sink module, where the two-phase bubbly flow is delivered to an inlet chamber of the second heat sink module and passes as a plurality of jet streams through a plurality of orifices within the second heat sink module and impinge against a second surface to be cooled.
FIG. 74 shows a portable cooling device that includes a plurality of heat sink modules mounted on a portable layer, the portable layer being rigid or conformable to a contoured heated surface and including one or more inlet connections and one or more outlet connections that can be connected to a cooling apparatus that delivers a flow of pressurized coolant to the portable cooling device to permit cooling of the heated surface through sensible and latent heating of the coolant within the plurality of heat sink modules.



DETAILED DESCRIPTION
The cooling apparatuses 1 and methods described herein are suitable for a wide variety of applications, ranging from cooling electrical devices to cooling mechanical devices to cooling chemical reactions and/or processes. Examples of electrical devices that can be effectively cooled with the cooling apparatuses 1 and methods include densely packed servers in data centers, medical imaging devices, solar panels, high-power diode laser arrays, and electric vehicle components (e.g battery packs, electric motors, and power electronics). Examples of mechanical devices that can be effectively cooled with the cooling apparatuses 1 and methods include turbines, internal combustion engines, turbochargers, after-treatment components, and braking systems. Examples of chemical processes that can be effectively cooled with the cooling apparatuses 1 include condensation processes involving rotary evaporators or reflux distillation condensers.
Compared to competing air or liquid cooling systems, the cooling apparatuses 1 and methods described herein consume less energy, have higher reliability, operate more safely, are less expensive, and have lower operating noise. The cooling apparatuses 1 described herein are suitable for retrofit on existing systems or can be incorporated into new systems. Due to its high efficiency, modularity, flexible connections, small size, and hot-swappability, the cooling apparatus 1 described herein redefines design constraints that have until now hampered the progress of new servers and other electronic devices. The cooling apparatus 1 described herein will allow the size of electronic device housings to be significantly reduced while simultaneously reducing the risk of overheating of critical components and maintaining or even improving device performance. Using the methods and components described herein, a high-efficiency cooling apparatus 1 for a wide variety of applications can be rapidly optimized, manufactured, and installed. In some examples, additive manufacturing processes can be used to rapidly manufacture heat sink modules 100 that permit consistent cooling of multiple device surfaces 12, even where a heat distributions on those surfaces are non-uniform, such as on multi-core microprocessors.
Due to their small size and flexible connections, the components described herein can be discretely packaged in many existing machines and devices that require efficient and reliable cooling of surfaces that produce high heat fluxes. For example, the cooling apparatuses 1 described herein can be discretely packaged in personal computers or servers to cool microprocessors and memory modules, in vehicles to cool battery packs, electric motors, and power electronics, and in medical imaging devices to cool power supplies and other electronic components.
In data center applications, the cooling apparatuses 1 and methods described herein can provide local, efficient cooling of critical system components and, where the data center 425 is located in an office building, can allow the ambient temperature of the office building to remain at a temperature that is comfortable for human occupants, while still permitting effective cooling of critical system components. Presently, competing air-cooled system use room air within the office building to cool critical system components by employing small fans to blow the air across finned surfaces of the system components. As the system components (e.g. microprocessors) are more highly utilized, they begin to generate more heat. To provide additional cooling, there are two options in competing air-cooled systems. First, the mass flow rate of room air across the components can be increased to increase the heat transfer rate, or second, the temperature of the room air can be reduced to provide a larger temperature differential between the room air and the component temperature, thereby increasing the heat transfer rate. Initially, fans speeds can be increased to provide higher flow rates of room air, which in turn provides higher heat transfer rates. However, at some point, maximum fan speeds will be attained, at which point the flow rate of room air can no longer be increased. At this point, if critical system components demand additional cooling (e.g. to prevent overheating or failure), the only option in competing air-cooled systems is to decrease the temperature of the room air by delivering larger volumetric flow rates of cool air from an air conditioning unit to the room to reduce the room temperature. This approach is highly inefficient and ultimately results in discomfort for human occupants of the office building, since larger volumetric flow rates of cool air eventually cause the air temperature within the building to reach an uncomfortably cool temperature, which can diminish worker productivity.
Two-Phase Flow Capability
In some aspects, the cooling apparatuses 1 described herein can be configured to cool a heat-generating surface 12 by flowing coolant 50 over the surface 12, directing jet streams 16 of coolant against the surface 12, or a combination thereof (as shown in FIGS. 26 and 30). The terms “heat-generating surface,” “surface to be cooled,” “surface of the device,” “heat source,” “heated surface,” “heat providing surface,” “device surface,” “component surface,” and “heat-producing surface” are used herein to describe any surface 12 of a component or device that is at a temperature above ambient temperature, whether due to heat produced by or within the component or device or whether due to heat transferred to the component or device from some other component or device that is in thermal communication with the surface 12. Within some components of the cooling apparatus 1, at least a portion of the coolant 50 can undergo a phase change from a liquid to a vapor in response to absorbing heat from the surface 12 of the device. The phase change can result in the coolant 50 transitioning from a single-phase liquid flow to two-phase bubbly flow or from a two-phase bubbly flow having a first number density of vapor bubbles to two-phase bubbly flow having a second number density of vapor bubbles, where the second number density is higher than the first number density. By initiating boiling proximate the surface 12 being cooled, and taking advantage of the highly-effective heat transfer mechanisms associated therewith, the cooling apparatuses 1 and methods described herein can deliver heat transfer rates that far exceed heat transfer rates attainable with traditional liquid cooling or air cooling systems. By providing dramatically increased heat transfer rates, the cooling apparatus 1 described herein is able to cool devices far more efficiently than any other existing cooling apparatus, which translates to significantly lower power consumption by the cooling apparatus 1 described herein. Where the cooling apparatus 1 is used in a large scale cooling application, such as a data center, and replaces a conventional air conditioning system, the cooling apparatus can result in significant savings on utility bills for a data center operator.
When a heat-generating surface 12 exceeds the saturation temperature of the coolant 50, boiling of the coolant proximate (i.e. at or near) the heat-generating surface occurs. This can occur whether the bulk fluid temperature of the coolant 50 is at or below its saturation temperature. If the bulk fluid temperature is below the saturation temperature of the coolant 50, boiling is referred to as “local boiling” or “subcooled boiling.” If the bulk fluid temperature of the coolant is equal to the saturation temperature, then “bulk boiling” is said to occur. Bubbles formed proximate the heat-generating surface 12 depart the surface 12 and are transported by the bulk fluid, creating a flow of liquid fluid with bubbles distributed therein, known as two-phase bubbly flow. Depending on the degree of subcooling, as the bubbly flow passes through tubing, some or all of the bubbles in the bubbly flow may condense and collapse as mixing of the fluid and bubbles occurs. As bubbles collapse back to liquid, the bulk fluid temperature rises. In saturated or bulk boiling, where the bulk fluid temperature is near the saturation temperature, the bubbles 275 distributed in the fluid may not collapse as the bubbly flow passes through tubing and as mixing of the fluid and bubbles occurs.
Two-phase flow can be described based on a volume fraction of vapor present in the flow, where the volume fraction of vapor in the flow (αvapor) plus the volume fraction of liquid (αliquid) in the flow is equal to one (αvapor+αliquid=1). The volume fraction of vapor (αvapor) is commonly referred to as “void fraction” even though the vapor volume is filled with low density gas and no true voids exist in the flow. The volume fraction within a tube, such as a section of flexible tubing 225 between two series-connected heat sink modules 100, can be calculated using the following equation:

αvapor=Avapor/Ax 

where Ax is the total cross-sectional flow area at point x in the tube, and Avapor is the cross-sectional area occupied by vapor at point x in the tube. The volumetric flux of vapor (jvapor) in a flow 51, also known as the “superficial velocity” of the vapor, can be calculated using the following equation:

jvapor=(vvapor*Avapor)/Ax=αvapor*vvapor 

where vvapor is the velocity of vapor in the tube. In some instances, the velocity of vapor (vvapor) and the velocity of the liquid (vliquid) in the flow may not be equal. This inequality in velocities can be described as a slip ratio and calculated using the following equation:

S=vvapor/vliquid 

Where the vapor velocity (vvapor) and the liquid velocity (vliquid) in the flow are equal, the slip ratio (S) is one. The flow quality is the flow fraction of vapor and is always between zero and one. Flow quality (x) is defined as:

x=mvapor/mvapor/(mvapor+mliquid)

where mvapor is the mass flow rate of vapor in the tube, mliquid is the mass flow rate of liquid in the tube, and m is the total mass flow rate in the tube (m=mvapor+mliquid). The mass flow rate of liquid is defined as:

mliquid=ρliquid*vliquid*Aliquid 

where ρliquid is the density of the liquid, and Aliquid is the cross-sectional area occupied by liquid at point x in the tube. Similarly, the mass flow rate of vapor is defined as:

mvapor=ρvapor*vvapor*Avapor 

where ρvapor is the density of the vapor. The distribution of vapor in a two-phase flow of coolant 50, such as a two-phase flow of coolant within a heat sink module 100 mounted on a heat-generating surface 12, affects both the heat transfer properties and the flow properties of the coolant 50. These properties are discussed in greater detail below.

A number of flow patterns or “flow regimes” have been observed experimentally by viewing flows of two-phase liquid-vapor mixtures passing through transparent tubes. While the number and characteristics of specific flow regimes are somewhat subjective, four principal flow regimes are almost universally accepted. These flow regimes are shown in FIG. 58 and include (1) bubbly flow (FIG. 58(a) shows bubbly flow having a first number density of bubbles, and FIG. 58(b) shows bubbly flow having a second number density of bubbles where the second number density is greater than the first number density), (2) slug flow (FIG. 58(c)), (3) churn or churn-turbulent flow (FIG. 58(d)), and (4) annular flow (FIG. 58(e)). Beyond annular flow, the flow will transition through wispy-annular flow before eventually reaching single-phase vapor flow.
Bubbly flow is generally characterized as individually dispersed bubbles 275 transported in a continuous liquid phase. Slug flow is generally characterized as large bullet-shaped bubbles separated by liquid plugs. Churn flow is generally characterized as vapor flowing in a chaotic manner through liquid, where the vapor is generally concentrated near the center of the tube, and the liquid is displaced toward the wall of the tube. Annular flow is generally characterized as vapor forming a continuous core down the center of the tube and a liquid film flowing along the wall of the tube.
To predict an existence of a particular flow regime, or a transition from one flow regime to another, requires the above-mentioned visually observed flow regimes to be quantified in terms of measurable (or computed) quantities. This is normally accomplished through the use of a flow regime map. An example of a flow regime map is provided in FIG. 59A. The flow regime map shown in FIG. 59A is valid for steam-water systems and shows ρvapor*jvapor2 on the x-axis and ρvapor*jvapor2 on the y-axis. A similar flow regime map can created for a dielectric coolant 50, such as a hydrofluorocarbon coolant, flowing over a heat-generating surface 12 within a heat sink module 100 or flowing within a flexible section of tubing 225, as described herein.
FIG. 59B shows the four two-phase flow regimes, including bubbly flow, slug flow, churn flow, and annular flow, plotted on void fraction versus mass flux axes. To maintain stability within the cooling apparatus during operation, it can be desirable to maintain either single-phase liquid flow, bubbly flow, or a combination thereof throughout the apparatus. Experimental testing confirmed that bubbly flow does not result in flow instabilities within the cooling apparatus 1. Conversely, the presence of slug, churn, or annular flow can result in flow instabilities and should therefore be avoided. To remain comfortably within the bubbly flow regime, it can be desirable to maintain the coolant below a predetermined void fraction and/or above a predetermined mass flux. The desired predetermined void fraction and predetermined mass flux can depend on several factors, including the configuration of the cooling apparatus 1 (e.g. components and layout), the type of coolant 50 being used, the coolant pressure within the apparatus, and the temperature of the surface to be cooled 12. In some examples, the void fraction of the coolant can be about 0-0.5, 0-0.4, 0-0.3, 0-0.2, or 0-0.1. In some examples, the mass flux of the coolant flowing through a heat sink module 100 can be about 10-2,000, 500-1,000, 750-1,500, 1,000-2,500, 2,250-2,500, 2,000-2,700, or greater than 2,700 kg/m2-s. As shown in FIG. 59B, as the void fraction increases (e.g. from about 0.3-0.5), the mass flux of the coolant must also increase to avoid transitioning from bubbly flow to slug or churn flow.
FIG. 60 shows a flow boiling curve where heat transfer rate is plotted as a function of “excess temperature” (Te). Excess temperature is the difference between the actual temperature of the surface to be cooled 12 and the fluid saturation temperature (Te=Tsurface−Tsat). The curve is divided into 5 regions (a, b, c, d, and e), each corresponding to certain heat transfer mechanisms.
In region (a) of FIG. 60, a minimum criterion for boiling is that the temperature of the heat-generating surface 12 exceeds the local saturation temperature of the coolant (Tsat). In other words, some degree of excess temperature (Te) is required for boiling to occur. In region (a), the excess temperature may be insufficient to support bubble formation and growth. Therefore, heat transfer may occur primarily by single-phase convection in region (a).
In region (b) of FIG. 60, bubbles begin forming at nucleation sites on the heat-generating surface 12. These nucleation sites are generally associated with crevices or pits on the heat-generating surface 12 in which non-dissolved gas or vapor accumulates and results in bubble formation. As the bubbles grow and depart from the surface 12, they carry latent heat away from the surface and produce turbulence and mixing that increases the heat transfer rate. Boiling under these conditions is referred to as nucleate boiling. In region (b), heat transfer is a complicated mixture of single-phase forced convection and nucleate boiling. This region is often called the mixed boiling or “partial nucleate boiling region.” As the temperature of the heat-generating surface 12 increases, the percentage of surface area that is subject to nucleate boiling also increases until bubble formation occupies the entire heat-generating surface 12.
In region (c) of FIG. 60, bubble density increases rapidly as the surface temperature increases further beyond the saturation temperature (Tsat). In this region, heat transfer can be dominated by bubble growth and departure from the surface 12. Formation and departure of these bubbles 275 can transport large amounts of latent heat away from the surface 12 and greatly increase fluid turbulence and mixing in the vicinity of the heat-generating surface 12. As a result, heat transfer can become independent of bulk fluid conditions such as flow velocity and temperature. Heat transfer in this region is know as “fully developed nucleate boiling” and is characterized by a substantial increase in heat transfer rate in response to only moderate increases in surface 12 temperature. However, there is a limit to the maximum rate of heat transfer that is attainable with fully developed nucleate boiling. At some point, the bubble density at the heat generating surface 12 cannot be increased any further. This point is know as the critical heat flux (“CHF”) and is denoted as c* in FIG. 60. One theory is that at point c*, the bubble density becomes so high that the bubbles actually impede the flow of liquid back to the surface 12, since bubbles in close proximity tend to coalesce, forming insulating vapor patches that effectively block the liquid coolant from reaching the heat-generating surface 12 and thereby prevent the liquid coolant from extracting latent heat, for example, by undergoing a phase change (i.e. boiling) at the surface 12.
It may be possible to delay the onset of critical heat flux by employing the cooling apparatuses 1 and methods described herein (e.g. heat sink modules capable of providing jet stream 16 impingement) that increase the heat transfer rate from the heated surface 12, thereby allowing the cooling apparatus 1 to safely and effectively cool a heat generating surface 12 that is at a temperature well above the saturation temperature of the coolant (e.g. about 20-30 deg C. above Tsat) without reaching or exceeding critical heat flux. In some examples, delaying the onset of critical heat flux, and thereby increasing the heat transfer rate of the cooling apparatus 1 to previously unattainable rates, can be achieved by increasing the three-phase contact line 58 length, as described herein (see e.g. FIG. 63 and related description), by using the methods and components (e.g. heat sink modules 100) described herein, which can provide a plurality of jet stream 16 impinging against a heated surface 12 where the jets are positioned at a predetermined jet height 18 away from the heated surface 12. To delay the onset of critical heat flux (and thereby allow the cooling apparatus 1 to operate safely and effectively in region (c) shown in FIG. 60), a mass flow rate 51, jet height 18, orifice 155 diameter, coolant temperature, and coolant pressure can be selected from the ranges described herein to provide a plurality of jet streams 16 that impinge the surface to be cooled 12 and effectively increase the three-phase contact line 58 length proximate the surface to be cooled 12. Although the cooling apparatus 1 can operate extremely well in regions (a) and (b), the efficiency of the cooling apparatus 1 may be highest when operating in region (c).
As the temperature of the surface 12 increases beyond the temperature associated with critical heat flux, the heat transfer rate actually begins to decrease, as shown in region (d) of FIG. 60. Further increases in the surface 12 temperature simply result in a higher percentage of the surface 12 being covered by insulating vapor patches. These insulating vapor patches reduce the area available for liquid to vapor phase change (i.e. boiling). Therefore, despite the surface temperature (Tsurface) continuing to increase, the overall heat transfer rate actually decreases, as shown in region (d) of FIG. 60. This region is referred to as the partial film or “transition film boiling region.” Reaching or exceeding the temperature associated with critical heat flux can be undesirable, since performance can decrease and become unpredictable. Moreover, due to rapid production of vapor proximate the surface to be cooled 12, the two-phase flow in the cooling apparatus 1 can increase in quality and transition from bubbly flow to slug, churn, or annular flow, which can result in undesirable pressure surges within the system due to a volume fraction of vapor exceeding a stable working range. It is therefore desirable to operate in regions (a), (b), or (c), below the onset of critical heat flux at point c*.
In region (e) of FIG. 84, a vapor layer covers the heat-generating surface 12. In this region, heat transfer occurs by conduction and convection through the vapor layer with evaporation occurring at the interface between the vapor layer and the liquid coolant. This region is known as the “stable film boiling region.” Similar to region (d), region (e) is not suitable for stable operation of the cooling apparatus 1 due to significant vapor formation resulting in slug, churn, or annular flow.
FIG. 61 shows a flow boiling curve for water at 1 atm, where heat flux is plotted as a function of excess temperature. As noted above, excess temperature is the difference between the actual temperature of the surface to be cooled 12 and the fluid saturation temperature (Te=Tsurface Tsat). The curve of FIG. 61 shows the onset of nucleate boiling, the point of critical heat flux, and the Leidenfrost point. Between the critical heat flux point and the Leidenfrost point is a transition boiling region where the coolant vaporizes almost immediately on contact with the heated surface 12. The resulting vapor suspends the liquid coolant on a layer of vapor within the outlet chamber 150 and prevents any further direct contact between the liquid coolant and the heated surface 12. Since vapor coolant has a much lower thermal conductivity than liquid coolant, further heat transfer between the heated surface 12 and the liquid coolant is slowed down dramatically, as shown by the downward slope of the plot between CHF and the Leidenfrost point. Beyond the Leidenfrost point, radiation effects become significant, as radiation from the heated surface 12 transfers heat through the vapor layer to the liquid coolant suspended above the vapor layer, and the heat flux again increases.
Experimental Data
FIG. 8 shows a plot of experimental data showing power consumed versus time to cool a computer room 425 having forty active dual-processor servers 400. The left portion of the plot, extending from about 15 to 390 minutes, shows power consumed by a CRAC tasked with cooling the computer room 425. From about 15 to 190 minutes, the servers 400 were fully utilized, and from about 240 to 360 minutes, the servers were at idle state. At about 390 minutes, the cooling apparatus 1 was activated to assist the CRAC with cooling the servers 400. However, the heat sink modules 100 connected to the cooling apparatus 1 were only installed on microprocessors in 25% of the servers (ten of forty servers). Nevertheless, a dramatic reduction in power consumption was recorded. From 390 to 590 minutes, the cooling apparatus 1 conserved about 1.5 kW of power compared to the baseline idle state cooled by the CRAC only, and from about 625 to 840 minutes, the cooling apparatus 1 conserved about 2 kW of power compared to the baseline fully utilized state cooled by the CRAC only. The reduction in power consumption measured in this experiment is expected to scale as more servers in the computer room are connected to the cooling apparatus 1. Consequently, if heat sink modules of the cooling apparatus 1 were installed on microprocessors of all forty servers, reductions in power consumption of about 6 kW (i.e. 55%) and 8 kW (i.e. 67%) compared to the baseline idle and baseline fully utilized states, respectively, are expected. Reductions in power consumption of this magnitude can translate to significant savings in annual operating expenses for computer room and data center operators.
Experimental tests have demonstrated that significantly higher heat transfer rates are achievable with the cooling apparatus 1 than with existing single-phase pumped liquid systems. This higher heat transfer rate can be attributed, at least in part, to establishing conditions in an outlet chamber 150 of the heat sink module 100 that promote boiling of the coolant proximate the surface to be cooled 12. During testing, a heat sink module 100 was provided that contained a plurality of orifices 155 configured to provide impinging jets streams 16 of coolant 50 directed against a surface to be cooled 12, as shown in FIG. 26. In a first test, the pressure in the outlet chamber 150 of the heat sink module 100 was set to establish a saturation temperature of about 95° C. for the coolant. In a second test, the pressure in the outlet chamber 150 of the heat sink module 100 was set to establish a saturation temperature of about 74° C. for the coolant. The saturation temperature of about 74° C. was chosen to substantially match the mean temperature of the heated surface (i.e. surface to be cooled 12) in the test. The same flow rate of coolant was used for each test. During the second test, bubbles 275 were generated in the outlet chamber 150 with the coolant having the lower saturation temperature. Such a phase change did not occur in the outlet chamber 150 with coolant having the higher saturation temperature in the first test. Overall, the heat transfer performance increased by 80% with the lower saturation temperature (i.e. the second test) where bubbles were generated compared to the higher saturation temperature (i.e. the first test) where bubbles were not generated.
One benefit of the cooling technology described herein is the ability to efficiently cool local hot spots on a heat-generating device 12 (e.g. hot spots on microprocessors 415). For example, if just one core of a given microprocessor 415 is more heavily utilized than other cores in the same processor, and a plurality of jet streams of coolant are directed at the surface of the microprocessor, more evaporation will occur proximate the hot core, thereby increasing the local heat transfer rate proximate the hot core relative to the cooler cores, and thereby self-regulating to maintain the entire surface 12 of the microprocessor at a more uniform temperature than is possible with purely single-phase cooling systems that are incapable of self-regulating. Because the cooling apparatus 1 is capable of self-regulating to cool local hot spots (e.g. by providing local increases in heat transfer rates through evaporation), the entire cooling system can be operated at lower flow rate and pressure, which conserves energy, and still handle fluctuations in processor temperature caused by variations in utilization. This is in sharp contrast to existing liquid cooling systems that are not capable of self-regulating to cool local hot spots and must therefore be operated at much higher flow rates and pressures to ensure adequate cooling of hot spots, for example, on microprocessors. In other words, existing liquid cooling systems must operate continuously at a setting that is designed to handle a peak heat load to ensure the system is capable of handling the peak heat load if it occurs. As a result, when the microprocessor is not being heavily utilized (which is quite often) existing systems operate at a pressure and flow rate that are considerably above where they would otherwise need to operate to handle a non-peak heat load. This approach needlessly consumes a significant amount of excess energy, and is therefore undesirable.
Coolant
As used herein, the general term “coolant” refers to any fluid capable of undergoing a phase change from liquid to vapor or vice versa at or near the operating temperatures and pressures of the cooling apparatuses 1. The term “coolant” can refer to fluid in liquid phase, vapor phase, or mixtures thereof (e.g. two-phase bubbly flow). A variety of coolants 50 can be selected for use in the cooling apparatus 1 based on cost, level of optimization desired, desired operating pressure, boiling point, and existing safety regulations that govern installation (e.g. such as regulations set forth in ASHRAE Standard 15 relating to permissible quantities of coolant per volume of occupied building space).
Selection of the coolant 50 for the cooling apparatus 1 can be influenced by desired dielectric properties of the coolant, a desired boiling point of the coolant, and compatibility with polymer materials used to manufacture the heat sink module 100 and the flexible tubing 225 of the apparatus 1. For instance, the coolant 50 may be selected to ensure little or no permeability through system components (e.g. heat sink modules and flexible tubing) and no damage to any system components (e.g. to ensure that seals are not damaged or compromised by the coolant).
Water is readily abundant and inexpensive. Although the cooling apparatuses 1 described herein can be configured to operate with water as the coolant 50, water has certain traits that make it less desirable than other coolant options. For instance, water does not change phase at a low temperature (such as 40-50° C.) without operating at very low pressures, which can be difficult to maintain in a relatively inexpensive cooling apparatus that includes at least some standard fittings and system components (e.g. gear pumps, pressure regulators, valves, and flexible tubing). In addition, water as a coolant requires a number of additives (e.g. corrosion inhibitors and mold inhibitors) and can absorb a range of materials from surfaces of system components it contacts. As water changes phase, these materials can precipitate out of solution, causing fouling or other issues within system components. Fouling is undesirable, since it can reduce system performance by effectively increasing the thermal resistance of certain components that are tasked with expelling heat from the system (e.g. heat exchanger 40) or tasked with absorbing heat into the system from devices being cooled by the system (e.g. copper base plate 430). The above-mentioned challenges can be overcome with appropriate filtration and fittings, which adds cost to the system. However, water is a highly effective heat transfer medium, so where increased heat transfer rates are required, the additional cost and complexity associated with using water as the coolant may be justified.
In some examples, it can be preferable to use a dielectric fluid, such as a hydrofluorocarbon coolant 50 instead of water. Unlike water, dielectric coolants 50 can be used in direct contact with electrical devices, such as CPUs, memory modules, and power converters without shorting electrical connections of the devices. Therefore, if a leak develops in the cooling apparatus and coolant drips onto an electrical device, there is no risk of damage to the electrical device. In some examples of the cooling apparatus 1, the dielectric coolant 50 can be delivered directly (e.g. by way of one or more jet streams 16) onto one or more surfaces of the electronic device (e.g. one or more surfaces of a microprocessor 415), thereby eliminating the need for commonly-used thermal interface materials (e.g. copper base plates 430 and thermal bonding materials) between the flowing coolant 50 and the electronic device and can thereby eliminate thermal resistances associated with those thermal interface materials, thereby enhancing performance and overall efficiency of the cooling apparatus 1.
Non-limiting examples of dielectric hydrofluorcarbon coolants 50 include 1,1,1,3,3-pentafluoropropane (known as R-245fa), hydrofluoroether (HFE), 1-methoxyheptafluoropropane (known as HFE-7000), and methoxy-nonafluorobutane (known as HFE-7100). One version of R-245fa is commercially available as GENETRON 245fa from Honeywell International Inc. headquartered in Morristown, N.J. HFE-7000 and HFE-7100 (as well as HFE-7200, HFE-7300, HFE-7500, HFE-7500, and HFE-7600) are commercially available as NOVEC Engineered Fluids from 3M Company headquartered in Mapleton, Minn. FC-40, FC-43, FC-72, FC-84, FC-770, FC-3283, and FC-3284 are commercially available as FLUOROINERT Electronic Liquids also from 3M Company.
GENETRON 245fa has a molecular weight of 134.0, a boiling point of 59.3 degrees F. at 1 atm, a critical temperature of 309.2 degrees F., a critical pressure of 529.5 psia, a saturated liquid density of 82.7 lb/ft3 at 86 degrees F., a specific heat of liquid of 0.32 Btu/lb-deg F at 86 degrees F., and a specific heat of vapor of 0.22 btu/lb-deg F at 1 atm and 86 degrees F.
NOVEC 7000 has a boiling point of 34 degrees C., a molecular weight of 200 g/mol, a critical temperature of 165 degrees C., a critical pressure of 2.48 MPa, a vapor pressure of 65 kPa, a heat of vaporization of 142 kJ/kg, a liquid density of 1400 kg/m3, a specific heat of 1300 J/kg-K, a thermal conductivity of 0.075 W/m-K, and a dielectric strength of about 40 kV for a 0.1 inch gap.
NOVEC 7100 has a boiling point of 61 degrees C., a molecular weight of 250 g/mol, a critical temperature of 195 degrees C., a critical pressure of 2.23 MPa, a vapor pressure of 27 kPa, a heat of vaporization of 112 kJ/kg, a liquid density of 1510 kg/m3, a specific heat of 1183 J/kg-K, a thermal conductivity of 0.069 W/m-K, and a dielectric strength of about 40 kV for a 0.1 inch gap.
In some examples, the coolant can be a combination of dielectric fluids described above. For instance, the coolant can include a combination of R-245fa and HFE-7000 or a combination of R-245fa and HFE-7100. In one example, the coolant 50 can include about 1-5, 1-10, 5-20, 10-20, 15-30, or 25-50 percent R-245fa by volume with the remainder being HFE-7000. In another example, the coolant 50 can include about 1-5, 1-10, 5-20, 10-20, 15-30, or 25-50 percent R-245fa by volume with the remainder being HFE-7100.
Combining dielectric hydrocarbon fluids to form a coolant mixture for use in the cooling apparatus 1 can be desirable for several reasons. First, certain fluids, such a R-245fa may be regulated in ways that restrict the volume of fluid that can be used in an occupied building, such as an office building. Since R-245fa has been shown to perform well in the cooling apparatus 1, it may be desirable to use as much R-245fa as legally permitted in the cooling apparatus 1, and if additional coolant volume is required, to use an unregulated coolant, such as HFE-7000 or HFE-7100, to increase the total coolant volume within the cooling apparatus 1 to reach the desired coolant volume.
Second, combining dielectric coolants can allow a coolant mixture with a desired boiling point to be formulated. R-245fa has a boiling point of about 15.2 degrees C. at 1 atm, and HFE-7000 has a boiling point of about 34 degrees C. at 1 atm. In some examples, neither of these boiling points may be optimal for use in a particular application. By combining R-245fa and HFE-7000, a coolant mixture can be created that behaves as if its boiling point were somewhere between 15.2 and 34 degrees C., depending on the mixture ratio. The ability to create a coolant mixture with a specific boiling point can be highly desirable for custom tailoring the coolant mixture for a specific application depending on the anticipated operating temperature of the surface to be cooled 12.
Cooling Apparatus
FIG. 1 shows a front perspective view of a cooling apparatus 1 installed on a plurality of racks 410 of servers 400 in a data center or computer room 425. The racks 410 of servers 400 are arranged in a row with a pump 20, reservoir 200, and other system components arranged near the left side of the row of racks 410. One or more tubes extend along the length of the row of racks 410 and fluidly connect servers 400 within each rack 410 to the cooling apparatus 1, thereby allowing heat-generating components 12 (such as microprocessors) within each server to be cooled by the cooling apparatus 1.
In addition to cooling microprocessors in servers, the cooling apparatus can be configured to cool a wide variety of other devices. In some examples, the cooling apparatus 1 can be configured to cool one or more heat-producing surfaces 12 associated with batteries, electric motors, control systems, power electronics, chemistry equipment (e.g. rotary evaporators or reflux distillation condensers), or machines or mechanical devices (e.g. turbines, internal combustion engines, radiators, braking components, turbochargers, engine intake manifolds, plasma cutters, drills, oil and gas exploratory and recovery equipment, water jet cutters, welding systems, or computer numerical control (CNC) mills or lathes).
FIG. 2A shows a rear view of the cooling apparatus 1, and FIG. 2B shows a detailed rear view of a right portion of the cooling apparatus shown in FIG. 2A. In this example, the cooling apparatus 1 can include a plurality of components and sub-assemblies fluidly connected to provide a cooling apparatus 1 that is capable of locally cooling one or more heat-producing surfaces 12 (e.g. flat surfaces, curved surfaces, or complex surfaces), such as surfaces associated with CPUs, memory modules, and motherboards located within the server housings.
FIG. 3 shows a left side view of the cooling apparatus 1 of FIG. 1. Portions of a primary cooling loop 300 are visible in FIG. 3, including a pump 20, reservoir 200, drain/fill location 245, shut-off valve 250, pressure gauge 255, inlet manifold 210, and return line 230. Portions of a first bypass 305 are also visible in FIG. 3, including a pressure regulator 60 and heat exchanger 40. As shown in FIG. 3, the primary cooling loop 300 and the first bypass 305 can be fluidly connected to the reservoir 200.
FIGS. 11A-14, 16-20, and 68-72 present a variety of configurations for the cooling apparatus 1. Depending on its configuration, the cooling apparatus 1 can include a plurality of fluidly connected components, including one or more pumps 20, one or more reservoirs 200, one or more heat exchangers 40, one or more inlet manifolds 205, one or more outlet manifolds 210, one or more pressure regulators 60, one or more sections of flexible tubing 225, and one or more heat sink modules 100 mounted on, or placed in thermal communication with, one or more surfaces to be cooled 12.
FIG. 11A shows an exemplary schematic of a cooling apparatus 1 having one heat sink module 100 mounted on a heat-generating surface 12. The heat-generating surface 12 can be any surface having a temperature above ambient temperature that requires cooling. For instance, the heat-generating surface 12 can be a surface of a mechanical or electrical device, such as a surface of a microprocessor 415. As identified by dashed lines in FIG. 11B, the cooling apparatus 1 can include a primary cooling loop 300 fluidly connecting a pump 20, at least one heat sink module 100, a return line 230, and a reservoir 200. The pump 20 can be configured to draw single-phase liquid coolant from the reservoir 200 and deliver a flow 51 of pressurized single-phase liquid coolant 50 to an inlet port 105 of a heat sink module 100. The heat sink module 100, being mounted on the heat-generating surface 12, can be configured to direct a flow of pressurized coolant 51 at the surface of the heat-generating surface 12 in the form of a plurality of jet streams 16 of coolant impinging the heat-generating surface 12, thereby facilitating heat transfer from the heat-generating surface to the flow of coolant. The return line 230 can be configured to transport the flow of coolant 51, which may include two-phase bubbly flow, from the outlet port 110 of the heat sink module 100 back to the reservoir 200 where it can be mixed with single-phase liquid coolant to promote condensation of vapor bubbles within the two-phase bubbly flow, thereby resulting in transition of the two-phase bubbly flow back to single-phase liquid coolant that can once again be delivered to the pump 20 without risk of cavitation.
As identified by dashed lines in FIG. 11C, the cooling apparatus 1 can include a first bypass 305 including a pressure regulator 60 and a heat exchanger 40. The purpose of the first bypass 305 can be to divert a portion of the flow 51 away from the primary cooling loop 300 and through the heat exchanger 40 where the fluid can be further cooled and returned to the reservoir 200 to assist in condensing vapor in the reservoir by further reducing the bulk fluid temperature of the liquid coolant in the reservoir 200. As a result, when the two-phase bubbly flow is delivered to the reservoir via the return line, it immediately mixes in the reservoir with a large volume of coolant that is well below the saturation temperature of the liquid, thereby promoting condensation of all vapor bubbles entering the reservoir via the return line. The portion of flow 51 that is diverted through the first bypass 305 can be controlled, at least in part, by adjusting the pressure regulator 60 located in the first bypass 305. The amount of flow that is diverted through the first bypass 305 may depend on the reservoir temperature and/or the quality (x) of the flow returning to the reservoir via the return line 230. For example, if the temperature of the fluid in the reservoir 200 increase to a predetermined threshold value (e.g. about 10-15 degrees below the saturation temperature), or if the quality of the flow increases (e.g. to about 0.1-0.3), it can be desirable to increase the amount of flow through the first bypass 305 to remove heat from the liquid using the heat exchanger so that cool liquid coolant can be circulated back to the reservoir 200 to ensure that vapor bubbles 275 rapidly condense within the reservoir 200 and are not permitted to reach the pump 20.
In the schematic shown in FIG. 11A, the heat exchanger 40 is positioned downstream of the pressure regulator 60, but this is not limiting. In other examples, the pressure regulator 60 can be positioned downstream of the heat exchanger 40, as shown in FIG. 12A, where the cooling apparatus 1 has one heat sink module 100 mounted on a heat source 12 and a pressure regulator 60 located downstream of the heat exchanger 40 in the first bypass 305.
As identified by dashed lines in FIG. 11D, the cooling apparatus 1 can include a second bypass 310 including a pressure regulator 60. The second bypass 310 can route a portion of the pressurized single-phase liquid flow around the heat sink module 100 and can be fluidly connect to the primary cooling loop 300 downstream of the heat sink module 100. Depending on the surface temperature of the heat-generating surface 12 and settings of the cooling apparatus (e.g. pressure, flow rate, coolant type, bulk coolant temperature at the module inlet 105, coolant saturation temperature, etc.), the primary cooling loop 300 may be transporting two-phase bubbly flow downstream of the outlet port 110 of the heat sink module 100. To encourage condensing of bubbles 275 within the two-phase bubbly flow before the coolant reaches the reservoir (and thereby reducing the likelihood of vapor being introduced to the pump 20), the second bypass 310 can route single-phase liquid coolant around the heat sink module 100 and deliver the single-phase liquid coolant to the primary cooling loop 300 that is carrying two-phase bubbly flow, effectively mixing the two flows upstream of the reservoir 200. This mixing encourages condensing of all or a portion of the bubbles in the two-phase bubbly flow before the flow is delivered back to the reservoir 200 via the return line 230, thereby further reducing the likelihood that any bubbles 275 will be drawn from the reservoir 200 and fed to the pump, where they could cause unwanted cavitation.
Because the bubbles 275 formed in the two-phase bubbly flow are relatively small and are distributed (i.e. dispersed) throughout the liquid coolant 50, the bubbles are carried through the primary cooling loop 300 by the momentum of the liquid coolant and do not travel vertically within the system due to gravitational effects. Consequently, the cooling apparatus 1 does not require a condenser mounted at a high point in the system to collect and condense vapor bubbles back to liquid, as competing systems do. Since no condenser is required, the cooling apparatus 1 can be much smaller in size and less expensive than competing systems that require a condenser. Also, the heat sink modules 100 and sections of flexible tubing 225 described herein can be installed in any orientation without concerns of vapor lock. To the contrary, in competing systems, the orientation of system components can be critical to ensure that all vapor is transported to a condenser located at a high point in the system by way of gravity to ensure that vapor does not make its way to the pump, where it could result in vapor lock and/or pump cavitation and system failure.
As used herein, “fluid communication” between two or more elements refers to a configuration in which fluid can be communicated between or among the elements and does not preclude the possibility of having a filter, flow meter, temperature or pressure sensor, or other devices disposed between such elements. The elements comprising the cooling apparatus 1 are preferably configured in a closed fluidic system, as shown in FIG. 11A, thereby permitting containment of the coolant 50 which would otherwise be prone to evaporate into the environment.
Pressure Regulator
The pressure regulator 60 can be any suitable type of pressure regulator that is capable of achieving suitable working pressures ranges and flow rates described herein to ensure smooth operation of the cooling apparatus 1. In some examples, the pressure regulator 60 can be a relief valve, such as a Series 69 relief valve manufactured by Aquatrol, Inc. of Elburn, Ill. One suitable Series 69 relief valve has an adjustment range of about 0-15 psi and a maximum flow rate of about 6.9 gallons per minute. This model pressure regulator is suitable for a cooling apparatus 1 configured to cool several racks 410 of servers 400 as shown in FIG. 3. For applications where a larger or smaller cooling apparatus 1 is required, a larger or smaller model pressure regulator can be used.
As shown in FIG. 11A, the pressure regulator 60 can be located in the second bypass 310 of the cooling apparatus 1 and can be used to control the pressure differential between the inlet port 105 and the outlet port 110 of the heat sink module (i.e. the pressure differential between the high-pressure coolant 54 at the inlet port 105 and the low-pressure coolant 55 at the outlet port 110). Where the cooling apparatus 1 has a plurality of heat sink modules 100 fluidly connected in parallel to the inlet manifold 210 and outlet manifold 215, as shown in FIG. 16, the pressure regulator 60 can be used to control the pressure differential between the inlet manifold and the outlet manifold.
In the cooling apparatus 1 shown in FIG. 11A, by adjusting the pressure regulator 60 located in the second bypass 310, the pressure differential between the inlet port 105 and outlet port 110 can be controlled. In the cooling apparatus 1 shown in FIG. 16, the pressure regulator 60 can be adjusted to provide a pressure differential between the inlet manifold 210 and the outlet manifold 215. In one example, the pressure regulator 60 can be adjusted to provide a pressure differential of about 5-15 or 10-15 psi between the inlet manifold 210 and the outlet manifold 215. For instance, if the high-pressure coolant 54 in the inlet manifold 210 is at a pressure of about 60 psi, the pressure regulator 60 can be adjusted to maintain low-pressure coolant 55 in the outlet manifold 215 at a pressure of about 45-55 or 45-50 psi. In another example, if the high-pressure coolant 54 in the inlet manifold 210 is at a pressure of about 30 psi, the pressure regulator 60 can be adjusted to maintain low-pressure coolant 55 in the outlet manifold 215 at a pressure of about 15-25 or 15-20 psi. In yet another example (where the contents of the cooling apparatus 1 are evacuated using a vacuum pump prior to adding the coolant, such that the resting pressure of the coolant is below atmospheric pressure), if the high-pressure coolant 54 in the inlet manifold 210 is at a pressure of about 15 psi, the pressure regulator 60 can be adjusted to maintain low-pressure coolant 55 in the outlet manifold 215 at a pressure of about 0-10 or 0-5 psi.
The pressure regulator 60 located in the second bypass 310 of the cooling apparatus 1, as shown in FIG. 16, can be adjusted to control the coolant flow rate through the second bypass 310, and by doing so, can simultaneously adjust the coolant flow rate through the heat sink modules 100. For instance, as the pressure differential between the inlet manifold 210 and the outlet manifold 215 shown in FIG. 16 is decreased by adjusting the pressure regulator 60 located in the second bypass 310, a higher percentage of coolant flow 51 will pass through the pressure regulator 60, effectively bypassing the heat sink modules 100 and resulting in a reduced coolant flow rate through the heat sink modules. Conversely, as the pressure differential between the inlet manifold 210 and outlet manifold 215 is increased by adjusting the pressure regulator 60 located in the second bypass 310, a lower percentage of coolant flow 51 will pass through the pressure regulator 60, resulting in an increased coolant flow rate through the heat sink modules 100.
As shown in FIG. 16, the pressure regulator 60 can be arranged in parallel with a plurality of cooling lines. Coolant flow through the pressure regulator 60 and the cooling lines can be similar to the way current flows in a circuit with resistors arranged in parallel. Increasing the flow resistance of the regulator 60 will decrease the flow through the second bypass 310 and increase the flow rate through the cooling lines. Conversely, decreasing the flow resistance of the regulator 60 will increase the flow through the second bypass 310 and decrease the flow rate through the cooling lines.
In some examples, the quality (x) of the two-phase bubbly flow exiting the heat sink module(s) 100 can be monitored with a sensor. When the quality (x) reaches a predetermined threshold value (e.g. about 0.25), the flow resistance of the pressure regulator 60 in the second bypass 310 can be increased to reduce the flow rate through the pressure regulator and increase the flow rate through the heat sink module(s), thereby reducing the quality (x) of the flow exiting the heat sink module(s) to ensure the bubbly-flow does not transition to slug flow or churn flow (see FIG. 59B) within the flexible tubing 225, which could result in flow instability.
Pump
The pump 20 can be any pump capable of generating a positive coolant pressure that forces coolant 50 to circulate through the cooling apparatus 1. In some examples, the pump 20 can generate a positive coolant pressure that forces coolant through the primary cooling loop 300, into an inlet port of a heat sink module 100, and through a plurality of orifices 155 within the heat sink module, thereby transforming the flow of coolant into a plurality of jet streams 16 of coolant that impinge against the surface to be cooled 12, as shown in FIG. 26. In some examples, it can be desirable to select a pump 20 that is capable of pumping single-phase liquid coolant and increasing the pressure of the coolant to about 15-30, 25-45, 30-50, 40-65, 50-75, 60-85, 75-150, 5-200, 5-150, or 100-200 psi.
In some examples, the contents of the cooling apparatus 1 may be evacuated using a vacuum pump prior to adding the coolant 50, thereby resulting in a sub-atmospheric pressure within the cooling apparatus 1. The coolant may be added to the system from a container that is also at a sub-atmospheric pressure. Once inside the system, the coolant will remain at a sub-atmospheric pressure. When the pump 20 is activated, it can be capable of pumping single-phase liquid coolant and increasing the pressure of the coolant to about 5-20, 10-25, or 15-30 psi at the pump outlet 22. In this example, the coolant 50 may be HFE-7000, HFE-7100, R-245fa, or a mixture thereof. In one example, the coolant mixture can include about 60-95, 70-95, or 85-95% HFE-7000 by volume and the remainder can be R-245fa. In some examples, the pump pressure can be set at a suitable value to provide a flow rate of about 0.7-1.3, 0.8-1.2, or 0.9-1.1 liters per minute through each heat sink module 100 in the cooling apparatus 1.
In one example, the pump 20 can be a variable speed positive displacement pump, such as a MICROPUMP gear pump by Cole-Parmer of Vernon Hills, Ill. Although a constant speed pump 20 can be used for simplicity, a variable speed pump can provide greater flexibility for cooling dynamic heat loads, such as microprocessors 415 with varying utilization rates and temperatures, since the variable speed pump can enable the flow 51 of coolant 50 to be adjusted to meet a flow rate required to cool the estimated (e.g. theoretical) or actual (e.g. measured) heat load at the one or more surfaces to be cooled 12, and then adjusted in real-time if the heat load is greater or less than the estimated heat load. More specifically, increasing the flow rate of coolant 50 may be required where the heat load is greater than the estimated heat load to avoid reaching critical heat flux at the surface to be cooled 12. Alternately, decreasing the flow rate of coolant 50 may be required where the heat load is less than the estimated heat load to reduce unnecessary power consumption by the pump 20. The variable speed pump can be controlled by an electronic control system of the cooling apparatus 1.
In some examples, a pressurizer can be used in place of or in addition to the pump 20. The pressurizer can be pressurized by any suitable method or device, such as a pneumatic or hydraulic device that coverts mechanical motion to fluid pressure to provide a volume of pressurized coolant within the pressurizer that is then used to circulate coolant 50 through the cooling apparatus 1.
Reservoir
In the cooling system 1, the pump 20 can be in fluid communication with a coolant reservoir 200. In some examples, the reservoir 200 can be a metal tank, such as a steel or aluminum tank (see, e.g. FIG. 3), or a plastic tank with a suitable pressure rating. In other examples, the reservoir 200 can be any suitable vessel that is capable of receiving a volume of coolant and safely housing the volume of coolant in compliance with any governing regulations. As described herein, with respect to certain embodiments of the cooling apparatus 1, such as embodiments shown in FIGS. 11A-D, the reservoir 200 can be configured to receive a variety of fluid flows, including two-phase bubbly flow via a primary cooling loop 300 and single-phase liquid flow via a first bypass loop 305. However, despite receiving two-phase bubbly flow via the return line 230 of the primary cooling loop 300, the cooling apparatus 1 can be configured to provide exclusively single-phase liquid coolant from a reservoir outlet to an inlet 21 of the pump 20. As vapor bubbles 275 are introduced to the reservoir by bubbly flow from the return line 230, the bubbles 275 tend to migrate to the top of the reservoir 200, and single-phase liquid tends to settle in the lower portion of the reservoir due to gravitational effects. A section of tubing 220, such as rigid or flexible section of tubing, can connect the reservoir 200 to the inlet 21 of the pump 20. In some examples, the section of tubing 220 can connect to a reservoir outlet located along a lower portion of the reservoir 200, and preferably at or near a bottom portion of the reservoir, to ensure that only single-phase liquid coolant, and not two-phase coolant, is drawn from the reservoir and provided to the inlet 21 of the pump 22. Providing only single-phase liquid coolant to the pump 20 can ensure that cavitation within the pump is avoided. Cavitation can occur if two-phase flow is provided to the pump, and is undesirable, since it can damage pump components, resulting in diminished pump capacity or pump failure.
To ensure that only single-phase liquid coolant is provided to the pump 20, and thereby avoiding pump cavitation, the volume of coolant in the reservoir 200 can be selected to be a certain volume ratio of the total volume of coolant in the cooling apparatus 1. Increasing the volume ratio can increase the likelihood that any vapor bubbles 275 within the two-phase bubbly flow being delivered to the reservoir 200 from the one or more heat sink modules 100 will have an opportunity to condense back to liquid before that quantity of coolant is drawn from the reservoir 200 and delivered back to the pump inlet 21 for recirculation through the cooling apparatus 1. The preferred volume ratio can depend on a variety of factors, including, for example, the heat load associated with the surface being cooled 12, the properties of the coolant 50 being used, the flow rate of coolant in the system, the flow quality (x) of coolant being returned to the reservoir 200, the percentage of coolant flow 51 being diverted through the first and second bypasses (305, 310), the operating pressure of the coolant, and the performance of the heat exchanger 40. In some examples, the volume ratio can be about 0.2-0.5, 0.4-1.0, 0.6-1.5, 1.0-2.0, or greater than 2.0. It can be desirable to encourage condensing of any bubbles that may be delivered to the reservoir 200 as two-phase bubbly flow returning from the one or more heat sink modules 100. Experiments have shown that maintaining the reservoir 200 at a fill level of about 30-90%, 40-80%, or 50-70%, (where fill level is defined as the percent volume of the reservoir 200 occupied by liquid coolant 50) results in effective condensing of bubbles 275 that are delivered to the reservoir by the return line 230. A liquid-vapor interface is established at the fill level of the reservoir 200, and this liquid-vapor interface may encourage condensation of the bubbles 275 due to hydrodynamic effects acting on the two-phase bubbly flow as it is delivered to (e.g. poured or sprayed into) the reservoir 200 and passes through the liquid-vapor interface within the reservoir and mixes with the sub-cooled single-phase liquid coolant residing in the reservoir. As shown in FIG. 3, the return line 230 carrying the two-phase bubbly flow can deliver the two-phase bubbly flow near an upper portion of the reservoir 200. In some examples, the delivery point of two-phase bubbly flow to the reservoir 200 can be located above the fill level of the reservoir to ensure the two-phase bubbly flow is delivered into the head space (i.e. vapor region) of the reservoir, such that gravity draws the two-phase bubbly flow downward through the liquid-vapor interface.
In some examples, the reservoir 200 can include a baffle positioned in the head space of the reservoir or partially in the head space and partially below the fill level (i.e. passing through the liquid-vapor interface). The baffle can be configured to encourage condensing of bubbles 275 in two-phase bubbly flow delivered to the reservoir 200. The baffle can span all or a portion of the reservoir 200 and can be positioned horizontally, vertically, or obliquely within the reservoir. The baffle can be made of a thermally conductive material, such as steel, aluminum, or copper. When two-phase bubbly flow 51 is delivered to the reservoir 200, the flow can pass through openings (e.g. a plurality of slots or holes) in the baffle, and heat can transfer from the two-phase bubbly flow to the baffle and, in some cases, to the walls of the reservoir 200 to which the baffle is mounted or in contact with. As heat is transferred away from the two-phase bubbly flow, bubbles 275 within the coolant 50 can condense, either due to decreases in the bulk fluid temperature in the reservoir or due to local decreases in fluid temperature proximate the condensing bubbles. The openings in the baffle can have any suitable shape. Non-limiting examples of baffle opening shapes include triangular, round, oval, rectangular, or hexagonal, or polygonal.
Inlet and Outlet Manifolds
As shown in FIG. 12T, an inlet manifold 210 can receive coolant 50 and can deliver the coolant to one or more portions of flexible tubing 225 that deliver the coolant to one or more heat sink modules 100 fluidly connected between the inlet manifold 210 and an outlet manifold 215. The inlet manifold 210 can have an inner volume that serves as an in-line reservoir for the coolant and effectively dampens pressure pulsations in the flow 51 of coolant that may be transmitted from the pump 20. In some examples, the proper size of the inner volume of the inlet manifold 210 can be determined by the flow rate of coolant 50 through the inlet manifold. For instance, the inner volume of the inlet manifold 210 may be configured to hold a volume of coolant that is greater than or equal to a volume equivalent to at least 5 seconds of coolant flow through the manifold. So for a coolant flow rate of about 1 liter/minute, the inlet manifold 210 can have an inner volume of about 0.083 liters. For smoother operation, and greater damping of pressure pulsations, the inlet manifold 210 can have an inner volume capable of storing at least 10, 15, 20 or more seconds of coolant flow 51. The outlet manifold 215 can be configured to have a similar internal volume as the inlet manifold 210 to provide similar damping of pressure pulsations between the heat sink modules 100 and the return line 230.
FIG. 12T shows a schematic of a cooling apparatus 1 configured to cool two racks 410 of servers 400. The cooling apparatus 1 in FIG. 12T has a similar configuration as the cooling apparatus 1 shown in FIGS. 1-3, but the cooling apparatus 1 in FIG. 12T only shows two server racks 410, whereas the cooling apparatus in FIGS. 1-3 shows eight server racks 410. Also, the cooling apparatus 1 in FIG. 12T shows fewer parallel cooling lines extending between each inlet and outlet manifold (210, 215). Nevertheless, the overall concept is similar. The cooling apparatus 1 in FIG. 12T includes a dedicated inlet manifold 210 and outlet manifold 215 for each server rack 410. This configuration provides a modular cooling system 1 that can be increased in size to accommodate additional server racks 410, for example, as a data center 425 increases its server count. Therefore, the configuration in FIG. 12T can easily be modified to resemble the configuration shown in FIGS. 1-3 by adding six additional server racks 410 and by increasing the number of cooling lines extending between each inlet and outlet manifold (210, 215).
FIG. 4 shows a rear side view of a server rack 410 with an inlet manifold 210 and outlet manifold 215 mounted vertically to the server rack 410. The inlet manifold 210 and the outlet manifold 215 can be fitted with a plurality of fittings 235, such as quick-connect fittings, that permit individual cooling loops 300 to be hot swapped without interrupting coolant flow through other cooling loops 300 of the apparatus 1. As shown in FIG. 4, the inlet and outlet manifolds (210, 215) can each include a plurality of fittings to permit a plurality of cooling lines 300 to be connected to each manifold. In some examples, the inlet and outlet manifolds (210, 215) can include extra, unutilized fittings 235, as shown in FIG. 4, to permit future expansion of the number of servers 400 cooled by the cooling apparatus 1.
Although the inlet and outlet manifolds (210, 215) are shown in a vertical orientation in FIG. 4, this is not limiting. As discussed herein, because the vapor bubbles 275 within the two-phase bubbly flow are effectively dispersed and suspended in the coolant flow and do not seek a high point in the cooling apparatus 1 in response to gravitational effects, the system components (such as the outlet manifold 215) do not need to be vertically oriented to ensure collection of vapor, as competing systems do. Consequently, the outlet manifold 215 can be oriented horizontally or at any other suitable orientation that is preferable for a particular installation in view of space constraints and manifold size.
Flexible Tubing
FIG. 5 shows a top perspective view of a server 400 with its lid removed and a portion of a cooling apparatus 1 having a primary cooling loop 300 installed within the server housing. The cooling loop 300 includes two heat sink modules 100 mounted on vertically oriented heat-generating components (e.g. CPUs) within the server 400. The heat sink modules 100 are arranged in a series configuration and are fluidly connected with sections of flexible tubing 225 to transport coolant between neighboring heat sink modules, from an outlet port 105 of the first heat sink module 100 to an inlet port 105 of the second heat sink module. In some examples, others types of tubing can be used, such as smooth tubing 225, as shown in FIG. 4. More specifically, smooth nylon or fluorinated ethylene propylene (FEP) tubing 225 can be used. In some examples, the flexible tubing 225 can be FEP tubing from Cole-Parmer of Vernon Hills, Ill. and can have a maximum temperature rating of about 400 degrees F., an inner diameter of about 0.25-0.375 inches, and a maximum working pressure of about 210 psi. The flexible tubing 225 can be chemically inert, nontoxic, heat resistant, and have a low coefficient of friction. In addition, the flexible tubing 225 may not deteriorate with age.
In some applications, corrugated, flexible tubing 225 can provide certain advantages. For instance, corrugated tubing can resist kinking when routed in space-constrained applications, such as within servers 400 as shown in FIGS. 5 and 6. Flexible, corrugated tubing can be routed in configurations where the tubing contains bends that result in 180-degree directional changes without kinking, as shown in FIG. 6. In some examples, the flexible, corrugated tubing 225 can be corrugated FEP tubing from Cole-Parmer and can have a maximum temperature rating of about 400 degrees F. and a maximum working pressure of about 250 psi.
An advantage of corrugated tubing 225 is that, when transporting two-phase bubbly flow, it may delay the onset of slug flow by causing the breakdown of larger bubbles into smaller bubbles and causing the breakdown of clusters of bubbles due to frictional effects acting on the bubbles as they pass through the corrugated tubing and contact the inner walls of the tubing. Slug flow occurs when one or more large or bullet-shaped bubbles of vapor form within the tubing 225. As shown in FIG. 58, large vapor bubbles within slug flow may be nearly as wide as the inner diameter of the tubing. Slug flow is undesirable, since it can create flow instabilities in the cooling apparatus 1, resulting in surging or chugging within the cooling loops 300, making it difficult to maintain desired pressures in certain components of the cooling system 1, such as the heat sink modules 100, and thereby making it difficult to provide consistent and predictable cooling of a heated surface 12. Slug flow can be combated by increasing the flow rate through the heat sink modules 100 to reduce flow quality (x) (due to less vapor formation), thereby restoring two-phase bubbly flow, for example, between series-connected heat sink modules 100. In some examples, the cooling apparatus 1 can be configured to detect the onset of slug flow (e.g. using a visual flow detection system) at an outlet port 110 of a heat sink module 100 or at some other point in the cooling loop 300 and to automatically increase the coolant flow rate 51 to restore two-phase bubbly flow at the outlets of the one or more heat sink modules 100.
Another advantage of corrugated tubing 225 is that it can resist collapse when vacuum pressure is applied to an inner volume of the tubing. Vacuum pressure may be applied to the tubing 225 during servicing of the cooling apparatus 1. For example, when draining coolant 50 from the system 1 to allow for repairs or maintenance to be performed, vacuum pressure can be applied to a location (e.g. a drain 245) in the cooling apparatus 1 to draw out coolant 50 from the tubes and components of the apparatus. Portions of the cooling apparatus 1 can then be safely disassembled without having to make other arrangements for containment of the coolant. Removing coolant 50 through the application of vacuum pressure can allow the coolant to be captured in a vessel and reused to fill the apparatus when servicing is complete, thereby reducing servicing costs and waste that would otherwise be associated with discarding and replacing the coolant.
FIG. 6 shows a top view of a server 400 with its lid removed and a portion of a cooling apparatus 1 visible within the server. This example of a server 400 includes a motherboard 405, two microprocessors 415, and two sets of three memory modules 420. The two microprocessors 415 are mounted parallel to the motherboard 405, and the memory modules 420 are mounted perpendicular to the motherboard 405. The cooling apparatus 1 includes two heat sink modules 100 arranged in a series configuration and fluidly connected by flexible sections of flexible tubing 225. The first heat sink module 101 is mounted on a first microprocessor, and the second heat sink module 102 is mounted on a second microprocessor. A first section of flexible tubing 225 delivers coolant the an inlet port 105 of the first heat sink module 101, and a second section of flexible tubing 225 delivers coolant from an outlet port 110 of the first heat sink module 101 to an inlet port 105 of the second heat sink module 102. As, shown, due to its flexibility, the second section of flexible tubing 225 can easily be routed around server components for ease of installation. The flexible tubing 225 can be arranged in a variety of configurations, including serpentine configurations, to allow any two heat sink modules 100 (e.g within a server housing) to be fluidly connected regardless of the orientation or placement of the two heat sink modules.
The heat sink modules 100 can be used within the server 400 to cool electrical components that produce the most heat, such as the microprocessors 415. Other components within the server 400 may also produce heat, but the amount of heat produced may not justify installation of additional heat sink modules 100. Instead, to remove heat generated by other electrical devices within the server 400, one or more fans 26 can be used to expel warm air from the server 400 housing, as shown in FIG. 6. The fans can be configured to draw cool room air into the server housing 400 and to expel warm air from the housing.
In some examples, the length of a section of flexible tubing 225 between series-connected modules can be at least 4, 6, 12, 18, or 24 inches in length. In some applications, increasing the length of the section of tubing 225 can promote condensation of bubbles 275 within the bubbly flow between series-connected heat-sink modules due to heat transfer from the liquid to the tubing 225 and ultimately from the tubing to the ambient air, as well as heat transfer within the coolant from the vapor portion of the flow to the liquid portion of the flow, thereby elevating the bulk fluid temperature as vapor bubbles collapse. In some applications, increasing the length of the second section of flexible, corrugated tubing 225 may promote breaking apart of clusters of bubbles that may form in the two-phase flow, thereby delaying the onset of plug/slug flow and maintaining two-phase bubbly flow.
Coolant Filter
FIG. 13 shows a schematic of a cooling apparatus 1 including a filter 260 located between the reservoir 200 and the pump 20 in the primary cooling loop 300. The filter 260 can trap and prevent debris from entering and damaging the pump 20. Likewise, the filter 260 can trap and prevent debris from passing through the primary cooling loop 300 to the one or more heat sink modules 100, where the debris could potentially clog small orifices 155 in the heat sink modules. The cooling apparatus 1 can include one or more filters 260 placed upstream or downstream of the pump 20, or in any other suitable locations. The filter 260 can be connected inline using quick-connect fittings. The filter 260 can be a disposable filter or a reusable filter. The filter can have a micron rating of about 5, 10, or 20 microns.
In some examples, the heat sink module 100 can include a filter 260 to ensure that no debris is permitted to enter the heat sink module and clog orifices 155 within the heat sink module. The filter 260 can be disposed within the heat sink module (e.g. a removable filter that is inserted within the inlet port 105, inlet passage 165, or inlet chamber 145), or can be attached in-line with the heat sink module 100, such as a filter component that is threaded onto the inlet port and that contains a filtration device. By placing the filter 260 in or immediately upstream of the heat sink module 100, clogging of orifices 155 within the heat sink module can be avoided regardless of where debris originates from in the cooling apparatus 1.
Heat Sink Module
The heat sink module 100 can be configured to mount on a surface to be cooled 12 and provide a plurality of jet streams 16 (e.g. an array of jet streams 16) of coolant that impinge against the surface to be cooled 12 to effectively remove heat from the surface to be cooled. By removing heat from the surface to be cooled 12, the heat sink module 100 can effectively maintain the temperature of the surface to be cooled 12 at a suitable level so that a device associated with the surface to be cooled 12 is able to operate without overheating (i.e. operate below a threshold temperature).
The heat sink module 100 can include a top surface 160 and a bottom surface 135 opposite the top surface. The heat sink module 100 can be uniquely sized and shaped for a particular application. For instance, where the heat sink module 100 is tasked with cooling a square-shaped microprocessor, the heat sink module 100 can have a square perimeter, as shown in FIGS. 21-24. In this example, the heat sink module 100 can be defined by a front side surface 175, a rear side surface 180, a left side surface 185, a right side surface 190, the top surface 160, and the bottom surface 135. In other applications, the perimeter shape of the heat sink module 100 can be round, polygonal, or non-polygonal.
The heat sink module 100 can have any suitable sealing feature located on the bottom surface 135 to facilitate sealing against the surface to be cooled 12 or against an intermediary surface, such as a surface of a thermally-conductive base member (e.g. a copper plate 430) that is adhere to the surface to be cooled 12. In some examples, the heat sink module 100 can include a channel 140 along its bottom surface 135, as shown in FIG. 24. The channel 140 can be configured to receive a suitable sealing member 125, such as a gasket or O-ring, as shown in FIG. 23. In some examples, the channel 140 can be a continuous channel that circumscribes an outlet chamber 150 of the heat sink module 100, as shown in FIG. 24. In other examples, the heat sink module 100 can include alternate or additional sealing materials, such as a liquid gasket material, a die cut rubber gasket, an adhesive sealant, or a 3-D printed gasket provided on the bottom surface 135 of the heat sink module 100.
Although the bottom surface 135 of the heat sink module shown in FIG. 23 is flat, this is non-limiting. For applications involving a contoured surface to be cooled 12, the bottom surface 135 of the heat sink module 100 can have a corresponding contour that matches the contour of the surface to be cooled 12 and a thereby allows a sealing member 125 disposed therebetween to provide a liquid tight seal. In one example, the bottom surface 135 of the heat sink module can have a contour configured to match an external surface contour of a cylindrical tube or vessel (e.g. a metallic vessel) used in a chemical process, such as a condensation process or cooling wort in a brewing process. The contoured bottom surface 135 of the heat sink module 100 can allow the heat sink module to be form a liquid-tight seal against the tube or vessel and cool an external surface of the tube or vessel that is exposed within the outlet chamber 150 of the heat sink module 100. Where the contents of a large vessel must be cooled rapidly, such as when chilling wort in a brewing process, a plurality of heat sink modules 100 can be arranged on the external surface(s) of the large vessel to remove heat from the vessel rapidly, thereby allowing the cooling apparatus 1 to replace a glycol chiller system in a modern brewery or a counterflow chiller (which uses a significant amount of chilled water) in a more traditional brewery.
The heat sink module 100 can include mounting holes 130 or locating holes, as shown in FIGS. 21 and 23, located near corners of the module and/or along one or more perimeter portions of the module. Fasteners 115 can be inserted through the mounting holes 130, as shown in FIG. 22, and installed into threaded holes associated with a mounting surface to which the heat sink module 100 is mounted, such as a mounting surface of a thermally conductive base member 430 (e.g. a copper base plate) or directly to a mounting surface of an electrical device (e.g. a microprocessor 415 or a motherboard 405). In some examples, screw-type fasteners 115 can be replaced with alternate types of fastening devices that allow for faster installation and/or removal of the heat sink module 100. In one example, the heat sink module 100 can be fastened to a heat source using a buckle mechanism, similar a ski boot buckle, to allow for rapid, tool-less installation. In other examples, the heat sink module 100 can be received by a snap fitting on the surface to be cooled 12, thereby allowing the heat sink module to be installed and uninstalled with ease by hand and without tools.
During installation of the heat sink module 100 on a surface to be cooled 12, one or more fasteners 115 can be inserted through one or more 130 holes in the heat sink module, and the one or more fasteners can engage mounting holes in the surface 12 to permit secure mounting of the heat sink module 100 to the surface 12. As the fasteners 115 are tightened, the heat sink module 100 can be drawn down tightly against the surface to be cooled 12, and the sealing member 125 (e.g. o-ring or gasket) can be compressed between the surface and the channel 140. Upon compression, the sealing member 125 can provide a liquid-tight seal to ensure that coolant 50 does not leak from the outlet chamber 150 during operation of the cooling system 1 as coolant 50 flows from the inlet port 105 to the outlet port 110 of the heat sink module 100.
The heat sink module 100 can include an inlet port 105, as shown in FIG. 21. The inlet port 105 can have internal or external threads 170 that allow a connector 120 to be connected to the inlet port. Any suitable connector 120 can be used to connect the inlet section of flexible tubing 225 to the inlet port 105. In some examples, as shown in FIG. 22, a metal or polymer connector 120 from Swagelock Company of Solon, Ohio can be used to connect the flexible tubing to the inlet port 105. The top surface 160 of the heat sink module 100 can include visual markings 132 to identify a preferred flow direction through the heat sink module to ensure proper routing of tubing to and from the heat sink module 100 to ensure that coolant flow 51 is delivered to the inlet port 105 and exits from the outlet port 110 and is not accidentally reversed.
As shown in FIG. 25, the heat sink module 100 can include an inlet passage 165 that fluidly connects the inlet port 105 to an inlet chamber 145 of the heat sink module. The heat sink module 100 can include a dividing member 195 that separates the inlet chamber 145 from the outlet chamber 150. The dividing member 195 can have a top surface and a bottom surface and can include one or more orifices 155 passing from the top surface to the bottom surface of the dividing member. The orifices 155 permit jet streams 16 of coolant 50 to be emitted from the bottom surface of the dividing member 195 and into the outlet chamber 150 when pressurized coolant 54 is delivered to the inlet chamber 145, as shown in FIG. 26.
As shown in the cross-sectional view of FIG. 25, the inlet chamber 145 can have a geometry that tapers in cross-sectional area from the front side surface 175 of the heat sink module 100 toward the rear side surface 180 of the heat sink module. The tapered cross-sectional area of the inlet chamber 145 can ensure that all orifices 155 receive coolant 50 at a similar pressure. Similarly, the outlet chamber 150 can increase in cross-sectional area in a direction from the rear surface 180 of the heat sink module toward the front surface 175 of the heat sink module 100. The increase in cross-sectional area of the outlet chamber 150 can provide suitable volume for expansion of the coolant that may occur as a portion of the liquid coolant transitions to vapor, as shown in FIG. 30, and exits the outlet port 110 of the heat sink module 100.
The heat sink module 100 can include one or more inlet passages 165 to permit fluid to enter the inlet chamber 145 and one or more outlet passages 166 to permit fluid to exit the outlet chamber 150. In this manner, the heat sink module 100 can be configured to permit fluid to flow through the outlet chamber 150. A dividing member 195 can at least partially separate the inlet chamber 145 from the outlet chamber 150. A plurality of orifices 155 can be formed in the dividing member as shown in FIGS. 24 and 25. The plurality of orifices 155 can be configured to each project a stream 16 of coolant 50 against the surface to be cooled 12. In some examples, the streams 16 of fluid projected against the surface 12 can be jet streams. As used herein, a “jet” or “jet stream” refers to a substantially liquid fluid filament that is projected through a substantially liquid or fluid medium or a mixture thereof. As used herein, a “jet stream” can include a single-phase liquid fluid filament or a two-phase bubbly flow filament. “Jet” or “jet stream” is contrasted with “spray” or “spray stream,” where “spray” or “spray stream” refers to a substantially atomized liquid fluid projected through a substantially vapor medium.
The inlet chamber 145 and the outlet chamber 150 can be formed within the heat sink module 100. The heat sink module 100 can be made from any suitable material and manufactured by any suitable manufacturing process. In some examples, the heat sink module 100 can be made of a polymer material and formed through a 3D printing process, such as stereolithography (SLA) using a photo-curable resin. Printers capable of producing heat sink modules as shown in FIGS. 21-54 are available from 3D Systems, Inc. of Rock Hill, S.C. In other examples, a module body can be injection molded to reduce cost and manufacturing time and an insertable orifice plate can be 3-D printed and attached to the module body to complete the heat sink module 100.
The heat sink module 100 can be configured to cool a surface 12 of a heat source. The heat sink module 100 can include an inlet chamber 145 formed within the heat sink module and an outlet chamber 150 formed within the heat sink module. In some examples, the outlet chamber 150 can have an open portion along the bottom side surface 135 of the heat sink module 100, as shown in FIG. 23. The open portion of the outlet chamber 150 can be enclosed by the surface 12 of a heat source when the heat sink module 100 is installed on the surface 12 of the heat source, as shown in FIG. 26. The heat sink module 100 can include a dividing member 195 disposed between the inlet chamber 145 and the outlet chamber 150. The dividing member 195 can include a first plurality of orifices 155 formed in the dividing member. The first plurality of orifices 155 can pass from a top side of the dividing member 195 to a bottom side of the dividing member and can be configured to deliver a plurality of jet streams 16 of coolant 50 into the outlet chamber 150 when pressurized coolant 54 is provided to the inlet chamber 145, as shown in FIG. 26.
The first plurality of orifices 155 can have any suitable diameter that allows the orifices to provide well-formed jets streams 16 of coolant 50 when pressurized coolant 54 is delivered to the inlet chamber 145 of the heat sink module 100. In some examples, the orifices 155 may all have uniform diameters, and in other examples, the orifices may not all have uniform diameters. In either case, the average diameter of the orifices 155 can be about 0.001-0.020, 0.001-0.2, 0.001-0.150, 0.001-0.120, 0.001-0.005, or 0.030-0.050 in.
In some examples, to ensure that well-formed jet streams 16 of coolant 50 are provided by the orifices 155, the length of the orifice can be selected based on the diameter of the orifice. For instance, where the first plurality of orifices 155 are defined by a diameter D and an average length L, in some cases L divided by D can be greater than or equal to one, about 1-10, 1-8, 1-6, 1-4, or 1-3. In the configuration shown in FIG. 26, the length of each orifice 155 can be determined based on an angle of the orifice with respect to the surface to be cooled 12 and based on the thickness of the dividing member 195. In some examples the dividing member 195 can have a thickness of about 0.005-0.25, 0.020-0.1, 0.025-0.08, 0.025-0.075, 0.040-0.070, 0.1-0.25, or 0.040-0.070 in. The thickness of the dividing member 195 can be selected to provide a desired length for the orifices 155 and to insure structural integrity of the heat sink module 100 when receiving pressurized coolant 54 in the inlet chamber 145. To minimize the height of the heat sink module 100 (e.g. to provide greater freedom when dealing with tight packaging constraints), it can be desirable to select the minimal dividing member thickness that still provides well-formed jet streams 16 and adequate structural integrity.
The heat sink module 100 can be made of any suitable material or process (e.g. a three-dimensional printing process) and can have any suitable color or can be colorless. In some examples, it may be desirable to visually inspect the operation of the heat sink module 100 to ensure that boiling is occurring within the heat sink module proximate the surface to be cooled 12. To permit visual inspection, at least a portion of the heat sink module 100 can be made of a transparent or translucent material. In some examples, the transparent or translucent material can form the entire heat sink module 100, and in other examples, the transparent or translucent material can form only a portion of the heat sink module, such as a window into the outlet chamber 150 of the heat sink module or a side wall of the heat sink module. In these examples, the window or side wall can permit boiling coolant within the outlet chamber 150 to be observed when the heat sink module 100 is installed on the surface to be cooled 12.
Orifices within Heat Sink Module
Each orifice 155 within the heat sink module 100 can include a central axis 74, as shown in FIG. 30. The central axis 74 of the orifice 155 may either be angled perpendicularly with respect to the surface to be cooled 12 or angled non-perpendicularly with respect to the surface to be cooled 12, the latter of which is shown in FIG. 30. FIG. 20 shows a cross-sectional view of a heat sink module with orifices 155 arranged at a 45-degree angle with respect to the surface to be cooled 12. If angled non-perpendicularly with respect to the surface to be cooled 12, the central axis 74 of the orifice 155 may define any angle between 0° and 90° with respect to the surface 12, such as about 5°, about 10°, about 15°, about 20°, about 25°, about 30°, about 35°, about 40°, about 45°, about 50°, about 55°, about 60°, about 65°, about 70°, about 75°, about 80° or about 85° or any range therebetween (e.g. 5-15°, 10-20°, 15-25°, 20-30°, 25-35°, 30-40°, 35-45°, 40-50°, 45-55°, 50-60°, 55-65°, 60-70°, 65-75°, 70-80°, or 75-85°). The orifice 155 may comprise any cross-sectional shape when viewed along its central axis 74. Various examples include a circular shape, an oval shape (to generate a fan-shaped jet stream), a polygonal shape, or any other suitable cross-sectional shape.
FIG. 31 shows a top cross-sectional view of the heat sink module of FIG. 21 taken along section C-C shown in FIG. 25. Section C-C passes through the dividing member 195 and exposes the array 76 of orifices 155 within the heat sink module 100. In this example, because the central axes 74 of the plurality of orifices are arranged at a 45-degree angle with respect to the dividing member 195, the orifices appear as ovals in FIG. 31 despite the orifice being cylindrical coolant passageways through the dividing member.
The heat sink module 100 preferably includes an array 76 of orifices 155. The central axes 74 of the orifices 155 in the array 76 may define different angles with respect to the surface to be cooled 12. Alternately, the central axis 74 of each orifice 155 in the array 76 may have the same angle with respect to surface 12, as shown in FIG. 30. In some examples, providing neighboring orifices with central axes 74 with the same angle with respect to the surface to be cooled 12 can be preferable to avoid interaction (i.e. interference) of the jet streams 16 prior to impingement on the surface to be cooled 12. By providing jet streams 16 that do not interfere with each other prior to impingement, the heat sink module 100 can provide jet streams 16 with sufficient momentum to disrupt vapor formation on the surface to be cooled 12, thereby increasing the three-phase contact line length on the surface to be cooled 12 and allowing higher heat fluxes to be effectively dissipated without reaching critical heat flux.
The array 76 of orifices 155 may be arranged in any configuration suitable for cooling the surface to be cooled 12. FIG. 62 shows possible orifice 155 configurations including (a) a regular rectangular jet array 76, (b) a regular hexagonal jet array 76, and (c) a circular jet array 76. In the regular hexagonal array 76, shown in FIGS. 23, 31 and 62(b), the arrays 76 can be organized into staggered columns 77 and rows 78. The staggering of orifices 155 in the array 76 is such that a given orifice 155 in a given column 77 and row 78 does not have a corresponding orifice in a neighboring row 78 in the given column 77 or a corresponding orifice 155 in a neighboring column 77 in the given row 78. If the orifices 155 are configured to induce a substantially same direction of flow 90 along the surface to be cooled 12 (as shown in FIGS. 30 and 32), the columns 77 and the rows 78 are preferably oriented substantially parallel and perpendicular, respectively, to the substantially same direction of flow 90. Arrays of orifices 155 in non-staggered arrangements can be used in other examples of the heat sink module 100.
The orifice 155 can be configured to project a jet stream 16 having any of a variety of shapes and any of a variety of trajectories. With regard to shape, the stream 16 is preferably a symmetrical stream. As used herein, “symmetrical stream,” refers to a jet stream 16 that is symmetrical in cross section. Examples of symmetrical streams include linear streams, fan-shaped streams, and conical streams. Linear streams have a substantially constant cross section along their length. Conical streams have a round cross section that increases along their length. Fan-shaped streams have a cross section along their length with a first cross-sectional axis being significantly longer than a second, perpendicular cross-sectional axis. In some versions of the conical jet streams 16, at least one and possibly both of the cross-sectional axes increase in length along the length of the stream. With regard to trajectory, the jet stream 16 preferably comprises a central axis 17. For the purposes herein, the “central axis 17 of the stream 16” is the line formed by center points of a series of transverse planes taken along the length of the stream 16, where each transverse plane is oriented to overlap with the smallest possible surface area of the stream 16, and each center point is the point on the transverse plane that is equidistant from opposing edges of the stream 16 along the transverse plane. In preferred versions, the orifice 155 projects a jet stream 16 having a central axis 17 that is substantially collinear with the central axis 74 of the orifice 155. However, the orifice 155 may also project a stream 16 having a central axis 17 that is angled with respect to the central axis 74 of the orifice 155. The angle of the central axis 17 of the stream 16 with respect to the central axis 74 of the orifice 155 may be any angle between 0° and 90°, such as about 1°, about 2°, about 3°, about 4°, about 5°, about 7°, about 10°, about 15°, about 20°, about 25°, about 30°, about 35°, about 40°, about 45°, about 50°, about 55°, about 60°, about 65°, about 70°, about 75°, or about 80° or any range therebetween. In such versions, the orifice 155 preferably projects a jet stream 16 where at least one portion of the jet stream 16 is projected along the central axis 74 of the orifice 155. However, the orifice 155 may also project a jet stream 16 where no portions of the jet stream 16 are projected along the central axis 74 of the orifices 155.
Similarly, the orifice 155 may be configured to project a jet stream 16 that impinges on the surface 12 at any of a variety of angles. In some versions, the orifice 155 projects a stream 16 at the surface 12 such that the entire stream (in the case of a linear stream), or at least the central axis 17 of the stream 16 (in the case of conical or fan-shaped streams), impinges perpendicularly on the surface 12 (i.e., at a 90° angle with respect to the surface). Perpendicular impingement upon a surface 12 induces radial flow of coolant 50 from contact points along the surface 12. While arrays 96 of perpendicularly impinging streams 16 are suitable for some applications, they are not optimal in efficiency. This is because opposing coolant flow from neighboring contact points interacts to form stagnant regions. Heat transfer performance in these stagnant regions can fall to nearly zero, which in high heat flux applications (e.g. cooling high performance microprocessors or power electronics) can pose risks associated with critical heat flux.
In a preferred examples shown in FIGS. 30 and 32, the orifices 155 are configured to project jet streams 16 of coolant that impinge the surface to be cooled 12 such that at least the central axis 17 of each jet stream 16, and more preferably the entire jet stream 16, impinges non-perpendicularly on the surface to be cooled 12 (i.e, at an angle other than 90° with respect to the surface), as shown in FIGS. 30-32. As a non-limiting example, the central axis 17 of the jet stream 16 may impinge on the surface 12 at any angle between 0° and 90°, such as about 1°, about 2°, about 3°, about 4°, about 5°, about 7°, about 10°, about 15°, about 20°, about 25°, about 30°, about 35°, about 40°, about 45°, about 50°, about 55°, about 60°, about 65°, about 70°, about 75°, or about 80° or any range there between.
FIG. 32 depicts a top view of a surface 12 on which jet streams 16 of an array 76 of jet streams impinges non-perpendicularly on the surface 12. The non-perpendicular impingement creates a flow pattern 90 to the right in which all the coolant 50 flows along the surface 12 in substantially the same direction 90. In some versions of patterns flowing in substantially the same direction 90, flow of coolant 50 at each portion of the surface 12 has a common directional vector component along a plane defined by the surface to be cooled 12. In other versions, coolant 50 at no two points on the surface 12 flows in opposite directions. In yet other versions, coolant 50 at no two points on the surface 12 flows in opposite directions or flows in perpendicular directions. Flowing coolant 50 in the substantially same direction eliminates stagnant regions on the surface being cooled 12, which helps avoid the onset of critical heat flux.
The plurality of orifices 155 in the array 76 are preferably configured to provide impinging jet streams 16 of coolant on the surface 12 in an array 96 of contact points 91 (i.e. where each contact point 91 is a jet stream 16 impingement location on the surface to be cooled 12) comprising staggered columns 97 and rows 98, as shown in FIG. 32. The staggering is such that a given contact point 91 in a given column 97 and row 98 does not have a corresponding contact point 91 in a neighboring column 97 in the given row 98 or a corresponding contact point 91 in a neighboring row 98 in the given column 97. If the coolant 50 is induced to flow across the surface 12 in substantially the same direction 90, as shown in FIG. 32, either the columns 97 or the rows 98 are preferably oriented substantially perpendicularly to the substantially same direction 90 of flow. Arrays 96 of contact points 91 arranged in this manner permit coolant 50 emanating from each contact point 91 in a given column 97 or row 98 to flow substantially between contact points 91 in a neighboring column 97 or row 98, respectively, as shown in FIG. 32. The heat sink module 100 shown in FIGS. 21 and 30 provides even, consistent flow of coolant 50 over the surface to be cooled 12, without formation of stagnation regions, and thereby encourages bubble 275 generation and evaporation, which dramatically increases the heat transfer rate from the surface to be cooled 12.
The heat sink module 100 can include an array 76 of orifices 155 with each orifice 155 having a central axis 74 angled non-perpendicularly with respect to the surface 12, where each orifice 155 projects a jet stream 16 of coolant 50 having a central axis 17 collinear with the central axis 74 of the orifice 155. In some examples, all the orifices 155 can have central axes 74 oriented at about the same angle and can project jet streams 16 of coolant having about the same trajectory and shape and can impinge against the surface 12 at about the same angle of impingement.
The array 76 of orifices 155 can be provided within the heat sink module 100 as illustrated and described with respect to FIGS. 23-31. The plurality of jet streams 16 emitted from the plurality of orifices 155 can promote bubble generation and evaporation at the surface to be cooled 12, thereby achieving higher heat transfer performance than conventional single-phase liquid cooling systems. Other implementations may promote bubble 275 generation using structures within the orifices 155, such as structures that encourage cavitation or degassing of non-condensable gasses absorbed in the liquid. Similarly boiling-inducing members 196 can be included in the heat sink module 100, as shown in FIGS. 45-50, or can be included on the surface to be cooled 12, as shown in FIG. 55.
Jet Streams with Entrained Bubbles
In some examples, it can be desirable provide jet streams 16 that contain entrained bubbles 275 to seed nucleation sites on the surface to be cooled 12. Seeding nucleation sites on the surface to be cooled 12 can promote vapor formation and can increase a heat transfer rate from the surface to be cooled 12 to the coolant 50. FIG. 73 shows a first heat sink module 100 fluidly connected to a second heat sink module 100. A section of flexible tubing 225 transports coolant from an outlet port 110 of the first heat sink module 100 to an inlet port 105 of the second heat sink module 100. Within the first heat sink module 100, a plurality of jet streams 16 of coolant are shown impinging a first surface to be cooled 12. Due to heat transferring from the first surface to be cooled 12 to the coolant 50 within in the outlet chamber 150 of the first heat sink module 100, vapor bubbles 275 form in the coolant 50. The bubbles 275 can be dispersed within the liquid coolant as it exits the outlet port 110 of the heat sink module 100. As the coolant 50 flows within the tubing 225 toward the inlet port 105 of the second heat sink module, some of the bubbles 275 may coalesce and form larger bubbles. The small and large bubbles 275 can be transported to an inlet chamber 145 of the second heat sink module. The small bubbles may be sufficiently small to travel through the orifices 155 and become entrained in a jet stream that impinges against the surface to be cooled. When the small bubbles impinge the surface to be cooled 12, they may seed nucleation sites on the surface to be cooled 12 and promote vapor formation, which can provide higher heat transfer rates. In some examples, as shown in FIG. 73, the larger bubbles 276 may be too large to pass through the orifices 155. But pressure and flow forces may draw the larger bubbles 276 toward the orifices 155, where upon contacting the orifice inlets, the larger bubbles 276 break into smaller bubbles that can pass through the orifices 155 and be entrained in the jet streams 16. In this way, the size of the orifice 155 determines the maximum bubble size that will be entrained in the jet stream 16 and will impinge the surface to be cooled 12. To provide jet streams 16 with entrained bubbles 275 that provide desirable seeding of nucleation sites on the surface to be cooled 12, the orifice 155 diameters within the heat sink module 100 can be about 0.001-0.020, 0.001-0.2, 0.001-0.150, 0.001-0.120, 0.001-0.005, or 0.030-0.050 in.
Anti-Pooling Orifices
Pooling of coolant 50 within the outlet chamber 150 of the heat sink module 100 is undesirable, since it can create stagnation regions or other undesirable flow patterns that result in non-uniform cooling of the surface to be cooled 12, which can lead to critical heat flux issues. To avoid pooling of coolant 50 in the outlet chamber 150, the heat sink module 100 can include a second plurality of orifices 156 extending from the inlet chamber 145 to a rear wall (or proximate the rear wall) of the outlet chamber 150, as shown in FIGS. 33-38. The second plurality of orifices 156 can be configured to deliver a plurality of anti-pooling jet streams 16 of coolant to a rear portion of the outlet chamber 150 when pressurized coolant 54 is provided to the inlet chamber 145. As shown in FIG. 33, the second plurality of orifices 156 can be arranged in a column along the rear wall of the outlet chamber 150 thereby preventing coolant from pooling near the rear wall of the outlet chamber 150.
FIG. 35 shows a detailed view of one anti-pooling orifice 156 taken from the cross-sectional view of FIG. 34. The anti-pooling orifice 156 can be configured to deliver an anti-pooling jet stream 16 of coolant to a rear region of the outlet chamber 150 to prevent coolant from pooling or stagnating near the rear wall of the outlet chamber 150. The central axes 75 of the anti-pooling orifice 156 can be arranged at an angle of about 0-90, 40-80, 50-70, or 60 degrees respect to the surface to be cooled 12. In some examples, the central axes 75 of the anti-pooling orifice 156 can be at a larger angle than the central axes 74 of the plurality of orifices 155, as shown in FIG. 35. This arrangement can prevent interaction of the anti-pooling jet stream with a neighboring jet stream 16 prior to impingement on the surface to be cooled 12, thereby decreasing the likelihood of stagnation points on the surface to be cooled 12 near the rear wall of the outlet chamber 150.
Boiling-Inducing Features
As described above, achieving boiling of coolant 50 proximate the surface to be cooled 12 can dramatically increase the heat transfer rate and overall performance of the cooling apparatus 1. To encourage boiling of coolant 50 within the outlet chamber 150, the heat sink module 100 can include one or more boiling-inducing members 196 extending from the bottom surface of the dividing member 195 toward the surface to be cooled 12, as shown in FIG. 46. The one or more boiling-inducing members 196 can be slender members extending from the bottom surface of the dividing member 195. In some examples, the one or more boiling-inducing members 196 can be configured to contact the surface to be cooled 12. In other examples, the one or more boiling-inducing members 196 can be configured to extend toward the surface to be cooled but not contact the surface to be cooled. Rather, a clearance can be provided between the one or more boiling-inducing members 196 and the surface to be cooled 196, such that coolant 50 can flow between the surface to be cooled 12 and the tips of the boiling-inducing members, thereby ensuring that no hot spots or stagnation regions are created on the surface to be cooled 12. The clearance distance can be any suitable distance, and in some examples can be 0.001-0.0125, 0.001-0.05, 0.001-0.02, 0.001-0.01, or 0.005-0.010 in.
Angled Inlet and Outlet Ports
The inlet port 105 and outlet port 110 of the heat sink module 100 can be angled to provide ease of installation in a wide variety of applications. For instance, when installing the heat sink module 100 on a microprocessor 415 that is mounted on a motherboard 405, as shown in FIG. 27, if the inlet port 105 of the heat sink module is arranged at an angle (α) that is greater than zero, a clearance distance is provided between a bottom surface of the inlet port 105 and the microprocessor 415 and motherboard 405. This clearance distance can allow a connector 120, such as a compression fitting, to be easily installed (e.g. threaded) on the inlet port 105) without interfering with or contacting the microprocessor or motherboard. In addition, angling the port upwards reduces the likelihood that the heat sink module 100 (and flexible tubing 225 connected to the inlet port 105) will interfere with other components (e.g. memory module 420, power supply, wiring, or cooling fan 26) that may be installed in the server 400 housing near the heat sink module 100. As shown in FIGS. 5, 6, 56, and 57, free space can be limited within on a motherboard 405 and in a server 400, and experimental installations have shown that angled inlet and outlet ports (105, 110) can be very helpful in making heat sink modules 100 fit in tight spaces where they would not otherwise fit.
The heat sink module 100 can include an inlet port 105 that is fluidly connected to the inlet chamber 145 by an inlet passage 165. The heat sink module 100 can include a bottom plane 19 associated with the bottom surface 135, as shown in FIG. 26. The inlet port 105 can be defined by a central axis 23. The central axis 23 of the inlet port 105 can be non-parallel and non-perpendicular to the bottom plane 19 of the heat sink module 100. For instance, the central axis 23 of the inlet port 105 can define an angle of about 10-80, 20-70, 30-60, or 40-50 degrees with respect to the bottom plane 19 of the heat sink module 100.
The heat sink module 100 can include an outlet port 110 that is fluidly connected to the outlet chamber 150 by an outlet passage 166. The outlet port 110 can be defined by a central axis 24, as shown in FIG. 29. The central axis 24 of the outlet port 110 can be non-parallel and non-perpendicular to the bottom plane 19 of the heat sink module 100. For instance, the central axis 24 of the outlet port 110 can define an angle of about 10-80, 20-70, 30-60, or 40-50 degrees with respect to the bottom plane 19 of the heat sink module 100.
Insertable Orifice Plate
In some instances, the heat sink module 100 can include two or more components that are assembled to construct the heat sink module. Since the plurality of orifices 155 disposed in the dividing member 195 can be the most intricate and costly portion of the heat sink module 100 to manufacture (due to the relatively small diameters of the orifices 155 requiring a tighter tolerance manufacturing process than the rest of the module), it may be desirable to manufacture an orifice plate 198 (e.g. that includes a dividing member 195 and a plurality of orifices 155) separately from the rest of the heat sink module (i.e. the module body 104) and subsequently assemble the module body 104 and the orifice plate 198. FIG. 65 shows an insertable orifice plate 198 attached to a module body 104 to form heat sink module 100.
In some examples, the orifice plate 198 can be manufactured by a first manufacturing method and the module body 104 can be manufactured by a second manufacturing method where the second manufacturing method is, for example, a lower cost and/or lower precision manufacturing method than the first manufacturing method. In some examples, the orifice plate 198 can be manufactured by a 3-D printing process, and the module body can be manufactured by an injection molding process. In other examples, the orifice plate 198 can be manufactured by an injection molding process, a casting process, or a machining or drilling process, and the module body 104 can be manufactured by any other suitable process.
FIG. 65 shows a heat sink module 100 with a module body 104 and an insertable orifice plate 198 installed therein. The insertable orifice plate 198 can be attached to the heat sink module 100 by any suitable method of assembly (e.g. fasteners, press fit, or snap fit). As shown in FIG. 65, the insertable orifice plate 198 can be pressed into the body 104 of the heat sink module 100 and can include a sealing member 126 that is configured to form a liquid-tight seal between the inlet chamber 145 and the outlet chamber 150. In some examples, the insertable orifice plate 198 can be removable, and in other examples the insertable orifice plate 198 may not be easily removable once installed in the body of the heat sink module 100. The plurality of orifice 155 in the orifice plate 198 can be optimized to cool a certain device, such as a certain brand and model of microprocessor 415 having a particular non-uniform heat distribution. When the microprocessor 415 is upgraded to a newer model, a first insertable orifice plate 198 in the heat sink module 100 can be replaced by a second insertable orifice plate 198 that has been optimized to cool the newer model processor. Consequently, instead of needing to replace the entire heat sink module 100, only the insertable orifice plate 198 needs to be replaced to ensure adequate cooling of the newer model processor. This approach can significantly reduce costs associated with upgrading servers 400 in data centers 425.
A heat sink module 100 can be configured to cool a heat source, such as a surface 12 of a heat source. The heat sink module 100 can include an inlet chamber 145 formed within the heat sink module. The heat sink module 100 can include an insertable orifice plate 198 and a module body 104, as shown in FIG. 65, where the insertable orifice plate is configured to attach within the module body 104. The insertable orifice plate 198 can separate the inlet chamber 145 from an outlet chamber 150. The insertable orifice plate 198 can include a first plurality of orifices 155 passing from a top side of the insertable orifice plate 198 to a bottom side of the insertable orifice plate 198. The first plurality of orifices 155 can be configured to deliver a plurality of jet streams 16 of coolant 50 into the outlet chamber 150 when pressurized coolant 54 is provided to the inlet chamber 145 of the heat sink module 100. The outlet chamber 150 can have an open portion proximate a bottom surface of the heat sink module 100, and the open portion can be configured to be enclosed by a surface 12 of a heat source when the heat sink module is installed on the surface of the heat source. In this example, the first plurality of orifices 155 can have an average diameter of about 0.001-0.020, 0.001-0.2, 0.001-0.150, 0.001-0.120, 0.001-0.005, or 0.030-0.050 in. The insertable orifice plate 198 can have a thickness of about 0.005-0.25, 0.020-0.1, 0.025-0.08, 0.025-0.075, 0.040-0.070, 0.1-0.25, or 0.040-0.070 in.
Jet Height
The heat sink module 100 can have a bottom plane 19 associated with the bottom surface 135 of the heat sink module, as shown in FIG. 26. The distance between the bottom plane 19 of the heat sink module and the bottom side of the insertable orifice plate 198 (i.e. where orifice 155 outlets are located) defines a “jet height” 18, which can be an important factor affecting heat transfer rates attainable from the surface to be cooled 12 in response to impinging jets 16 of coolant 50 being delivered from the plurality of orifices 155. In some examples, the distance between the orifice 155 outlets and the surface to be cooled 12 can be about 0.01-0.75, 0.05-0.5, 0.05-0.25, 0.020-0.25, 0.03-0.125, or 0.04-0.08 in. In some examples, the jet height 18 can define the height of the outlet chamber 150 of the heat sink module 100.
As shown in FIG. 26, the outlet chamber 150 can have a tapered profile that permits for expansion of the coolant 50 as the coolant flows towards the outlet port 110 and as the quality (x) of the coolant increases in response to vapor formation proximate the surface to be cooled 12. To provide this tapered volume, the bottom surface of the dividing member may be arranged at an angle with respect to the surface to be cooled. Consequently, a jet height 18 of a first orifice 155 located near a front side of the heat sink module 100 may be less than a jet height 18 of a second orifice 155 located near a rear side of the heat sink module. In these examples, a non-uniform jet height 18 may be defined as falling within a suitable range, such as about 0.01-0.75, 0.05-0.5, 0.05-0.25, 0.020-0.25, 0.03-0.125, or 0.04-0.08 in. In other examples, an average jet height can be calculated based on the non-uniform jet height values, and the average jet height can be about 0.01-0.75, 0.05-0.5, 0.05-0.25, 0.020-0.25, 0.03-0.125, or 0.04-0.08 in.
In some examples, the distance between the bottom surface of the insertable orifice plate 198 (or dividing member 195) and the bottom surface 135 of the heat sink module 100 can define the jet height 18. The jet height (H) can be selected based on the average diameter (dn) of the plurality of orifices 155. The relationship between the jet height 18 and the average diameter of the plurality of orifices 155 can be expressed as a ratio (H/dn). Examples of suitable values for H/dn can be about 0.25-30, 0.25-10, 5-20, 15-25, or 20-30 for the heat sink module 100 described herein.
Jet Spacing
The orifices 155 within the heat sink module 100 can have any suitable configuration forming an array 76. FIGS. 62(a), (b), and (c) show configurations of orifices 155 having a rectangular jet array, a hexagonal jet array, and a circular jet array, respectively. Spacing (S) of the orifices 155 can be selected based on the average diameter (dn) of the plurality of orifices 155. As shown in FIG. 62(b), for a hexagonal jet array 76, spacing between jets from left to right (i.e. in a streamwise direction for oblique jet impingement as shown in FIG. 32) is identified as Scol, and spacing between jets from top to bottom (i.e. cross-stream direction for oblique impingement as shown in FIG. 32) is identified as Srow. Where Scol is set equal to S, and Srow is set equal to (2col/√3), a relationship between jet spacing S and the average diameter of the plurality of orifices 155 can be expressed as S/dn. Suitable values for S/dn can be about 1.8-330, 1.8-50, 25-125, 100-200, 150-250, 200-300, or 275-330 for the rectangular, hexagonal, and circular jet arrays 76 shown in FIGS. 62(a), (b), and (c), respectively.
Internal Threads on Inlet and Outlet Ports
In some examples, corrugated, flexible tubing 225 can be used to fluidly connect heat sink modules 100 to the cooling apparatus. The corrugated, flexible tubing 225 can include spiral corrugations extending along the length of the tubing 225, similar to course threads on a screw. To facilitate fast connection of a section of flexible tubing 225 to the heat sink module 100, corresponding corrugation-mating features can be provided on the interior surfaces of the inlet and outlet ports (105, 110) of the heat sink module. The corresponding corrugation-mating features can be molded into the inlet and outlet ports (105, 110) thereby serving as internal threads. As a result, fluidly connecting a section of flexible corrugated tubing 225 to a port (105 or 110) of the heat sink module 100 can be as simple as threading the section of tubing 225 into the port. In some examples the diameter of the port (105, 110) can taper inward, thereby ensuring a liquid-tight fit as the section of tubing 225 is threaded into the port. To further ensure a liquid-tight seal, a thread sealant, such as a Teflon tape or a spreadable thread sealant can be provided between the interior surface of the port (105, 110) and the outer surface of the section of flexible tubing 225. In other examples, an adhesive, such as epoxy, can be provided between the interior surface of the port (105, 110) and the outer surface of the section of flexible tubing 225 to further ensure a liquid-tight seal and to prevent inadvertent disconnection of the section of tubing from the port.
Leakproof Coating
The heat sink module 100 can be manufactured from a plastic material through, for example, an injection molding process or an additive manufacturing process. Depending of the properties of the plastic material used to manufacture the heat sink module 100, and the type of coolant 50 used with the cooling apparatus 1 (and the molecular size of the coolant), leakage of coolant through the walls of the heat sink module 100 may occur. To avoid leakage, the heat sink module 100 can be coated with a leakproof coating. In some examples, the leakproof coating can be a metalized coating, such as a nickel coating deposited on an outer surface of the heat sink module 100 or along the inner surfaces of the heat sink module (e.g. inner surfaces of the inlet and outlet ports, inlet and outlet passages, and inlet and outlet chambers). The leakproof coating can be made of a suitable material and can have a suitable thickness to ensure that coolant does not migrate through the walls of the heat sink module 100 and into the environment. The leakproof coating can be applied to surfaces of the heat sink module 100 by any suitable application method, such as arc or flame spray coating, electroplating, physical vapor deposition, or chemical vapor deposition.
Internal Bypass in Heat Sink Module
To promote condensing of two-phase bubbly flow upstream of the reservoir 200, and thereby reduce the likelihood of vapor being drawn into the pump 20 from the reservoir, the heat sink module 100 can include an internal bypass that routes a portion of the coolant 50 flow delivered to the inlet port 105 of the module around the heated surface 12. The internal bypass can be formed within the heat sink module 100. For instance, the internal bypass can be a, injection molded, cast, or 3D printed internal bypass formed within the heat sink module 100 and configured to transport coolant from the inlet port 105 to the outlet port 110 without bringing the fluid in contact with the surface to be cooled 12. The coolant that flows through the internal bypass can remain single-phase liquid coolant that is below the saturation temperature of the coolant. Near the outlet port 110 of the heat sink module 100, the single-phase liquid coolant that is diverted through the internal bypass can be mixed with two-phase bubbly flow (i.e. two-phase bubbly flow generated by jet stream impingement against the surface to be cooled 12) that was not diverted. Mixing of the single-phase liquid coolant with the two-phase bubbly flow can result in condensation and collapse of vapor bubbles 275 within the mixed flow 50, thereby reducing the void fraction of the coolant 50 flow delivered to the reservoir 200 and, in turn, reducing the likelihood of vapor bubbles being delivered to the pump 20.
In some examples, as shown in FIG. 12E, the internal bypass 65 in the heat sink module can include a pressure regulator 60. The pressure regulator 60 can be disposed at least partially within the internal bypass 65 and can serve to restrict flow through the internal bypass 65, thereby controlling the proportion of coolant flow through the internal bypass, and as a result, the proportion of coolant flow through the plurality of orifices 155 along a standard flow path 66 through the heat sink module. The internal pressure regulator 60 can be an active or passive regulator. In some examples, the pressure regulator can be a thermostatic valve that increases flow through the internal bypass 65 as the temperature of the coolant increases or decreases. In other examples, the pressure regulator 60 can be computer controlled pressure regulator where flow is adjusted based on a temperature and/or a pressure of the coolant upstream or downstream of the heat sink module 100. In other examples, the pressure regulator 60 can be a simple flow constriction (e.g. a physical neck) in the internal bypass that effectively restricts flow by providing flow resistance.
Cooling Assembly
FIG. 7 shows a cooling assembly including a heat sink module 100 fluidly connected to two sections of flexible tubing 225. The heat sink module 100 has an inlet port 105 and an outlet port 110. One end of the first section of flexible tubing 225 is fluidly connected to the inlet port 105 by a first connector 120, and one end of the second section of flexible tubing 225 is fluidly connected to the outlet port 110 by a second connector 120. In some examples, the connectors 120 can be liquid-tight fittings, such as compression fittings. The cooling assembly can be used to cool any heat generating surface associated with a device, such as an electrical or mechanical device.
Series-Connected Heat Sink Modules
FIG. 14 shows a schematic of a cooling apparatus 1 having three heat sink modules 100 arranged in a series configuration on three surfaces to be cooled 12. As shown by way of example in FIG. 15, the three heat sink modules 100 can be fluidly connected with tubing, such as flexible tubing 225. The three surfaces to be cooled 12 can be three separate surfaces to be cooled or can be three different locations on the same surface to be cooled 12.
FIG. 15 shows a portion of a primary cooling loop 300 of a cooling apparatus 1 where the cooling loop 300 includes three series-connected heat sink modules 100 mounted on three heat-providing surfaces 12 (see, e.g. FIG. 14). The heat sink module 100 can be connected by sections of flexible tubing 225. A single-phase liquid coolant 50 can be provided to a first heat sink module 100 by a section of tubing 225-0, and due to heat transfer occurring within the first heat sink module 100-1 (i.e. heat being transferred from the first heat-generating surface 12 to the flow of coolant), two-phase bubbly flow can be generated and transported in a first section of flexible tubing 225-1 extending from the first heat sink module 100-1 to the second heat sink module 100-2. The two-phase bubbly flow contains a plurality of bubbles 275 having a first number density. Due to heat transfer occurring within the second heat sink module 100-2 (i.e. heat being transferred from the second heat-generating surface 12 to the flow of coolant), higher quality (x) two-phase bubbly flow can be generated and transported from the second module 100-2 to the third heat sink module 100-3 through a second section of flexible tubing 225-2. In the second section of flexible tubing 225, the two-phase bubbly flow contains a plurality of bubbles 275 having a second number density, where the second number density is higher than the first number density. Due to heat transfer occurring within the third heat sink module 100 (i.e. heat being transferred from the third heat-generating surface 12 to the flow of coolant), even higher quality (x) two-phase bubbly flow can be generated and transported out of the third heat sink module 100-3 through a third section of tubing 225-3. In the third section of tubing 225-3, the two-phase bubbly flow contains a plurality of bubbles 275 having a third number density, where the third number density is higher than the second number density.
Parallel-Connected Heat Sink Modules
FIG. 16 shows a schematic of a cooling apparatus 1 having a primary cooling loop 300 that includes three parallel cooling lines where each parallel cooling line includes three heat sink modules 100 fluidly connected in series. The cooling apparatus shown in FIG. 16 can be configured to cool nine independent heat-generating surfaces 12, such as nine microprocessors 415. Other variations of the cooling apparatus 1 shown in FIG. 16 can include more than three parallel cooling lines, and each cooling line can include more than three series-connected modules 100.
As shown in the schematic of FIG. 16, additional heat sink modules 100 can be added to the cooling apparatus 1 in parallel cooling loops 300 that they are serviced by, for example, the same pump 20, reservoir 200, and heat exchanger 40. Alternatively, as shown in FIG. 17, the cooling apparatus 1 can include additional reservoirs 200, pumps 20, and/or heat exchangers 40 in parallel for the purpose of redundancy and reliability. As used herein, an additional component “in parallel” refers to a component in fluid communication with the other components in a manner that bypasses only components of the same type without bypassing different types of components. An example of an additional component added in parallel is shown with the additional heat sink modules 100 in FIG. 16, where three parallel cooling loops 300 are provided that each are serviced by the same reservoir 200 and pump 20.
Single Heat Sink Module for Multiple Heat Sources
To reduce installation costs, it can be desirable to cool more than one heat source 12 using a single heat sink module 100. Example installations are shown in FIGS. 66 and 67. FIG. 66 shows an example of an existing server 400 with a heat sink module retrofitted thereon. The server 400 includes a motherboard 405, two microprocessors 415 mounted on the motherboard, and a finned heat sink 440 mounted on each microprocessor 415. Rather than spend time and effort removing the finned heat sink modules 440 already installed on the microprocessors 415, instead, a thermally conductive base member 430 can be placed in thermal contact with both finned heat sinks 440, as shown in FIG. 66. The thermally conductive base member 430 can extend from a first finned heat sink 440 to a second finned heat sink 440. A heat sink module 100 can be mounted on a surface 12 of the thermally conductive base member 430. By directing a plurality of jet streams 16 of coolant at the surface to be cooled 12 of the thermally conductive base member 430, the configuration shown in FIG. 66 can cool two microprocessors simultaneously at a lower cost than installing two heat sink modules and without having to uninstall any factory-installed components of the server (e.g. the finned heat sinks 440). By not uninstalling factory-installed hardware, this cooling method can avoid potentially voiding a factory warranty on the server 400 or computer.
FIG. 67 shows an arrangement where a thermally conductive base member 430 extends from a first microprocessor 415 to a second microprocessor 415 mounted on a motherboard 405. A heat sink module 100 can be mounted on a surface 12 of the thermally conductive base member 430. By directing a plurality of jet streams 16 of coolant at the surface to be cooled 12 of the thermally conductive base member 430, the configuration shown in FIG. 67 can cool two microprocessors 415 simultaneously at a lower cost than using two heat sink modules. To ensure even cooling of each microprocessor, it can be desirable for the thermally conductive base member 430 to make contact with an entire, or substantially the entire, top surface of each microprocessor, as shown in FIG. 67.
Surface to be Cooled
The surface to be cooled 12 can be exposed within the outlet chamber 150 of the heat sink module 100, such that the jet streams 16 of coolant 50 impinge directly on the surface to be cooled 12 without thermal interference materials disposed between the surface 12 and the coolant 50. As used herein, “surface to be cooled” refers to any electronic or other device having a surface that generates heat and requires cooling. Non-limiting, exemplary surfaces to be cooled 12 include microprocessors 415, microelectronic circuit chips in supercomputers, power electronics, mechanical components, process containers, or any electronic circuits or devices requiring cooling, such as diode laser packages. The surface to be cooled 12 can be exposed within the outlet chamber 150 of the heat sink module 100 by constructing the outlet chamber to include the surface 12 within the chamber 150 or by constructing the outlet chamber such that the surface to be cooled 12 serves as a bounding wall of the outlet chamber 150, as shown in FIG. 26. In some examples, the heat sink module 100 can form an enclosure, such as a sealed liquid-tight enclosure, against the surface to be cooled 12 using one or more sealing members (e.g. o-rings, gaskets, or adhesives).
In some examples of the cooling apparatus 1, coolant 50 can be delivered to a heat sink module 100 that is mounted directly on a surface to be cooled, such as a surface of a microprocessor 415 that is electrically connected to a motherboard 405, as shown in FIG. 27. In other examples, the heat sink module 100 can be mounted on a thermally conductive intermediary object, such as a thermally conductive base member 430, as shown in FIG. 26. The assembly of the heat sink module 100 and the thermally conductive base member 430 can then be mounted on a heat source, such as a microprocessor 415 electrically connected to a motherboard 405, as show in FIG. 28. A layer of thermal interface material (e.g. solder thermal interface material or polymer thermal interface material) can be applied between a top surface of the heat source (e.g. microprocessor) and a bottom surface of the thermally conductive base member 430. The thermally conductive base member 430 can be made of a material with a high thermal conductivity, such as copper, silver, gold, aluminum, or tungsten.
The thermally conductive member 430 can be placed in thermal communication with an electronic device, or other type of device, that has a surface 12 that generates heat and requires cooling, such as a microprocessor 415, microelectronic circuit chip in a supercomputer, or any other electronic circuit or device requiring cooling, such as diode laser packages.
Three-Phase Contact Line Length
FIG. 63 shows a top view of a heated surface 12 covered by coolant 50, where the coolant has regions of vapor coolant 56 and wetted regions of liquid coolant 57 in contact with the heated surface 12. The dark areas in FIG. 63 show the vapor coolant regions 56, and the light areas show the liquid coolant regions 57. A length of a three-phase contact line 58 is measured as a sum of all curves where liquid coolant 57, vapor coolant 56, and the solid heated surface 12 are in mutual contact on the heated surface 12. The three-phase contact line 58 length can be determined using suitable image processing techniques.
The heat transfer rate from the surface to be cooled 12 to the coolant 50 has been shown to strongly correlate with the length of the three-phase contact line 58 on the surface to be cooled 12. Consequently, increasing the length of the three-phase contact line 58 can be desirable when attempting to increase the heat transfer rate from the surface to be cooled. Increasing the heat transfer rate is desirable, since it increases the efficiency of the cooling apparatus 1 and allows higher heat flux surfaces to be cooled by the cooling apparatus.
By providing jet streams 16 of coolant that impinge the surface to be cooled 12 from a suitable jet height 18, the heat sink modules 100 described herein effectively increase the length of the three-phase contact line 58. Consequently, the heat sink modules 100 described herein provide much higher heat transfer rates than competing cooling systems. By selecting orifice 155 diameters, jet heights 18, coolant pressures, and orifice orientations from the ranges provided herein, the heat sink module 100 can provide jet streams 16 with sufficient momentum to disrupt vapor formation on the surface to be cooled 12, thereby increasing the length of the three-phase contact line 58 on the surface to be cooled 12 and thereby allowing higher heat fluxes to be effectively dissipated without reaching critical heat flux.
Redundant Cooling Apparatus
In some examples, it can be desirable to have a fully redundant cooling apparatus 1 where each heat-generating surface 12 is cooled by at least two completely independent cooling loops 300. In the event of failure of a first independent cooling loop 300, a second independent loop can be configured to provide sufficient cooling capacity to adequately cool the heat-generating surface 12 and thereby avoid any downtime or reduction in performance when the heat-generating surface 12 is, for example, a microprocessor 415 or other critical system component. In a fully redundant cooling apparatus 1, the heat-generating component 12 be adequately cooled by a first cooling apparatus (and can continue to operate normally) while repairs are made on a failed component within a second cooling apparatus of the redundant cooling apparatus 1.
FIG. 9 shows a front perspective view of a fully redundant cooling apparatus 1 installed on eight racks 410 of servers 400 in a data center 425. The redundant cooling apparatus 1 includes two independent primary cooling loops 300, each similar to the primary cooling loop described with respect to FIGS. 1-3. FIG. 10 shows a rear view of the redundant cooling apparatus 1 of FIG. 9. In FIGS. 9 and 10, the redundant cooling apparatus has an independent pump 20, an independent reservoir 200, and an independent heat exchanger 40 associated with each independent primary cooling loop 300. However, in some examples, the primary cooling loops 300 may be fluidly connected and may share a common reservoir 200 and/or a common heat exchanger 40. Such an arrangement may be needed where redundant cooling loops 300 are desired but where safety regulations restrict the volume of coolant that can be used in a confined space.
FIG. 18 shows a schematic of a redundant cooling apparatus 1 with a first primary cooling loop 300 that includes two parallel cooling lines where each parallel cooling line is fluidly connected to three redundant heat sink modules 700 arranged in series, and a second primary cooling loop 300 that includes two parallel cooling lines where each parallel cooling line is fluidly connected to the three redundant heat sink modules 700 arranged in series.
FIG. 19 shows a top view of a redundant cooling apparatus installed in a data center or computer room 425 having twenty racks 410 of servers 400. Each primary cooling loop 300 of the redundant cooling apparatus 1 can be fluidly connected to a heat exchanger 40 located inside of the room 425 where the servers are located. In some examples, the heat exchanger can dump heat into the room 425, and a CRAC can be used to remove the heat from the room.
FIG. 20 shows a top view of a redundant cooling apparatus installed in a data center or computer room 425 having twenty racks 410 of servers 400. Each primary cooling loop 300 of the redundant cooling apparatus can be fluidly connected to a heat exchanger 40 located outside of the room 425 where the servers are located. In some examples the heat exchanger 40 can be connected to a chilled water system of a building. In other examples, the heat exchanger 40 can be connected to an air conditioning unit located outside of the room 425 (e.g. outside of the building).
Redundant Heat Sink Module
FIG. 51A shows a top perspective view of a redundant heat sink module 700. FIG. 51B shows a top view of the redundant heat sink module of FIG. 51A, where a first independent flow path 701 and the second independent flow path 702 are represented by dashed lines. In the example shown in FIG. 51B, the first independent flow path 701 passes through a first region near a middle of the redundant heat sink module 700, and the second independent flow path 702 passes through a second region outside of the perimeter of the first region. The first and second independent flow paths (701, 702) can be completely independent, meaning that no amount (or no substantial amount) of coolant 51 transfers from the first independent flow path to the second independent flow path or vice versa. The first independent flow path can extend from a first inlet port 105-1 to a first outlet port 110-1. Similarly, a second independent flow path 702 can extend from a second inlet port 105-2 to a second outlet port 110-2.
The first independent flow path 701 can include a first inlet passage 165-1 extending from the first inlet port 105-1 to a first inlet chamber 145-1. A first plurality of orifices 155-1 can extend from the first inlet chamber 145-1 to a first outlet chamber 150-1 and can be configured to provide a plurality of jet streams 16 of coolant into the first outlet chamber 150-1 when pressurized coolant is provided to the first inlet chamber 145-1. A first outlet passage 166-1 can extend from the first outlet chamber 150-1 to the first outlet port 110-1. A first plurality of anti-pooling orifices 156-1 can extend from the first inlet chamber 145-1 to a location proximate a rear wall of the first outlet chamber 150-1 and can be configured to provide a plurality of jet streams 16 of coolant proximate a rear wall of the first outlet chamber 150-1 when pressurized coolant is provided to the first inlet chamber 145-1.
The second independent flow path 702 can include a second inlet passage 165-2 extending from the second inlet port 105-2 to a second inlet chamber 145-2. A second plurality of orifices 155-2 can extend from the second inlet chamber 145-2 to a second outlet chamber 150-2 and can be configured to provide a plurality of jet streams 16 of coolant into the second outlet chamber 150-2 when pressurized coolant is provided to the second inlet chamber 145-2. A second outlet passage 166-2 can extend from the second outlet chamber 150-2 to the second outlet port 110-2. A second plurality of anti-pooling orifices 156-2 can extend from the second inlet chamber 145-2 to a location proximate a wall of the second outlet chamber 150-2 and can be configured to provide a plurality of jet streams 16 of coolant proximate the wall of the second outlet chamber 150-2 when pressurized coolant is provided to the second inlet chamber 145-2.
FIG. 51D shows a bottom view of the redundant heat sink module 700 of FIG. 51A. The first independent flow path 701 includes an array of orifices 155 arranged in a first region located near a middle portion of the module 700. The second independent flow path 702 includes an array of orifices 155 arranged in a second region located beyond (e.g. outside of) the perimeter of the first region. In other examples, the first region can be located near a first half of the module 700 and the second region can be located near a second half of the module 700, as shown in the parallel path example of FIG. 53.
The first outlet chamber 150-1 of the redundant heat sink module 700 can have an open portion that can be enclosed by a surface to be cooled 12 when the redundant heat sink module 700 is installed on a surface to be cooled. Similarly, the second outlet chamber 150-2 of the redundant heat sink module 700 can have an open portion that can be enclosed by a surface to be cooled 12 when the redundant heat sink module 700 is installed on a surface to be cooled. To facilitate sealing against the surface to be cooled 12, the heat sink module can include a first sealing member 125-1 and a second sealing member 125-2, as shown in FIG. 51D. The first sealing member 125-1 (e.g. o-ring, gasket, sealant) can be disposed within a first channel 140-1 formed in a bottom surface 135 of the redundant heat sink module 700. The first channel 140-1 can circumscribe the first outlet chamber 150-1, and the first sealing member 125-1 can be compressed between the first channel 140-1 and the surface to be cooled 12 to provide a liquid-tight seal therebetween. The redundant heat sink module 700 can include a second sealing member 125-2, as shown in FIG. 51D. The second sealing member 125-2 (e.g. o-ring, gasket, sealant) can be disposed within a second channel 140-2 formed in the bottom surface 135 of the redundant heat sink module 700. The second channel 140-2 can circumscribe the second outlet chamber 150-2, and the second sealing member 125-2 can be compressed between the second channel 140-2 and the surface to be cooled 12 to provide a liquid-tight seal therebetween. In this example the first sealing member 125-1 can provide a liquid-tight seal between the first outlet chamber 150-1 and the second outlet chamber 150-2).
FIG. 51F shows a side cross-sectional view of the redundant heat sink module 700 of FIG. 51A taken along section A-A shown in FIG. 51E. FIG. 51G shows a side cross-section view of the redundant heat sink module 700 of FIG. 51A taken along section B-B shown in FIG. 51E. FIG. 51I shows a cross-sectional view of the redundant heat sink module 700 of FIG. 51A taken along section C-C shown in FIG. 51H. FIG. 51K shows a side cross-sectional view of the redundant heat sink module of FIG. 51A taken along section D-D shown in FIG. 51J. FIG. 51M shows a side cross-section view of the redundant heat sink module 700 of FIG. 51A taken along section E-E of FIG. 51L.
FIG. 17 shows a schematic of a redundant cooling apparatus 1 having a redundant heat sink module 700 mounted on a heat source 12. The redundant heat sink module 700 is connected to two independent primary cooling loops 300. In another example, the redundant heat sink module 700 can be replaced with two separate heat sink modules 100, where a first heat sink module 100 is connected to a first independent primary cooling loop 300, and a second heat sink module 100 is connected to a second independent primary cooling loop 300.
Portable Servicing Unit
A portable servicing unit can be provided to aid in draining the cooling apparatus 1, for example, when servicing or repairing the cooling apparatus. The portable servicing unit can include a vacuum pump. The portable servicing unit can include a hose, such as a flexible hose, having a first end a second end. A first end of the hose can be configured to fluidly connect to an inlet of the vacuum pump of the portable servicing unit. A second end of the hose can be configured to fluidly connect to a connection point (e.g. a drain 245) of the cooling apparatus 1 through, for example, a threaded fitting or a quick-connect fitting. The portable machine can include a portable reservoir fluidly connected to an outlet of the vacuum pump. When connected to the cooling apparatus 1 and activated, the vacuum pump of the portable servicing unit can apply vacuum pressure to the cooling apparatus 1 by way of the hose, which results in coolant flowing from the cooling apparatus, through the hose and vacuum pump, and into the portable reservoir. When servicing is complete, fluid from the portable reservoir can be pumped back into the cooling system or transported to an appropriate disposal or recycling facility. In some examples, the portable servicing unit can include one or more thermoelectric heaters. The thermoelectric heaters can be placed in thermal communication with components of the cooling apparatus 1, and by transferring heat to coolant within the apparatus, the thermoelectric heaters can promote evacuation of fluid from the apparatus through a drain 245 or other access point in the apparatus.
3-D Printing
One or more components of the cooling apparatus 1 can be manufactured by a three-dimensional printing process, also known as additive manufacturing. The heat sink module 100, or portions of the heat sink module, such as an insertable orifice plate 198, can be manufactured by a three-dimensional printing process. In some examples, a three-dimensional manufacturing process can be used to create tubing 225 used to fluidly connect a first heat sink module 100 to a second heat sink module, such as the section of tubing shown in FIG. 73. In some examples, a three-dimensional printing process can be used to form a combined heat sink module 100 and section of tubing 225. In some examples, a three-dimensional printing process can be used to form two heat sink modules 100 fluidly connected by a section of tubing 225, as shown in FIG. 73. This approach can eliminate potential leak points that would typically exist, for example, at threaded connections where fittings attach a section of tubing 225 to an inlet or outlet port (105, 110) of the heat sink modules. This approach can also reduce installation time and reduce risk of installation error.
In some examples, components of the cooling apparatus 1 can be formed by a stereolithography process that involves forming layers of material curable in response to synergistic stimulation adjacent to previously formed layers of material and successively curing the layers of material by exposing the layers of material to a pattern of synergistic stimulation corresponding to successive cross-sections of the heat sink module. The material curable in response to synergistic stimulation can be a liquid photopolymer.
Coolant Temperature, Pressure, and Flow Rate
In some examples, it can be desirable to maintain coolant surrounding a surface to be cooled 12 at a pressure that results in the saturation temperature of the coolant being slightly above the temperature of jet streams of coolant being projected at the surface to be cooled 12. As used herein, “maintain” can mean holding at a relatively constant value over a period of time. “Coolant surrounding a surface” refers to a steady state volume of coolant immediately surrounding and in contact with the surface to be cooled 12, excluding jet streams 16 of coolant projected directly at the surface to be cooled 12. “Saturation temperature” is used herein as is it is commonly used in the art. The saturation temperature is the temperature for a given pressure at which a liquid is in equilibrium with its vapor phase. If the pressure in a system remains constant (i.e. isobaric), a liquid at saturation temperature evaporates into its vapor phase as additional thermal energy (i.e. heat) is applied. Similarly, if the pressure in a system remains constant, a vapor at saturation temperature condenses into its liquid phase as thermal energy is removed. The saturation temperature can be increased by increasing the pressure in the system. Conversely, the saturation temperature can be lowered by decreasing the pressure in the system. In specific versions of the invention, a saturation temperature “slightly above” the temperature of jet streams 16 of coolant projected at the surface to be cooled 12 refers to a saturation temperature of about 0.5° C., about 1° C., about 3° C., about 5° C., about 7° C., about 10° C., about 15° C., about 20° C., or about 30° C. above the temperature of coolant 50 projected against the surface. Establishing a saturation temperature of coolant 50 surrounding a surface 12 slightly above the temperature of the jet stream 16 of coolant projected at the surface provides for at least a portion of the coolant projected at the surface to heat and evaporate after contacting the surface, thereby greatly increasing the heat transfer rate and efficiency of the cooling apparatus 1.
The appropriate pressure at which to maintain the coolant to achieve the preferred saturation temperatures can be determined theoretically by rearranging the following Clausius-Clapeyron equation to solve for P0:




  
    T
    B
  
  =
  
    
      (
      
        
          
            R
            ⁢
            
              
            
            ⁢
            
              ln
              ⁡
              
                (
                
                  P
                  0
                
                )
              
            
          
          
            Δ
            ⁢
            
              
            
            ⁢
            
              H
              vaporization
            
          
        
        +
        
          1
          
            T
            0
          
        
      
      )
    
    
      -
      1
    
  




where: TB=normal boiling point (K), R=ideal gas constant (J-K−1mol−1), P0=vapor pressure at a given temperature (atm), ΔHvaporization=heat of vaporization of the coolant (J/mol), T0=given temperature (K), and ln=natural log to the base e.

In the above equation, the given temperature (T0) is the temperature of coolant 50 in contact with, and heated by, the surface to be cooled 12. The normal boiling point (TB) is the boiling point of the coolant at a pressure of one (1) atmosphere. The heat of vaporization (ΔHvap) is the amount of energy required to convert or vaporize a given quantity of a saturated liquid (i.e., a liquid at its boiling point) into a vapor. As an alternative to determining the appropriate pressure theoretically, the appropriate pressure can be determined empirically by adjusting the pressure and detecting evaporation or bubble generation at a surface to be cooled 12, as shown in FIG. 30. Bubble generation can be visually detected with a human eye when transparent components, such as a transparent heat sink module 100 or transparent flexible tubing 225, is used to construct the cooling apparatus 1. In some examples, the heat sink module 100 or the flexible tubing 225 can be transparent throughout, and in other examples, at least a portion of the heat sink module 100 or flexible tubing 225 can be transparent to provide a transparent window portion that permits a system operator or electronic eye to visually detect the presence of bubbles 275 within the coolant 50 flow and to make system adjustments based on that visual detection. For instance, if no bubbles 275 are visually detected exiting the outlet chamber 150 of the heat sink module 100, the coolant flow rate can be reduced by reducing the pump 20 speed, thereby reducing energy consumed by the pump 20 and reducing overall energy consumption and operating cost. Conversely, if slug or churn flow is detected (see, e.g. FIGS. 58 and 59B), the coolant flow rate 51 can be increased to eliminate the presence of those unwanted flow regimes and restore the system to two-phase bubbly flow.
During operation of the cooling apparatus 1, coolant 50 can be flowed into an outlet chamber 150 of the heat sink module 100. The surface to be cooled 12 can be exposed within the outlet chamber 150 or, as shown in FIG. 30, the surface to be cooled 12 can serve as a bounding surface of the outlet chamber 150 when the heat sink module 100 is installed on the surface to be cooled 12. The coolant 50 can be introduced to the outlet chamber 150 at a predetermined pressure that promotes a phase change upon the liquid coolant 50 contacting, and being heated by, the surface to be cooled 12. One example of such a cooling apparatus 1 for performing various cooling methods described herein is shown in FIG. 11A. The cooling apparatus 1 can include a heat sink module 100, as shown in FIGS. 26 and 30. The heat sink module 100 can include an outlet chamber 150 with a surface 12 to be cooled exposed within the outlet chamber 150. The pump 20, as shown in FIG. 11A, can provide coolant 50 at a predetermined pressure to an inlet 21 of the heat sink module 100.
The cooling apparatus 1 as described above and as shown in FIG. 11A can include several steady-state zones comprising either liquid flow or two-phase bubbly flow. The nature of the coolant 50 in each zone can depend on the temperature and pressure of the coolant in each zone. In the example in FIG. 11A, a zone comprising high-temperature coolant 52 includes the coolant 50 surrounding the surface to be cooled 12 within the outlet chamber 150 (excluding the jet streams 16 of coolant 50 projected into the outlet chamber 150 through the orifices 155 of the heat sink module 100) of the heat sink module 100 and extends downstream to the heat exchanger 40 (see FIG. 11A for direction of flow 51). Portions of the high-temperature coolant 52 within the outlet chamber 150 are preferably at a temperature approximately equal to or above the saturation temperature. A zone of low-temperature coolant 53 extends from downstream of the reservoir 200 to at least the inlet port 105 of the first heat sink module 100 and includes the jet streams 16 of coolant 50 injected into the outlet chamber 150 of the first heat sink module 100. The low-temperature coolant 53 is preferably at a temperature slightly below the saturation temperature of the coolant 50 surrounding the surface 12, wherein “slightly below” can include 0.5-1, 0.5-3, 1-3, 1-5, 3-7, 5-10, 7-10, 7-15, 10-15, 15-20, 15-30, about 0.5, about 1, about 3, about 5, about 7, about 10, about 15, about 20, or about 30° C. or more below the saturation temperature of coolant 50 surrounding the surface to be cooled 12. Heat transfer from the surface to be cooled 12 to the coolant 50 with the outlet chamber 150 of the heat sink module 100 serves to transition the low-temperature coolant 53 to high-temperature coolant 52. In some examples, the surface to be cooled 12 heats a portion of the coolant 50 contacting the surface 12 to its saturation temperature, thereby promoting evaporation and formation of two-phase bubbly flow, which exits the heat sink module through the outlet port 110.
A zone of low-pressure coolant 55 includes the coolant 50 surrounding the surface to be cooled 12 within the outlet chamber 150 (which excludes the jet streams 16 of coolant 50 projecting into the outlet chamber 150 through the orifices 155 of the heat sink module) and extends downstream to an inlet 21 of the pump 20. The low-pressure coolant 55 is preferably at a pressure that promotes evaporation of coolant 50 when heated at the surface 12. Therefore, the pressure of the low-pressure coolant 55 preferably determines a saturation temperature to be about equal to the temperature of the high-temperature coolant 52. A zone of high-pressure coolant 54 includes a portion downstream of the pump outlet 22 and extends to at least the inlet port 105 of the first heat sink module 100. The high-pressure coolant 54 is preferably at a pressure suitable for generating jet streams 16 of coolant that are capable of penetrating liquid present in the outlet chamber 150 and impinging the surface to be cooled 12. In some examples, the pump 20 can provide high-pressure coolant 54 at a pressure of about 1-20, 10-30, 25-50, 40-60, or 50-75, 60-80, or 75-100 psi. In other examples, the pump 20 can provide high-pressure coolant 54 at a pressure of about 85-120, 100-140, 130-160, 150-175, 160-185, 175-200, or greater than 200 psi.
The pump 20 serves to transition low-pressure coolant 55 to high-pressure coolant 54 as the coolant passes from the pump inlet 21 to the pump outlet 22. In some examples, the pump 20 can provide high-pressure coolant 54 at a pressure that is about 10-20, 15-30, 20-40, 30-45, or 40-60 psi or greater above the pressure of the low-pressure coolant 55. The high-pressure coolant 54 in the cooling apparatus 1 applies a positive pressure against the plurality of orifices 155 in the heat sink module 100, and the plurality of orifices 155 serve to transition the high-pressure coolant 54 to low-pressure coolant 55, as the coolant 50 equilibrates to the pressure of the low-pressure coolant 55 after passing through the plurality of orifices as jet streams 16 and mixing with the coolant in the outlet chamber 150 of the heat sink module 100.
With the apparatus 1 described above, a flow rate is set by the pump 20 to handle the expected heat load produced by the surface to be cooled 12. A specific pressure for the low-pressure coolant 55 is set and maintained by one or more pumps 20 and by one or more pressure regulators 60, as shown in the various schematics presented in FIGS. 11A-14, 16-18, and 68-72 to establish a saturation temperature for the coolant 50 surrounding the surface to be cooled 12 to be slightly above the saturation temperature of the low-temperature coolant 53. Relatively high-pressure 54 low-temperature 53 coolant 50 is projected as jet streams 16 from the plurality of orifices 155 against the surface to be cooled 12, whereby the coolant 50 undergoes a pressure drop upon equilibrating with fluid present in the outlet chamber 150 and a portion of the fluid may heat to its saturation temperature upon contacting the surface 12 and absorbing heat from the surface. A portion of the heated coolant 50 undergoes a phase transition at the surface to be cooled 12, which causes highly efficient cooling of the surface 12. Downstream of the heat sink module 100, the relatively low-pressure 55, high-temperature 52 coolant flow is then mixed with low-pressure 55, low-temperature 54 coolant from the second bypass 310 to promote condensing of vapor bubbles 275 within the low-pressure 55, high temperature 52 coolant by cooling it below its saturation temperature, which produces a flow of low-pressure 55, low-temperature 53 coolant in the return line 230 that returns the coolant 50 to the reservoir 200. Upon being drawn form the lower portion of the reservoir 200 to the pump inlet 21, the low-pressure 55, low-temperature 53 coolant is then transitioned to high-pressure 54, low-temperature 53 coolant as it passes through the pump 20. The high-pressure 54, low-temperature 53 coolant is then circulated back to the inlet port 105 of the first heat sink module 100 and the above-described process is repeated.
Cooling System Preparation and Operation
In some applications, it can be desirable to fill the cooling apparatus 1 with a dielectric coolant 50 that is at a pressure below atmospheric pressure (e.g. less than about 14.7 psi). For example, when cooling microprocessors 415, it can be desirable fill the cooling apparatus 1 with HFE-7000 (or a coolant mixture containing HFE-7000 and, for example, R-245fa) that is at a pressure below atmospheric pressure to reduce the boiling point of the dielectric fluid. To accomplish this, the portable servicing unit (or other vacuum source) can be used to apply a vacuum to the cooling apparatus 1 to purge the contents of the cooling apparatus. Upon reducing the pressure within the cooling apparatus 1 to about 0-3, 0-5, 1-5, 4-8, 5-10, or 8-14.5 psi, the dielectric coolant 50 can be added to the cooling apparatus 1. In some examples, operation of the pump 20 may only increase the pressure of the dielectric coolant about 1-15, 5-20, or 10-25 psi above the baseline sub-atmospheric pressure. Consequently, the operating pressure of the high pressure coolant 54 within the cooling apparatus 1 may be about equal to atmospheric pressure (e.g. about 8-14, 10-16, 12-18, or 14-20 psi), thereby ensuring that that saturation temperature of the dielectric coolant remains low enough to ensure that boiling can be achieved when jet streams 16 of coolant impinge the surface to be cooled 12 associated with a microprocessor 415. Providing high-pressure coolant 54 at a pressure near atmospheric pressure has other added benefits. First, low pressure tubing 225 can be used, which is lightweight, flexible, and low cost. Second, because of the minimal pressure difference between the high-pressure coolant 54 and the surrounding atmosphere, fluid leakage from fittings and other joints of the cooling apparatus 1 may be less likely.
Heat Exchanger
The cooling apparatus 1 can include a heat exchanger 40 in fluid communication with the bypass 305. In some examples, the heat exchanger 40 can be upstream of the pressure regulator 60 in the bypass 305, and in other examples, the heat exchanger 40 can be downstream of the pressure regulator 60 in the bypass 305. “Downstream” and “upstream” are used herein in relation to the direction of flow 51 of coolant 50 within the cooling apparatus 1. Any heat exchanger 40 capable of reducing the temperature of the coolant 50 to below its saturation temperature is acceptable. Non-limiting examples include shell-and-tube, plate, adiabatic-wheel, plate-fin, pillow-plate, fluid, dynamic-scraped-surface, phase-change, direct contact, and spiral heat exchangers. The heat exchanger 40 can operate by parallel flow or counter flow. An air-to-liquid heat exchanger 40 can be a fin-and-tube type, a micro-channel type, or any other suitable air-to-liquid type of heat exchanger.
In some examples, the heat exchanger 40 can be an air-to-liquid heat exchanger having a fan 26 mounted thereon to increase the rate of heat transfer between the working fluids (i.e. between the coolant 50 and the ambient air), as shown in FIGS. 12P, 12Q, and 19. In some examples, it may be desirable to place the heat exchanger 40 on a roof of a building. In other examples, the heat exchanger 40 can be a liquid-to-liquid heat exchanger and can be connected to an external cooling fluid (such as chilled water from a building supply line, as shown in FIG. 20). More specifically, the heat exchanger 40 can be connected to a chilled water supply line of a building, which allows heat rejected from the cooling apparatus 1 to be removed from the room 425 where the cooling apparatus 1 is installed instead of being rejected to the room air, where it could result in an increase in the room air temperature.
The flow rate of coolant 50 through the heat exchanger 40 can be monitored and controlled to avoid reducing the temperature of the low-temperature 53 coolant to or below the dew point of ambient air in the room 425 where the surface to be cooled 12 is located. Reaching the dew point is undesirable, since it can cause condensation to form on an outer surface of the flexible tubing 225 or other components of the apparatus 1. If this occurs, water droplets can form on and fall from the outer surface of the tubing 225 onto sensitive electrical components within the server 400, such as the microprocessor 415 or memory modules 420, which is undesirable. Consequently, the low-temperature 53 coolant should be maintained at a temperature above the dew point of ambient air in the room 425 to ensure that condensation will not form on any components of the cooling apparatus 1 that are in close proximity to sensitive electrical devices being cooled.
In some examples, if the low-temperature 53 coolant is cooled below the dew point of ambient air in the room by the heat exchanger 40, a preheater can be provided in line with, or upstream of, the line (e.g. flexible tubing 225) that transports coolant 50 flow into the server 400 housing and into the heat sink module 100. The preheater can be used to heat the coolant flow to bring the coolant temperature above its dew point temperature, thereby avoiding potential complications caused by condensation forming on the lines within the server housing. In some examples, the preheater can be configured to operate only when needed, such as when the temperature of the low-temperature coolant drops below its dew point.
The temperature of the low-temperature coolant 52 can be monitored with one or more temperature sensors positioned in the cooling lines, and data from the sensors can be input to the controller. For instance, a first temperature sensor can be positioned upstream of the preheater, and a second temperature sensor can be positioned downstream of the preheater. When the first temperature sensor detects a coolant temperature that is below the dew point of ambient air in the room 425, the controller can be configured to activate the preheater to heat the low-temperature coolant 52 to bring the temperature of the low-temperature coolant above the dew point of the ambient air in the room 425. In some examples, the rate of heat addition can be ramped up gradually, and once the temperature detected by the second temperature sensor is above the dew point of the ambient air, the controller can be configured to stop ramping the rate of heat addition and instead hold the heat addition constant. The controller can continue instructing the preheater to heat the low-temperature coolant 52 until preheating is no longer needed. For instance, the controller can continue instructing the preheater to heat the low-temperature coolant 52 until the temperature detected by the first temperature sensor is above the dew point of the ambient air.
Although the preheating process described above includes measuring the temperature of the low-temperature coolant 52 directly, in other examples the surface temperature of the outer surface of the tubing (e.g. 225) can be measured instead of measuring the coolant temperature directly. For instance, temperature sensors can be affixed directly to the outer surface of the tubing (e.g. 225) upstream and downstream of the preheater. In some instances, this approach can permit faster installation of the temperature sensors and can reduce the number of potential leak points in the cooling apparatus 1. In other examples, a contactless temperature-sensing device, such as an infrared temperature sensor, can be used to detect the temperature of the coolant or the temperature of the tubing 225 transporting the coolant.
To ensure the temperature of the low temperature coolant 52 remains above the dew point temperature of the ambient air, the flow rate through the heat exchanger 40 can be decreased and/or the fan speed of a fan 26 mounted on the heat exchanger 40 can be reduced to lower the heat rejection rate from the heat exchanger 40 if a low temperature threshold is detected in the low-temperature coolant. This step can be taken instead of, or in conjunction with, using the preheater to avoid dew formation on any components of the cooling apparatus 1.
Electronic Control System
The cooling apparatus 1 can include an electronic control system 850, as shown in FIG. 12Q, to enhance performance and reduce power consumption of the cooling apparatus 1. In some examples, the electronic control system 850 can include a microcontroller. The microcontroller can be electrically connected to one or more system components, such as a heat exchanger fan 26, a pressure regulator 60, a shut-off valve, or a pump 20, and can be configured to dynamically adjust settings of the one or more components within the cooling apparatus 1 during operation of the cooing apparatus to enhance performance and/or reduce overall power consumption. In one example, the microcontroller can be electrically connected to a variable speed drive for the pump 20, as described in U.S. Patent Publication No. 2006/0196627 to Shedd et al., which is hereby incorporated by reference in its entirety. The microcontroller and the variable speed drive can allow the pump 20 to operate at a lower power when the thermal load decreases. For instance, the operating pressure at the pump outlet 22 can be decreased when the thermal load falls, thereby decreasing the flow rate through the cooling apparatus 1 and the heat sink modules 100 fluidly connected thereto. The ability to operate the variable speed drive at a lower power conserves energy, and is therefore desirable. Where the cooling apparatus 1 includes independent redundant cooling loops, the electronic control system 850 can be configured to operate a first cooling loop while a second cooling loop is on standby. In some examples, the electronic control system 850 can be configured to activate the second cooling loop only if the first cooling loop experiences a malfunction or is otherwise unable to effectively cool the surface to be cooled 12. In this way, the redundant cooling apparatus 1 can reduce power consumption by about 50% compared to a redundant cooling apparatus where both cooling loops operate continuously.
When a redundant cooling apparatus is provided, the apparatus may run for long periods of time (e.g. years) without experiencing any malfunctions or component failures. Consequently, during these long periods of time, only one cooling loop will be needed and the other cooling loop will remain on standby. To ensure that each cooling loop remains functional and ready to operate when needed, the electronic control system 850 can alternate between operating the first cooling loop and the second cooling loop when only one cooling loop is needed. For instance, the control system can be configured to activate the first cooling loop for a certain period of time (e.g a number of hours or days) while the second cooling loop remains on standby. Once the certain period of time has passed, the electronic control system 850 can then activate the second cooling loop, and once the second cooling loop is operating as desired, can place the first cooling loop on standby. Cycling between operating the first cooling loop and operating the second cooling loop can extend the life of certain system components within each loop (e.g. pump seals) and can increase the likelihood that the standby loop is ready for operation if the other cooling loop experiences a malfunction. Cycling between the first and second cooling loops can also ensure that operating time is equally distributed between the two cooling loops, thereby potentially increasing the overall useful life of the redundant cooling apparatus 1.
The cooling apparatus 1 can include one or more sensors that deliver data to the electronic control system 850 to allow a malfunction within the cooling apparatus 1 to be detected and communicated to an operator. The cooling apparatus can include one or more temperature sensors, pressure sensors, visual flow sensors, flow quality sensors, vibration sensors, smoke detectors, fluorocarbon detectors, or leak detectors that deliver data to the electronic control system 850. Each sensor can be electrically connected or wirelessly connected to the electronic control system 850. Upon detection of a malfunction within the cooling apparatus 1, the electronic control system 850 can be configured to notify a system operator, for example, with a visual or audible alarm. The electronic control system 850 can be configured to send an electronic message (e.g. an email or text message) to a system operator to alert the operator of the malfunction. The electronic message can include specific details associated with the malfunction, including data recorded from the one or more sensors connected to the electronic control system 850. The electronic message can also include a part number associated with the component that has likely failed to permit the operator to immediately determine if the part exists in local inventory, and if not, to order a replacement part from a vendor as soon as possible. The electronic message, and any data relating to the malfunction, can be stored in a computer readable medium and/or transmitted to the system manufacturer for quality control, warranty, and/or recall purposes.
Cooling Apparatus with Rooftop Dry Cooler
FIG. 12P shows a schematic of a cooling apparatus 1 having a primary cooling loop 300, a first bypass 305, and a second bypass 310, where the first bypass 305 is connected to a heat exchanger 40 that can be a rooftop dry cooler. The cooling apparatus 1 can include an electronic control system 850 having a microcontroller that receives inputs from sensors regarding flow rate, pressure, and temperature and determines heat removed (W), rate of heat removed (kW-h over time), and pump 20 power consumption. The cooling apparatus 1 can include two pumps 20 arranged in a parallel configuration for redundancy. Shut-off valves 250 can be provided near each pump inlet 21 and outlet 22, thereby allowing for hot-swapping of a failed pump 20. The shut-off valves 250 can be electronically controlled by the electronic control system 850 or manually controlled, depending on the complexity of the cooling apparatus 1. Where the shut-off valves 250 are electronically controlled, a motor fail-safe 855 (see, e.g. FIG. 12P) can be provided to monitor the status of the pumps 20, and in case of pump failure, can deactivate the failed pump and activate the non-failed pump to ensure continued flow of coolant through the primary cooling loop 300 to the surface to be cooled 12. In some examples, the cooling apparatus 1 can include a strainer 260 downstream of the pumps 20 and a filter 260 upstream of the pumps 20. In some examples, the pressure regulator 60 located between the heat exchanger 40 and the reservoir 200 can be a back pressure valve, such as a liquid relief valve manufactured by Kunkle Valve and available from Pentair, Ltd. of Minneapolis, Minn. In some examples, the pressure regulator 60 positioned in the first bypass 305 can be a back pressure valve, such as a liquid relief valve manufactured by Cash Valve, also available from Pentair, Ltd.
Portable Cooling Device
FIG. 74 shows a portable cooling device 750 that includes a plurality of heat sink modules 100 mounted on a portable layer 755. In some examples, the portable layer 755 can be a rigid material, such as metal, carbon fiber composite, or plastic. In other examples, the portable layer 755 can be a conformable material, such as fabric, foam, or an insulating blanket. The portable layer 755 can be contoured to correspond to any heated surface 12. The plurality of heat sink modules (100, 700) can be attached to the portable layer 755 by any suitable method of adhesion. The heat sink modules (100, 700) can be fluidly connected in series and/or parallel configurations. The portable cooling device 750 can include one or more inlet connections 236 and one or more outlet connections 237 that can be connected to a cooling apparatus 1 that delivers a flow of pressurized coolant 50 to the portable cooling device 750 to permit cooling of the heated surface 12 through sensible and latent heating of the coolant within the plurality of heat sink modules. In some examples, each heat sink module can be mounted on a thermally conductive base member 430. Where the portable layer 755 is made from an insulated blanket or other insulating member, the portable cooling device 750 can be wrapped around a vessel to cool the vessel and its contents. In this example, the portable layer 755 can include suitable fastening devices (e.g. snaps, ties, zippers, Velcro, or magnets) to allow the portable cooling device to be removably attached to the vessel.
Heat Sink Module Examples
In one example, a heat sink module 100 for cooling a heat providing surface 12 can include an inlet chamber formed 145 within the heat sink module and an outlet chamber 150 formed within the heat sink module. The outlet chamber 150 can have an open portion, such as an open surface. The open portion can be enclosed by the heat providing surface 12 to form a sealed chamber when the heat sink module 100 is installed on the heat providing surface 12, as shown in FIG. 26. The heat sink module 100 can include a dividing member 195 disposed between the inlet chamber 145 and the outlet chamber 150. The dividing member 195 can include a first plurality of orifices 155 formed in the dividing member. The first plurality of orifices 155 can extend from a top surface of the dividing member 195 to a bottom surface of the dividing member 195. The first plurality of orifices 155 can be configured to deliver a plurality of jet streams 16 of coolant 50 into the outlet chamber 150 and against the heat providing surface 12 when the heat sink module 100 is installed on the heat providing surface 12 and when pressurized coolant 50 is delivered to the inlet chamber 145.
A distance between the bottom surface of the dividing member 195 and the heat providing surface 12 can define a jet height 18 of the plurality of orifices 155 when the heat sink module 100 is installed on the heat providing surface 12. The jet height 18 can be about 0.01-0.75, 0.05-0.5, 0.05-0.25, 0.020-0.25, 0.03-0.125, or 0.04-0.08 in.
The first plurality of orifices 155 can have an average diameter of about 0.001-0.020, 0.001-0.2, 0.001-0.150, 0.001-0.120, 0.001-0.005, or 0.030-0.050 in. The first plurality of orifices 155 can have an average diameter of D and an average length of L, and L divided by D can be greater than or equal to one or about 1-10, 1-8, 1-6, 1-4, or 1-3.
The dividing member can have a thickness of about 0.005-0.25, 0.020-0.1, 0.025-0.08, 0.025-0.075, 0.040-0.070, 0.1-0.25, or 0.040-0.070 in. Each orifice of the first plurality of orifices 155 can have a central axis, and the central axes of the first plurality of orifices 155 can be arranged at an angle of about 20-80, 30-60, 40-50, or 45 degrees with respect to the surface to be cooled 12.
The first plurality of orifices 155 can be arranged in an array 76, and the array can be organized into staggered columns 77 and staggered rows 78, as shown in FIG. 31, such that a given orifice 155 in a given column 77 and a given row 78 does not have a corresponding orifice 155 in a neighboring row 78 in the given column 77 or a corresponding orifice in a neighboring column 77 in the given row 78.
The heat sink module 100 can include a second plurality of orifices 156 extending from the inlet chamber 145 to a rear wall of the outlet chamber 150, as shown in FIG. 38. The second plurality of orifices 156 can be configured to deliver a plurality of anti-pooling jet streams of coolant 16 to a rear portion of the outlet chamber 150 when pressurized coolant is provided to the inlet chamber 145. Each orifice of the second plurality of orifices comprises a central axis, wherein the central axes of the second plurality of orifices are arranged at an angle of about 40-80, 50-70, or 60 degrees with respect to the surface to be cooled. The second plurality of orifices 156 can be arranged in a column along the rear wall of the outlet chamber 150.
The heat sink module 100 can include one or more boiling-inducing members 196 extending from the bottom side of the dividing member 195 toward the heat providing surface, wherein the one or more boiling-inducing members 196 are slender members extending from the bottom surface of the dividing member 195. In one example, the one or more boiling-inducing members 196 can be configured to contact the heat providing surface 12. In another example, the one or more boiling-inducing members 196 can be configured to extend toward the heat providing surface 12, but not contact the heat providing surface 12. Instead, a clearance distance can be provided between the ends of the one or more boiling-inducing members 196 and heat providing surface. The clearance distance can be about 0.001-0.0125, 0.001-0.05, 0.001-0.02, 0.001-0.01, or 0.005-0.010 in.
The inlet chamber 145 of the heat sink module 100 can decrease in cross-sectional area in a direction from a front surface 175 of the heat sink module toward a rear surface 180 of the heat sink module, as shown in FIG. 26. The outlet chamber 150 of the heat sink module 100 can increase in cross-sectional area in a direction from a front surface 170 of the heat sink module toward a rear surface 180 of the heat sink module.
The heat sink module 100 can include an inlet port 105 and an inlet passage 165 fluidly connecting the inlet port 105 to the inlet chamber 145. The heat sink module 100 can include an outlet port 110 an outlet passage 166 fluidly connecting the outlet chamber 150 to the outlet port 110. The heat sink module 100 can include a bottom surface 135 and a bottom plane 19 associated with the bottom surface, as shown in FIG. 26. The inlet port 105 can have a central axis 23 that defines an angle (α) of about 10-80, 20-70, 30-60, or 40-50 degrees with respect to the bottom plane 19 of the heat sink module 100. Similarly, the outlet port 110 can have a central axis that defines an angle of about 10-80, 20-70, 30-60, or 40-50 degrees with respect to the bottom plane of the heat sink module.
An additive manufacturing process, such as stereolithography, can be used to manufacture the heat sink module. The stereolithography process can include forming layers of material curable in response to synergistic stimulation adjacent to previously formed layers of material and successively curing the layers of material by exposing the layers of material to a pattern of synergistic stimulation corresponding to successive cross-sections of the heat sink module. The material curable in response to synergistic stimulation can be a liquid photopolymer.
The elements and method steps described herein can be used in any combination whether explicitly described or not. All combinations of method steps as described herein can be performed in any order, unless otherwise specified or clearly implied to the contrary by the context in which the referenced combination is made.
As used herein, the singular forms “a,” “an,” and “the” include plural referents unless the content clearly dictates otherwise.
Numerical ranges as used herein are intended to include every number and subset of numbers contained within that range, whether specifically disclosed or not. Further, these numerical ranges should be construed as providing support for a claim directed to any number or subset of numbers in that range. For example, a disclosure of from 1 to 10 should be construed as supporting a range of from 2 to 8, from 3 to 7, from 5 to 6, from 1 to 9, from 3.6 to 4.6, from 3.5 to 9.9, and so forth.
All patents, patent publications, and peer-reviewed publications (i.e., “references”) cited herein are expressly incorporated by reference to the same extent as if each individual reference were specifically and individually indicated as being incorporated by reference. In case of conflict between the present disclosure and the incorporated references, the present disclosure controls.
The methods and compositions of the present invention can comprise, consist of, or consist essentially of the essential elements and limitations described herein, as well as any additional or optional steps, components, or limitations described herein or otherwise useful in the art.
It is understood that the invention is not confined to the particular construction and arrangement of parts herein illustrated and described, but embraces such modified forms thereof as come within the scope of the claims.
Several impingement technologies exist, but few have shown commercial promise and none have gained wide-scale commercial acceptance to date due to instability issues, relatively high flow rate requirements, limitations on scalability, and other shortcomings.
An improved heat sink module 100 with an array of impinging jet streams 16 has been developed and is described herein. By providing modular heat sink modules 100 that can be connected in series and parallel configurations to cool a plurality of surfaces 12 simultaneously, selecting an appropriate jet height 18, selecting an appropriate coolant pressure and temperature, selecting an appropriate dielectric coolant 50, selecting an appropriate bypass flow configuration, and angling the orifices 155 at a non-perpendicular angle with respect to the surface to be cooled 12, a scalable jet impingement technology has been developed 100. Importantly, the heat sink modules 100 are easy to package inside new and existing server 400 housings and personal computer housings, as well as on a wide variety of other electrical devices and mechanical devices as described herein.
The foregoing description has been presented for purposes of illustration and description. It is not intended to be exhaustive or to limit the claims to the embodiments disclosed. Other modifications and variations may be possible in view of the above teachings. The embodiments were chosen and described to explain the principles of the invention and its practical application to enable others skilled in the art to best utilize the invention in various embodiments and various modifications as are suited to the particular use contemplated. It is intended that the claims be construed to include other alternative embodiments of the invention except insofar as limited by the prior art.

## Claims

1. A heat sink module for cooling a heat providing surface, the heat sink module comprising:
an inlet chamber formed within the heat sink module;
an outlet chamber formed within the heat sink module, the outlet chamber having an open portion, the open portion configured to be enclosed by the heat providing surface when the heat sink module is installed on the heat providing surface;
a dividing member disposed between the inlet chamber and the outlet chamber, the dividing member comprising a first plurality of orifices formed in the dividing member, the first plurality of orifices extending from a top surface of the dividing member to a bottom surface of the dividing member, the first plurality of orifices configured to deliver a plurality of jet streams of coolant into the outlet chamber and against the heat providing surface when the heat sink module is installed on the heat providing surface and when pressurized coolant is provided to the inlet chamber; and
a second plurality of orifices extending from the inlet chamber to a rear wall of the outlet chamber, the second plurality of orifices configured to deliver a plurality of anti-pooling jet streams of coolant to a rear portion of the outlet chamber when pressurized coolant is provided to the inlet chamber.

2. The heat sink module of claim 1, wherein the first plurality of orifices have an average diameter of about 0.001-0.020, 0.001-0.2, 0.001-0.150, 0.001-0.120, 0.001-0.005, or 0.030-0.050 in.

3. The heat sink module of claim 1, wherein the dividing member has a thickness of about 0.005-0.25, 0.020-0.1, 0.025-0.08, 0.025-0.075, 0.040-0.070, 0.1-0.25, or 0.040-0.070 in.

4. The heat sink module of claim 1, wherein each orifice of the first plurality of orifices comprises a central axis, wherein the central axes of the first plurality of orifices are arranged at an angle of about 20-80, 30-60, 40-50, or 45 degrees with respect to the surface to be cooled.

5. The heat sink module of claim 1, wherein the first plurality of orifices are arranged in an array, the array being organized into staggered columns and staggered rows, such that a given orifice in a given column and a given row does not have a corresponding orifice in a neighboring row in the given column or a corresponding orifice in a neighboring column in the given row.

6. The heat sink module of claim 1, wherein each orifice of the second plurality of orifices comprises a central axis, wherein the central axes of the second plurality of orifices are arranged at an angle of about 40-80, 50-70, or 60 degrees with respect to the surface to be cooled.

7. The heat sink module of claim 6, wherein the second plurality of orifices are arranged in a column along the rear wall of the outlet chamber.

8. The heat sink module of claim 1, further comprising one or more boiling-inducing members extending from the bottom side of the dividing member toward the heat providing surface, wherein the one or more boiling-inducing members are slender members extending from the bottom surface of the dividing member.

9. The heat sink module of claim 8, wherein the one or more boiling-inducing members are configured to contact the heat providing surface.

10. The heat sink module of claim 8, wherein the one or more boiling-inducing members are configured to extend toward the heat providing surface, and wherein a clearance distance is provided between the one or more boiling-inducing members and heat providing surface, the clearance distance being about 0.001-0.0125, 0.001-0.05, 0.001-0.02, 0.001-0.01, or 0.005-0.010 in.

11. The heat sink module of claim 1, wherein the inlet chamber decreases in cross-sectional area in a direction from a front surface of the heat sink module toward a rear surface of the heat sink module.

12. The heat sink module of claim 1, wherein the outlet chamber increases in cross-sectional area in a direction from a front surface of the heat sink module toward a rear surface of the heat sink module.

13. The heat sink module of claim 1, further comprising:
an inlet port;
an inlet passage fluidly connecting the inlet port to the inlet chamber;
an outlet port; and
an outlet passage fluidly connecting the outlet chamber to the outlet port.

14. The heat sink module of claim 13, wherein the heat sink module comprises a bottom surface and a bottom plane associated with the bottom surface, wherein the inlet port comprises a central axis, and wherein the central axis of the inlet port defines an angle of about 10-80, 20-70, 30-60, or 40-50 degrees with respect to the bottom plane of the heat sink module.

15. The heat sink module of claim 13, wherein the heat sink module comprises a bottom surface and a bottom plane associated with the bottom surface, wherein the outlet port comprises a central axis, and wherein the central axis of the outlet port defines an angle of about 10-80, 20-70, 30-60, or 40-50 degrees with respect to the bottom plane of the heat sink module.

16. The heat sink module of claim 1, wherein the heat sink module is manufactured by an additive manufacturing process.

17. The heat sink module of claim 16, wherein the additive manufacturing process is a stereolithography process, the stereolithography process comprising forming layers of material curable in response to synergistic stimulation adjacent to previously formed layers of material and successively curing the layers of material by exposing the layers of material to a pattern of synergistic stimulation corresponding to successive cross-sections of the heat sink module, wherein the material curable in response to synergistic stimulation is a liquid photopolymer.

18. The heat sink module of claim 1, wherein the first plurality of orifices have an average diameter of D and an average length of L, and wherein L divided by D is greater than or equal to one or about 1-10, 1-8, 1-6, 1-4, or 1-3.

19. The heat sink module of claim 1, wherein a distance between the bottom surface of the dividing member and the heat providing surface defines a jet height of the plurality of orifices when the heat sink module is installed on the heat providing surface, wherein the jet height is about 0.01-0.75, 0.05-0.5, 0.05-0.25, 0.020-0.25, 0.03-0.125, or 0.04-0.08 in.