Patent Application
20250071943
This invention relates to cooling systems and systems and methods to control them. In particular, this invention relates to a cooling system having both active and passive modes. A particularly suitable application, for example, is in data center cooling systems.
Data centers often require large amounts of energy to operate. The servers in these data centers generate a large amount of heat, requiring cooling. To reduce the energy use of data centers, more efficient cooling systems are desired.
In one aspect, the invention relates to a cooling system including an evaporator, a passive condenser, a heat exchanger, a liquid line, and a pump. The evaporator contains a primary cooling medium. The evaporator is configured to receive a process fluid and, when receiving the process fluid, extract heat from the process fluid to cool the process fluid and to change the phase of the primary cooling medium from liquid to gas. The passive condenser includes an outer surface and is fluidly coupled to the evaporator. The passive condenser is configured to have an airstream directed over the outer surface thereof, and when the airstream is directed over the outer surface of the passive condenser, the passive condenser is configured (i) to receive the primary cooling medium in the gas phase from the evaporator, (ii) to transfer heat from the primary cooling medium, (iii) to change the phase of the primary cooling medium from gas to liquid, and (iv) to supply the primary cooling medium in the liquid phase to the evaporator. The heat exchanger is fluidly coupled to the evaporator and configured to have a secondary cooling medium selectively provided thereto. When the secondary cooling medium is provided to the heat exchanger, at least some of the primary cooling medium in the gas phase switches from being received by the passive condenser to the heat exchanger without operating any valves located between the evaporator and the passive condenser and between the evaporator and the heat exchanger, and the heat exchanger is configured (i) to receive the primary cooling medium in the gas phase from the evaporator, (ii) to transfer heat from the primary cooling medium, (iii) to change the phase of the primary cooling medium from gas to liquid, and (iv) to supply the primary cooling medium in the liquid phase to the evaporator. When the secondary cooling medium is not provided to the heat exchanger, the heat exchanger does not supply the primary cooling medium in the liquid phase to the evaporator. The liquid line fluidly connects the evaporator to each of the passive condenser and the heat exchanger to supply the primary cooling medium in the liquid phase to the evaporator from at least one of the passive condenser and the heat exchanger. The pump is located in the liquid line and configured to pump the primary cooling medium in the liquid phase to the evaporator. The passive condenser is arranged in parallel with the heat exchanger relative to the fluid flow of the primary cooling medium.
In another aspect, the invention relates to a cooling system including an evaporator, a plurality of passive condensers, at least one heat exchanger, a liquid line, and a pump. The evaporator contains a primary cooling medium. The evaporator is configured to receive a process fluid and, when receiving the process fluid, extract heat from the process fluid to cool the process fluid and to change the phase of the primary cooling medium from liquid to gas. Each passive condenser has an outer surface and is fluidly coupled to the evaporator. Each passive condenser being configured to have an airstream directed over the outer surface thereof, and, when the airstream is directed over the outer surface of the passive condenser, the passive condenser is configured (i) to receive the primary cooling medium in the gas phase from the evaporator, (ii) to transfer heat from the primary cooling medium, (iii) to change the phase of the primary cooling medium from gas to liquid, and (iv) to supply the primary cooling medium in the liquid phase to the evaporator. The at least one heat exchanger is fluidly coupled to the evaporator and configured to have a secondary cooling medium selectively provided thereto. When the secondary cooling medium is provided to the at least one heat exchanger, at least some of the primary cooling medium in the gas phase switches from being received by the passive condenser to the at least one heat exchanger without operating any valves located between the evaporator and the passive condenser and between the evaporator, and the heat exchanger and the at least one heat exchanger is configured (i) to receive the primary cooling medium in the gas phase from the evaporator, (ii) to transfer heat from the primary cooling medium, (iii) to change the phase of the primary cooling medium from gas to liquid, and (iv) to supply the primary cooling medium in the liquid phase to the evaporator. When the secondary cooling medium is not provided to the at least one heat exchanger, the heat exchanger does not supply the primary cooling medium in the liquid phase to the evaporator. The liquid line fluidly connects the evaporator to each passive condenser of the plurality of passive condensers and the at least one heat exchanger to supply the primary cooling medium in the liquid phase to the evaporator from at least one of the plurality of passive condensers and the at least one heat exchanger. The pump located in the liquid line and configured to pump the primary cooling medium in the liquid phase to the evaporator. At least one passive condenser of the plurality of passive condensers is arranged in parallel with the at least one heat exchanger relative to the fluid flow of the primary cooling medium.
These and other aspects of the invention will become apparent from the following disclosure.
The cooling system 200 may be divided into two sections, an interior air handler 202 and an exterior condensing unit 204. The portion of the cooling system 200 through which the return air 124 flows, is cooled, and is returned as supply air 122 is referred to herein as the interior air handler 202. The data center 100 shown in
The cooling system 200 of this embodiment has two modes, a passive mode and an active mode. The passive mode may also be referred to as an economization mode.
The cooling system 200 is used to cool a process fluid that contains extracted heat from the electronic components, such as servers, in the racks. The primary coolant loop 240 includes an evaporator 230 thermally coupled to the process fluid. In this embodiment, the process fluid is air, more specifically, the return air 124, and the evaporator 230 is a coil and preferably a one-pass, flooded coil. Any suitable coil may be used including, for example, finned tube coils or microchannel coils, such as those described U.S. Patent Application Pub. Nos. 2018/0038660 and 2021/0368647, the disclosures of which are incorporated by reference herein in their entirety. In both the passive mode and the active mode, the return air 124 is directed over the outer surface of the evaporator 230 by the supply air fans 126. A primary cooling medium is contained within the evaporator 230. The primary cooling medium may be any suitable refrigerant that changes phase from a liquid to a gas, including for example R-134a, and even natural refrigerants such as water. The primary cooling medium also may be referred to as a refrigerant herein. The hot, return air 124 evaporates the primary cooling medium in the evaporator 230 as it passes over the outer surface of the evaporator 230. The phase change of the primary cooling medium from a liquid phase to a gas (or vapor) phase cools the return air 124, allowing it to be returned to the data center 100 as cool, supply air 122.
As noted above and discussed further below, the process fluid may be other suitable fluids including, for example, liquids such as water, water and glycol mixtures, and a non-conductive fluid (dielectric). In these embodiments, the evaporator 230 may be other suitable heat exchangers, including, for example, a plate heat exchanger, a coaxial heat exchanger, or a shell and tube heat exchanger.
The primary cooling medium circulates through a primary coolant loop 240 including the evaporator 230. The primary coolant loop 240 includes tubes, pipes, conduits, and the like, to fluidly connect the various components of the primary coolant loop 240, some of which are shown in
In the passive mode, shown in
When the ambient air conditions are not sufficient to cool the return air 124 to the desired conditions (e.g., temperature) for the supply air 122, the cooling system 200 may be operated in an active mode shown in
In this embodiment, the secondary cooling system 270 is a direct expansion (DX) cooling system using the common refrigeration cycle, and the secondary cooling medium is any suitable refrigerant used in such systems. The secondary cooling system 270 includes a compressor 272 to increase the pressure and temperature of the secondary cooling medium before it is cooled in a condenser 274. In this embodiment, the condenser 274 of the secondary cooling system 270 may also be cooled by the scavenger air 206, and the condenser 274 of the secondary cooling system 270 also may be of any suitable condensers, such as those discussed above for the passive condenser 210. The secondary cooling medium then passes through an expansion valve 276, reducing its pressure and temperature, before flowing into the active condenser 220.
The cooling system 200 preferably operates without the use of valves to switch between modes. In this embodiment, the passive condenser 210 and active condenser 220 are arranged in parallel with each other with respect to the flow of the primary cooling medium. The vapor pipe 250 is bifurcated such that the primary cooling medium in the gas phase flows from the evaporator 230 to one of the passive condenser 210 and the active condenser 220. The primary cooling medium in the gas phase naturally travels to the colder of the two condensers 210, 220 to condense. During the passive mode, the primary cooling medium in the gas phase travels to the passive condenser 210, and, during the active mode, the bulk of the primary cooling medium in the gas phase travels to the active condenser 220. Thus, by activating the secondary cooling system 270 to cool the active condenser 220, the cooling system 200 automatically switches from passive mode to active mode, and by deactivating the secondary cooling system 270, the cooling system 200 switches back to the passive mode. When the ambient temperature is not low enough to provide sufficient heat rejection, the secondary cooling system 270 is activated and at least some of the primary cooling medium in the gas phase switches from being received by the passive condenser 210 to the active condenser 220 without operating any valves located between the evaporator and the passive condenser and between the evaporator and the heat exchanger. In the passive mode, the secondary cooling system 270 is not activated and the secondary cooling medium is not provided to the active condenser 220. In the passive mode, the active condenser 220 does not supply the primary cooling medium in the liquid phase to the evaporator 230. In the active mode, some of the primary cooling medium may condense even in the passive condenser 210.
As noted above, after being condensed in either the passive condenser 210 or the active condenser 220, the primary cooling medium in the liquid phase is supplied to the evaporator 230 through a liquid refrigerant line 260. The passive condenser 210 and the active condenser 220 are both fluidly coupled to a common liquid refrigerant line 260 (also referred to as a liquid line). A pump 280 is located in the liquid refrigerant line 260 and configured to pump the primary cooling medium in the liquid phase to the evaporator. The use of a pump 280 enables the cooling system 200 to be utilized in configurations that are not conducive to the use of natural circulation and gravity, such as conditions where the condensers cannot be placed high enough to provide sufficient pressure head to support the flow of the primary cooling medium in the primary coolant loop 240. Such configurations include, for example, the multi-story data center 100 shown in
In the embodiment shown in
The cooling system 200 may include a plurality of primary coolant loops 240. In this embodiment, the cooling system 200 includes two primary coolant loops 240, a first primary coolant loop 242 and a second primary coolant loop 244. As shown in
The condensing unit 204 shown in
As shown in
The first primary coolant loop 242 also includes three first active condensers 222. One of each of the three first active condensers 222 is located in each of of the first, second, and third circuits. In this embodiment, each of the secondary cooling systems 270 includes two condensers 274 connected in parallel to each other. The condensers 274 are located in the same circuit as the corresponding first active condenser 222. Note the compressor 272 is labeled in
The second primary coolant loop 244 also includes a plurality of second passive condensers 214. In this embodiment, the second primary coolant loop 244 includes six second passive condensers 214. The second passive condensers 214 are connected in parallel with each other, and the second evaporators 234 and are fluidly connected to each of the second passive condensers 214 by the second common vapor pipe 254 and the second common liquid refrigerant line 264. Two of the second passive condensers 214 are located in each of the first, second, and third circuits.
In this emboidment, the second primary coolant loop 244 includes one second active condenser 224 located in parallel with the six second passive condensers 214. The second active condenser 224 is also fluidly connected to the second evaporators 234 by the second common vapor pipe 254 and the second common liquid refrigerant line 264. The second active condenser 224 of the second primary coolant loop 244 is located in the fourth circuit. The fourth circuit includes the second active condenser 224 and its corresponding secondary cooling system 270, but does not include any second passive condensers 214. Each of the four circuits thus includes a secondary cooling system 270.
The arrangements of each of the first, second, and third circuits are similar to each other. The following description of the first circuit applies equally to the second and third circuits. The condensers 212, 214, 222 in the first circuit are arranged in two sets, a first condenser set and a second condenser set. Scavenger air 206 may be driven over the outer surfaces of each of the condenser sets by the scavenger fans 208. The first condenser set and the second condenser set are arranged in parallel with each other relative to the air flow of the scavenger air 206. Each of the first condenser set and the second condenser set contains one of each of the first passive condenser 212 of the first primary coolant loop 242, the second passive condenser 212 of the second primary coolant loop 244, and the condenser 274 of the secondary cooling system 270.
The condensers 212, 212, 274 are arranged in series relative to the air flow of the scavenger air 206. The scavenger air 206 is drawn by scavenger fans 208 of the first circuit through each of the condensers as follows. The scavenger air 206 is ambient air drawn from the outdoor environment surrounding the condensing unit 204 and is first passed through the first passive condenser 212 of the first primary coolant loop 242. Next, the scavenger air 206 is passed through the second passive condenser 212 of the second primary coolant loop 244. Then, the scavenger air 206 passes through the condenser 274 of the secondary cooling system 270 before being exhausted to the outside by the scavenger fans 208. Each of the scavenger fans 208 may be independently variable or at least variable between different circuits. This arrangement of condensers 212, 212, 274 in the first circuit allows for a counter flow design. The primary cooling medium in first primary coolant loop 242 is cooler than the primary cooling medium in the second primary coolant loop 244. Thus, the coldest scavenger air 206 passes through the coldest condenser (the first passive condenser 212) first, and then after being heated by the first passive condensers 212, scavenger air 206 passes through the warmer second passive condenser 214.
The cooling system 200 shown in
When the ambient temperatures are low enough, all of the circuits may be operating in the passive (economization) mode, and the speed of the scavenger fans 208 may be adjusted to help control the temperature of the supply air 122 to a desired set point. If the temperature of the supply air 122 is above the set point and the flow rate of the scavenger air 206 is at its maximum, at least one secondary cooling system 270 may be engaged and the secondary cooling medium supplied to at least one of the first active condensers 222 or second active condenser 224. In the cooling system 200 shown in
If the temperature of the supply air 122 is below the set point and all secondary cooling systems 270 (active cooling modes) are off with the fan speed of the scavenger fans 208 at a minimum, scavenger fans 208 may be staged off as necessary to maintain the temperature of the supply air 122 at the set point. In a case where all but one of the scavenger fans 208 are off, only one of the first primary coolant loop 242 and the second primary coolant loop 244 may be operated. As discussed below, each of the first primary coolant loop 242 and the second primary coolant loop 244 includes a pump 280, namely a first pump 282 and a second pump 284, respectively, to supply the primary cooling medium in the liquid phase to the first evaporators 232 and the second evaporators 234. Operating only one of the first primary coolant loop 242 or the second primary coolant loop 244 can be achieved by operating only one of the first pump 282 or the second pump 284. When the pump 282, 284 is not operating, the corresponding loop 242, 244 is deactivated.
The first pump 282 and the second pump 284 may also be used to help regulate the cooling system 200. Each of the first pump 282 and the second pump 284 may be configured to precisely control the liquid level (amount of primary cooling medium in the liquid phase) in the first evaporators 232 and second evaporators 234, respectively, and maintain a desired temperature of the vapor leaving each evaporator 232, 234. For example, each of first pump 282 and the second pump 284 may be a variable speed pump and controlling the speed of the pump 282, 284 controls the amount of primary cooling medium supplied to the first evaporators 232 and the second evaporators 234. Using the first pump 282 and the second pump 284 in such a manner allows the primary cooling medium to efficiently circulate through the first primary coolant loop 242 and the second primary coolant loop 244 for a wide range of heat loads and ambient air conditions. Adjusting the speed of the pump 282, 284 can be used to prevent too much liquid 204 from entering the evaporators 232, 234 (e.g., flooding the evaporator 232, 234), which could inhibit vapor flow out of the evaporator 232, 234. Further, adjusting the speed of the pump 282, 284 can be used to prevent too little liquid from entering the evaporators 232, 234 (e.g., starving the evaporator 232, 234), which could inhibit effective and efficient condensing in the condensers 212, 214, 222, 224. Such considerations, and speed control for the pump 282, 284, may be particularly relevant where the interior air handler 202 and the condensing unit 204 are separated, as greater distances require larger amounts of the primary cooling medium, further exacerbating the issues discussed above such as flooding.
Various approaches may be used to set the speed of the pumps 282, 284 and thus the amount of liquid flowing into the evaporators 232, 234. For example, the speed of the pumps 282, 284 may be based on heat absorption in the evaporator 232, 234, heat rejection of the return air 124/supply air 122, heat rejection in the condensers 212, 214, 222, 224, heat absorption by the scavenger air 206, or superheat of the vapor. These factors for controlling the speed of the pumps 282, 284 may be measured as described in U.S. Patent Application Pub. No. 2021/0368647, the disclosure of which is incorporated by reference herein in its entirety.
A controller 290 may be used to operate the cooling system 200. In this embodiment, the controller 290 is a microprocessor-based controller that includes a processor 292 for performing various functions discussed herein and a memory 294 for storing various data. The controller 290 may also be referred to as a CPU. In some embodiments, control of the cooling system 200 may be implemented by way of a series of instructions stored in the memory 294 and executed by the processor 292.
The controller 290 may be communicatively coupled to various temperature sensors (“TS”) 296 to monitor the temperature of various environments. The controller 290 is configured to receive temperature information, such as the temperature, from the temperature sensors 296. As shown in
The controller 290 may also be communicatively and operatively coupled to other components of the cooling system 200 and used to control those components as well. For example, the supply air fans 126 and the scavenger fans 208 may be communicatively and operatively coupled to the controller 290, and thus the controller 290 may be used to operate the supply air fans 126 and the scavenger fans 208 as discussed above. The controller 290 may also be communicatively and operatively coupled to the secondary cooling system 270 of each loop and used to turn on or off (activate or deactivate) the secondary cooling system 270, as discussed above. Further, the controller 290 may be communicatively and operatively coupled to the first pump 282 and the second pump 284 to control the operation of each of the first pump 282 and the second pump 284, as discussed herein.
As noted above, each of the first passive condensers 212 and the first active condensers 222 may supply the primary cooling medium in the liquid phase to the first common liquid refrigerant line 262. Likewise, each of the second passive condensers 214 and the second active condenser 224 may supply the primary cooling medium in the liquid phase to the second common liquid refrigerant line 264. As shown in
As noted above and shown in
There may be other configurations where the inlets 268 of the first evaporators 232 and the second evaporators 234 are located at an elevation where gravity and natural circulation are not sufficient to move the primary cooling medium from the outlets 266 of the condensers 212, 214, 222, 224 to the inlets 268. In a configuration that operates without the use of pumps (e.g., first pump 282 and second pump 284), the elevation of the condensers 212, 214, 222, 224 relative to the evaporators 232, 234 and, more specifically, the difference in elevation between the outlets 266 and the inlets 268, provides the maximum hydraulic force available to drive the primary cooling medium in the liquid phase to the evaporators 232, 234. This hydraulic force must be sufficient to overcome the resistance (pressure drop) to the flow of the primary cooling medium within the primary coolant loop 240 (e.g., each of the first primary coolant loop 242 and the second primary coolant loop 244) in order to circulate the primary cooling medium within the primary coolant loop 240 by natural circulation and gravity. Where the available pressure (hydraulic force) due to elevation is less than the pressure drop of the system (primary coolant loop 240), the system will not operate by natural circulation and gravity and options available in such situations include increasing pipe sizing or reducing the massflow of the system. Increasing the pipe sizing, however, increases the installation cost and increases the refrigerant charge required, and reducing the massflow reduces the heat rejection capability of the system. In such situations, the embodiments using a pump 280 discussed herein may be preferred.
The following tables illustrate examples of the second primary coolant loop 244 showing elevations where the embodiments discussed herein may be preferred. Table 1 shows the pressure drop of the system in equivalent linear feet (meters) of pipe for two different mass flows: a mass flow that provides 400 kW of heat rejection capacity and a mass flow that provides 300 kW of heat rejection capacity. A straight length of pipe has a pressure drop per lineal foot of pipe, and the other components in the system, such as elbows, t-sections, the condensing coils, the evaporator coils, etc., may also be converted into equivalent linear feet (meters) of pipe (see, e.g., table 14.7 of the Copper Development Association Inc., Design Handbook). The total is then added to arrive at the total equivalent linear feet (meters) for the second primary coolant loop 244 shown in Table 1. The following examples use R-134a as the primary cooling medium. The diameter of the second common vapor pipe 254 is four inches (10 cm), and the diameter of the second common liquid refrigerant line 264 is two inches (5 cm). Table 2 shows the available hydraulic force for different elevation differences.
As can be seen by comparing the available hydraulic force (Table 2) to the pressure drop (Table 3), a vertical separation of eight feet (2.4 m) or ten feet (3.0 m) provides sufficient pressure for the system (second primary coolant loop 244) to operate by natural circulation and gravity for systems having equivalent linear feet of even 300 feet (91 m). Likewise, a vertical separation of six feet (1.8 m) provides sufficient pressure for the system (second primary coolant loop 244) to operate by natural circulation and gravity for systems having equivalent linear feet of even 300 feet (91 m) with a mass flow for 300 kW in heat rejection. In contrast, the embodiments discussed herein may be used where the available hydraulic force is not sufficient. As can be seen from Tables 1 and 2 above, in a 300 kW heat rejection system, the embodiments discussed herein may be used when the vertical separation is four feet (1.2 m) and the primary coolant loop 240 has a pressure drop of 150 equivalent linear feet (46 m) or more. Similarly, in a 400 kW heat rejection system, the embodiments discussed herein may be used when the vertical separation is six feet (1.8 m) and the primary coolant loop 240 has a pressure drop for 225 equivalent linear feet (69 m) or more and, more preferably when a factor of safety (0.5 PSI (3.4 kPa)) is applied, 150 equivalent linear feet (46 m) or more. In some cases, particularly with the application of a (0.5 PSI (3.4 kPa)) factor of safety, the embodiments discussed herein may be used when the vertical separation is four feet (1.2 m) or less regardless of the equivalent linear feet.
Moreover, relying on natural circulation and gravity, if the condensers 212, 214, 222, 224 and evaporators 232, 234 are positioned appropriately, the system may use relatively large first common liquid refrigerant line 262 and second common liquid refrigerant line 264 to reduce the pressure drop of the first common liquid refrigerant line 262 and second common liquid refrigerant line 264, thus resulting in a relatively large amount of primary cooling medium in each of the first primary coolant loop 242 and the second primary coolant loop 244. Without pumps 280, the line size may be about two 2⅛ inches (5.40 cm), but with a pump 280, the line size can be reduced to about 1⅜ inches (3.49 cm). With corresponding reductions in the first common liquid refrigerant line 262 and second common liquid refrigerant line 264, the refrigerant charge of the primary cooling medium may be reduced by up to forty percent depending on interconnecting line length. The interconnecting line is the portions of the vapor pipes 252, 254 and liquid refrigerant lines 262, 264 between the interior air handler 202 and the condensing unit 204.
Another benefit of using pumps, such as pump 280, is that the pumped system facilitates combining the interior air handler 202 and the condensing unit 204 into a single unit that can be sized to be for shipping over the road.
Over the road transport of a single unit system (cooling system 300) may be advantageous as it allows the unit to be factory built as a single unit and reduces the assembly required at the site where the cooling system 300 will be used. The cooling system 300 can thus be charged and tested for faster deployment and improved quality control. This system may then be connected to the racks 112 to be cooled by a suitable fluid conduit, such as air ducts (not shown) to the rooms holding the racks 112, in this embodiment. The cooling system 300 thus includes a process fluid inlet and a process fluid outlet. Each of the process fluid inlet and a process fluid outlet are fluidly connected to the evaporator 230 to provide the process fluid to and receive the cooled process fluid from the evaporator 230. In this embodiment, the cooling system 300 includes supply air opening 302 and a return air opening 304, that can be connected to ducts to convey the supply air 122 and the return air 124, respectively.
The single unit system (cooling system 300) has additional benefits, including, for example, a reduced primary cooling medium (refrigerant) charge because the amount of piping can be reduced by, for example, omitting the interconnecting piping. The single unit system (cooling system 300) may provide for additional flexibility in the data center 100 configuration as different duct configurations may more radically adapt to the layout and configuration of the data center 100 as compared to pipes such as the vapor pipe 250 and liquid refrigerant line 260, discussed above. Moreover, moving the interior air handler 202 to a position that is exterior to the data center 100 allows for additional floor space on each of the floors 102, 104, 106, that can be used for various purposes including allowing additional racks 112.
In some embodiments, the primary coolant loop 240 (e.g., each of the first primary coolant loop 242 and the second primary coolant loop 244) may include a refrigerant receiver 246, as shown in
The refrigerant receiver 246 may be used when the primary coolant loop 240 is operating in the active mode. Each of the first passive condensers 212 and second passive condensers 214 may have significantly more volume than each of the first active condensers 222 and the second active condenser 224. When operating in the active mode, excess primary cooling medium may be present because of the reduced volume of the first active condensers 222 and the second active condenser 224. The refrigerant receiver 246 may be used to accumulate this excess primary cooling medium and to prevent the primary cooling medium from backing-up into the first active condensers 222 or the second active condenser 224. Such a back-up could reduce the efficiency of the heat rejection in the first active condensers 222 or second active condenser 224. In some embodiments, the refrigerant receiver 246 thus may be used to collect the excess primary cooling medium when the primary coolant loop 240 (e.g., each of the first primary coolant loop 242 and the second primary coolant loop 244) is operating with at least one of the circuits in the active mode. The refrigerant receiver 246 is configured to receive excess primary cooling medium when the evaporator 230 is receiving the primary cooling medium in the liquid phase from at least one of the first active condensers 222 or the second active condenser 224.
The refrigerant receiver 246 may be any suitable refrigerant receiver. Additionally or alternatively, the refrigerant receiver 246 may be an oversized pipe (such as an oversized portion of the first common liquid refrigerant line 262 or second common liquid refrigerant line 264) that is sized appropriately to hold the excess primary cooling medium.
The process fluid cooled by the cooling system 200 in the example discussed above is air (e.g., return air 124). In these previous discussions, air (process fluid) is directed over racks 112 containing electronics and heated before being directed over an evaporator 230 (return air 124) to be cooled. The cooling systems 200 described herein are not limited to cooling air, however, and may be used to cool any suitable fluid. The process fluid may include, for example, liquids such as water, water and glycol mixtures, and a non-conductive fluid (dielectric). In the embodiments discussed above, where the process fluid is air, the evaporator 230 was suitably a microchannel coil or finned tube coils. Where the process fluid is a liquid instead of a vapor (gas), other suitable evaporators 230 may be used, including, for example, a microchannel cold plate, a plate heat exchanger, a coaxial heat exchanger, or a shell and tube heat exchanger.
When the process fluid is a liquid, for example, the process fluid may be circulated in a process fluid loop by a pump. The process fluid may be configured to receive heat from a heat load such as the electronic equipment stored in the rack 112. In some embodiments, the process fluid loop may include an air to liquid heat exchanger and heated air (such as the air in the rack 112) is passed through the heat exchanger to heat the process fluid.
In other embodiments, the cooling system 200 may be used with an immersion cooling system.
In
In the embodiments described above, the servers 114 are physically separated from the evaporator 230 and the process fluid loop 130 is used to transport heat from the servers 114 or other information technology (“IT”) equipment to the evaporator 230. The inventions described herein are not so limited, however, and the evaporators 230 may be any liquid to refrigerant heat exchanger, where a circulating liquid (dielectric fluid, water, or other fluid) transports heat from the IT equipment to the refrigerant that is integral to the two-phase thermosiphon loop. Such other suitable evaporators 230 include, for example, a cold plate integrated into the servers 114 or IT component to directly absorb heat from the component and/or chips therein or a plurality of tubular surfaces directly integrated into a submersion cooling system.
Although this invention has been described with respect to certain specific exemplary embodiments, many additional modifications and variations will be apparent to those skilled in the art in light of this disclosure. It is, therefore, to be understood that this invention may be practiced otherwise than as specifically described. Thus, the exemplary embodiments of the invention should be considered in all respects to be illustrative and not restrictive, and the scope of the invention to be determined by any claims supportable by this application and the equivalents thereof, rather than by the foregoing description.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/US2023/060192 | 1/6/2023 | WO |
| Number | Date | Country | |
|---|---|---|---|
| 63297000 | Jan 2022 | US |
