Apparatus for collecting atmospheric water vapor

Abstract

The present invention relates to devices, systems and products that utilize thermodynamic processes such as condensation, phase change and melting to attract, capture and convert atmospheric water vapor into useful liquid water.

Description

Cross Reference to Related Applications

[0001] This application claims priority to U.S. Provisional Application No. 61 / 413,995, filed November 16, 2010, and U.S. Provisional Patent Application No. 61 / 532,104, filed September 8, 2011. The entire contents of these priority applications are incorporated herein by reference.

[0002] This application is also related to U.S. Provisional Application No. 61 / 413,995, filed November 16, 2010; U.S. Provisional Patent Application No. 61 / 532,104, filed September 8, 2011; PCT / US2012 / 065170, filed November 15, 2012; PCT / US2012 / 065174, filed December 15, 2012; PCT / US2017 / 041530, filed July 11, 2016; Mexican Patent No. 344188, issued December 8, 2016; and U.S. Patent No. US 9711705 B2, issued July 18, 2017. The entire contents of all of these related applications are incorporated herein by reference. TECHNICAL FIELD

[0003] The present disclosure relates generally to the harvesting and / or acquisition of atmospheric water using a thermodynamic process known as water deposition. The present disclosure also relates generally to a device designed to attract and capture water vapor within the atmosphere, instantaneously phase change the captured water vapor into a solid state in the form of frost, a process known as deposition, a mechanism to extract the harvested frost, a process to phase change the extracted frost into its liquid state, and finally store and / or make the liquid water available for various applications, systems, products, devices, and / or components, including, for example, potable water, domestic potable water, agricultural and other commercial or personal uses. BACKGROUND

[0004] There are currently many devices, systems, and products, and these devices, systems, and products are being used to harvest water vapor from the atmosphere using condensation. Since the condensation of water depends on both temperature and pressure, such devices, systems, and products must be designed and / or engineered to accommodate the incoming atmospheric air and the vast array of constantly changing environmental temperatures and pressures that make up the water vapor. These changes in environmental temperature and pressure add significant embedded system costs and ongoing energy costs due to the above design and / or engineering considerations in order to achieve the required system water condensation conditions and to produce overall system collection efficiency.

[0005] In some products, the engineering is designed to accommodate variable atmospheric environmental conditions adding additional size, weight, and components to the overall package, increasing the end product, installation, and operating costs. In most cases, the ability and efficacy of the system to harvest atmospheric water is directly related to the ambient relative humidity and temperature conditions. Low relative humidity and high temperatures decrease overall performance and in many cases, useful water harvesting is limited to systems in atmospheric conditions greater than 30% relative humidity. Additionally, in all currently marketed condensation-based systems, at lower relative humidity levels, liquid water harvesting decreases while the cost per unit of water harvested increases. Additionally, currently marketed condensation-based systems are unable to harvest water when the dew point of water in the atmosphere is below the freezing point of water.

[0006] There are also many other water sectors used to obtain and deliver usable liquid water such as reservoirs, rivers, aquifers, groundwater wells, wastewater treatment plants, and desalination plants. Many of these sources and systems have been used successfully for centuries. However, as the global population continues to increase, water resource shortages are becoming more prevalent. Additionally, the capacity of current reservoirs, rivers, and aquifers has been decreasing as the human water demand increases and the climate changes. Contamination of these sources also increases the population and industry's inability to obtain usable liquid water. Additionally, all of the above sources have embedded energy and maintenance costs when water is obtained from the source.

[0007] Additionally, in many cases, all of the above sources rely on distribution systems that depend on auxiliary maintenance and energy. These auxiliary requirements add additional cost per unit of water delivered for the end user.

[0008] There are many distribution methods currently used to transport water to the end user. Some common examples are: water pipes, pipelines, trucks, ships, and / or different combinations of these methods. However, these methods are often inadequate due to the energy cost and / or maintenance cost of the water delivery system increasing as the population size and age of the system increases. In many cases, even in first-world cities, over 30% to 50% of deliverable water is lost due to pipeline leaks leading to the end user. In the case of modern aqueduct systems, a significant amount of the obtainable deliverable water is evaporated into the atmosphere as the obtainable deliverable water travels from the source location to the local distribution plant where the end user is located. Additionally, in some cases, the energy used for water harvesting, distribution, and delivery is up to twenty percent of the total energy consumption of the population.

[0009] Accordingly, improved apparatuses, systems, and / or products are needed for more efficiently and effectively harvesting and delivering available clean water in order to meet the growing water needs of a growing population. Moreover, as populations increasingly migrate into cities, having an increasing number of commercial and industrial interests within or near these populations, improved apparatuses, systems, and products are needed to efficiently and effectively source the needed water locally to reduce or eliminate water distribution, delivery, and associated maintenance costs. The present disclosure is directed to overcoming and / or ameliorating at least one of the disadvantages of the prior art. SUMMARY

[0010] Exemplary embodiments described herein can involve harvesting water vapor (also referred to as atmospheric water vapor) taken from the atmosphere using the thermodynamics of deposition, resulting in captured frost and / or ice. In exemplary embodiments, the captured frost and / or ice can be extracted from a collection area or surface and stored in a thermally controlled environment, allowing the frost to melt into liquid water.

[0011] In exemplary embodiments, the harvested atmospheric water vapor can be collected, converted, stored, and / or delivered, and thus available on demand at a user's desired location. For example, in exemplary embodiments, the apparatuses, systems, and / or products can eliminate or reduce the need for distribution and / or delivery of liquid water.

[0012] In exemplary embodiments, a desired amount of atmospheric water vapor can be harvested from atmospheres of various temperatures. For example, in exemplary embodiments, the apparatuses, systems, and / or products can harvest a desired amount of atmospheric water vapor in any climatic zone (e.g., tropical, temperate, or polar).

[0013] In exemplary embodiments, a desired amount of atmospheric water vapor can be harvested from atmospheres of various altitudes. For example, in exemplary embodiments, the apparatuses, systems, and / or products can harvest a desired amount of atmospheric water vapor at sea level and / or high altitudes, and any altitudes therebetween.

[0014] In exemplary embodiments, a desired amount of atmospheric water vapor can be harvested from atmospheres of various relative humidity (R.H.) levels. For example, in exemplary embodiments, the apparatuses, systems, and / or products can harvest a desired amount of atmospheric water vapor at R.H. levels of less than 5% R.H., 10% R.H., 20% R.H., 30% R.H., and / or greater.

[0015] In exemplary embodiments, a desired amount of atmospheric water vapor can be harvested from atmospheres of outdoor environments.

[0016] In exemplary embodiments, a desired amount of atmospheric water vapor can be harvested from atmospheres of indoor environments.

[0017] In example embodiments, a desired amount of atmospheric water vapor can be acquired in a combination of the atmosphere of an indoor environment and / or an outdoor environment.

[0018] In example embodiments, the acquired atmospheric water vapor can be drawn into the device, system, and / or product by using a lower temperature within the collection area of the system than the temperature of the ambient atmosphere.

[0019] In example embodiments, the acquired atmospheric water vapor can be drawn into the device, system, and / or product by using a lower pressure within the collection area of the system than the pressure of the ambient atmosphere.

[0020] In example embodiments, the acquired atmospheric water vapor can be drawn into the device, system, and / or product by using some combination of a lower temperature and a lower pressure within the collection area of the system than the ambient atmosphere.

[0021] In example embodiments, the captured frost can be extracted by means of scraping the frost from the collection surface.

[0022] In example embodiments, the captured frost can be extracted by means of utilizing a vibrational frequency on the collection surface.

[0023] In example embodiments, the captured frost can be aided in extraction by means of gravity through the use of an icephobic coating on the collection surface.

[0024] In example embodiments, the low temperature of the collection area or surface can be achieved by means of a refrigeration cycle system (e.g., compressor, condenser coil, expansion device, evaporator coil, and working fluid).

[0025] In example embodiments, the low temperature of the collection area or surface can be achieved by means of a Stirling cycle system (e.g., Sterling Chiller and regenerator).

[0026] In example embodiments, the low temperature of the collection area or surface can be achieved by means of the Peltier effect (e.g., thermoelectric module chiller and heat sink).

[0027] In example embodiments, the low temperature of the collection area or surface can be achieved by means of a thermoacoustic refrigeration system (e.g., electro-acoustic transducer, resonator, regenerator, high and low temperature heat exchangers, and acoustic medium or working fluid).

[0028] In example embodiments, the low temperature collection area or surface can initially be achieved by means of a controlled release of a liquid nitrogen cartridge and thereafter maintained by any of the previously described cooling methods.

[0029] In exemplary embodiments, the low temperature collection region or surface can be maintained by any of the previously described cooling methods, with the addition of a phase change material (PCM) used as a thermal barrier within the collection region to reduce the work required by the system for the cooling process. For example, encapsulating the evaporator coil within a PCM with a phase change point of -35°C to change from a liquid phase to a solid allows the system to be designed such that the selected cooling system turns on at -36°C and then turns off again at, for example, -40°C, performing a minimal amount of work to maintain a 4°C temperature delta, rather than running continuously with a much larger temperature delta from the ambient temperature of the atmosphere, for example 30°C, to the desired -40°C, which can be as much as a 70°C temperature delta. Additionally, the specific heat of a solid phase material is generally lower than the specific heat of its liquid or gaseous state, meaning that less energy is required to cool the PCM in its solid state than if it were in its liquid or gaseous state.

[0030] In exemplary embodiments, a pressure lower than ambient pressure in the collection region can be achieved by maintaining a low temperature in the collection region and providing an outlet means for cooling dry air.

[0031] In exemplary embodiments, the heat generated by the cooling cycle of the system can be used to melt the captured frost into liquid water.

[0032] In exemplary embodiments, the newly melted liquid water (chilled water) can be used to reduce heat, thereby reducing the energy requirements of the cooling cycle of the system. For example, the fan inlet for the condenser coil can be positioned to draw air through the chilled water tank of the system to reduce the required fan speed, and thus the total energy required by the system.

[0033] In exemplary embodiments, a portion of the capillary expansion device of the refrigeration cycle cooling system can be embedded or partially embedded in the cold PCM of the evaporator coil to control the state of the refrigerant at the end of the liquid line, thereby reducing the energy requirements of the system.

[0034] In exemplary embodiments, the heat generated by the cooling system can be adjusted and transferred to another system, such as a water heater or space heater, by using a brazed plate heat exchanger embedded in a liquid PCM material before or after the condenser coil, thereby reducing the work and energy required by the system.

[0035] In exemplary embodiments, the device, system, and / or product can be engineered to be installed in a manner to ensure that the volume of water to be delivered to the end user is gravity fed by reducing or eliminating the use of a pump and ancillary maintenance and / or energy costs.

[0036] In exemplary embodiments, the device, system, and / or product can employ the use of additional filtration devices to deliver certified potable water.

[0037] In addition to the embodiments discussed in the summary, other embodiments are disclosed in the specification, drawings, and claims. The summary is not meant to encompass every embodiment, combination, or variation contemplated by the disclosure. BRIEF DESCRIPTION OF DRAWINGS

[0038] Example embodiments will now be described, by way of example only, with reference to the attached figures, of which:

[0039] Figure 1 is a schematic of an exemplary embodiment of a system for harvesting atmospheric water vapor by means of a thermodynamic process known as deposition.

[0040] Figure 2 is a schematic of another exemplary embodiment of a system for harvesting atmospheric water vapor by means of a thermodynamic process known as deposition. Figure 2 Similar to Figure 1 , except that in Figure 2 A device is disclosed that saves some of the cooling work done by the refrigeration cycle by embedding the evaporative coil in a low temperature encapsulated PCM.

[0041] Figure 3 is a schematic of the embedded evaporative coil of Figure 2 .

[0042] Figure 4 is a cross-sectional view of the embedded evaporative coil of Figure 3 .

[0043] Figure 5 is a schematic of another exemplary embodiment of a system for harvesting atmospheric water vapor by means of a thermodynamic process known as deposition. Figure 5 Similar to Figure 2 , except that in Figure 5 The end of the condensing coil and the expansion device are also embedded in the low temperature encapsulated PCM disclosed in Figure 2 , Figure 3 and Figure 4 .

[0044] Figure 6 is a schematic of another exemplary embodiment of a system for harvesting atmospheric water vapor by means of a thermodynamic process known as deposition. Figure 6 Similar to Figure 5 , except that in Figure 10 Instead of a fan and a condensing coil, a brazed plate heat exchanger transfers the harvested thermal energy to the secondary system.

[0045] Figure 7 is Figure 1 , Figure 2 , Figure 5 and / orFigure 6 schematic of an exemplary embodiment disclosed herein, which discloses a method of attracting, directing, and circulating atmospheric water vapor into and out of a collection area.

[0046] Figure 8 is Figure 7 schematic detail of an exemplary embodiment disclosed herein, which discloses a method of thermally isolating frost collection surfaces.

[0047] Figure 9 is Figure 8 another schematic detail of an exemplary embodiment disclosed herein, which discloses a method of controlling volume circulation between frost collection surfaces.

[0048] Figure 10 is Figure 7 another schematic detail of an exemplary embodiment disclosed herein, which discloses a method of removing frost from collection surfaces into an integrated water tank. DETAILED DESCRIPTION

[0049] Exemplary embodiments described herein relate to the use of a thermodynamic process known as water deposition to attract and harvest atmospheric water vapor, in which water vapor "skips" the liquid phase and goes directly from vapor to ice or frost.

[0050] Exemplary embodiments described herein relate to reducing the energy demand of current refrigeration systems that are capable of achieving and maintaining subzero temperatures required for water deposition. Certain embodiments can be at least 10% or as much as 100% independent of grid energy and / or fossil fuels.

[0051] Exemplary embodiments described herein relate to reusing a fraction of the thermal energy released from within water vapor when it phase changes to a solid phase, or in other embodiments, a substantial fraction. Certain embodiments can employ a supplemental system to reuse the harvested thermal energy by converting the harvested thermal energy into kinetic energy to do work on the system using a working fluid. For example, the thermal energy can be directed to a supplemental system in which the thermal energy is used to drive a heat engine. The use of a supplemental system that utilizes directed thermal energy can also reduce the work of the condenser coils of the main system to reject waste heat to the environment, which in turn will reduce the power demand of the compressor.

[0052] Exemplary embodiments described herein can be beneficial for natural and built environments and for economic reasons. In exemplary embodiments, at least for certain applications, the systems, methods, and / or apparatuses can eliminate or reduce the need for external electrical power to be transmitted into the system. In exemplary embodiments, the thermal energy harvested from water vapor can be stored. In other exemplary embodiments, the thermal energy can be stored and can be transported to another location of the system or to a supplemental system.

[0053] Example embodiments described herein relate to utilizing captured frost-to-liquid water phase change to assist the condensing side of a refrigeration cycle, thereby reducing the energy demand of the overall system.

[0054] Example embodiments described herein can be beneficial for natural and built environments and for economic reasons. In example embodiments, at least for certain applications, the systems, methods, and / or apparatuses can eliminate or reduce the need for water to be provided by an external water distribution and / or delivery system. In example embodiments, the systems, methods, and / or apparatuses can be installed directly at an end user location and connected directly to an end user internal water system. In certain applications, particularly for new construction, example embodiments described herein can reduce or eliminate the cost and / or maintenance of an underground or other municipal water supply system. In certain applications, example embodiments described herein can reduce or eliminate the cost of delivering water to an end user by truck. Additionally, in example embodiments described herein, the systems, methods, and / or apparatuses can eliminate or reduce the need for a water pump at the end user.

[0055] Figure 1 is a schematic of an example embodiment of a system that utilizes a thermodynamic process known as deposition to harvest atmospheric water vapor that instantaneously freezes the water vapor. Figure 1 Example embodiments of are an improvement over current atmospheric water harvesting systems that utilize a more generally known thermodynamic process of condensing water to harvest liquid water from the atmosphere.

[0056] Figure 1The atmospheric water harvester consists of three processes. The first process is driven by a mature and commercially available refrigeration cycle used in everyday refrigerators and / or freezers. Input energy 1, A / C or D / C power, powers the compressor 2 and fan 3, whose on / off status is determined by switch 4 and temperature sensor 5. The closed loop refrigeration cycle consists of compressor 2, condensing coil 6, expansion device 7, and evaporating coil 8. A volume of working fluid, typically a commercial refrigerant, is sealed within the aforementioned closed loop refrigeration cycle. When the system is in the "on" state, the compressor 2 is on, compressing the working fluid within the condensing coil 6, typically in a vapor state when the system is "off, into a liquid. The fan 3 is also on, blowing ambient air across the condensing coil 6 to help a portion of the thermal energy 15 of the working fluid exit the system through the walls of the condensing coil 6 and into the ambient air. The process of compressing and expelling thermal energy 15 from the working fluid condenses the working fluid from a vapor state to a liquid state. Furthermore, this portion of the refrigeration cycle is referred to as the "high pressure / high temperature side" of the system. The "high pressure" is due to the compressor 2 pumping the refrigerant (working fluid) into one end of the condensing coil 6, while the expansion device 7 at the other end of the condensing coil 6 restricts the flow of refrigerant. The "high temperature" is a result of the thermal energy 15 exiting the system through the walls of the condensing coil 6 during this stage of the process. The expansion device 7 restricts the flow of working fluid from the condensing coil 6 into the evaporating coil 8 on the opposite side of the system, referred to as the "low pressure / low temperature side" of the system. The low pressure inside the evaporating coil 8 is due to the restricted flow of working fluid through the expansion device 7 on one side of the evaporating coil 8, and due to the suction of the compressor 2 on the opposite end of the evaporating coil 8. The working fluid or refrigerant enters the evaporating coil 8 from the expansion device 7 in a vapor state due to the lower pressure inside the evaporating coil 8. The phase change of the working fluid from a liquid to a vapor introduces thermal energy 15 into the system through the walls of the evaporating coil 8, thereby cooling the evaporating coil 8 and the frost collection surface 9 attached to it on its way back to the compressor. This cycle continues until the temperature sensor 5 senses the temperature of the frost collection surface 9 of the system process designed to collect atmospheric water vapor, and the switch 4 is turned on, "turning off' the compressor 2 and fan 3 of the refrigeration cycle. For example, the design temperature of the frost collection surface can be -10°C, -20°C, -30°C, -40°C, -50°C, or lower. For example, the sensor can be set to "turn on" when the frost collection surface 9 temperature is above -10°C; the sensor can be set to "turn off' when the frost collection surface 9 temperature is below -45°C.

[0057] Figure 1 The second process of the atmospheric water harvester is driven by the thermodynamic reaction process between the water vapor in the atmosphere that comes in close proximity to and / or contacts the frost collection surface 9. This reaction process is a direct result of the second law of thermodynamics; the result is that heat must be transferred unidirectionally from a hotter object to a colder object. In Figure 1In the case of an atmospheric water harvester, the warmer object is the water vapor 13 interacting with the frost collection surface 9 of the colder object. As is the case with any energy transfer system, the greater the difference between the high and low temperatures, the greater the potential and rate of energy transfer.

[0058] The strength of the heat conduction process can be easily calculated and / or expressed using the heat conduction law, also known as Fourier's Law.

[0059] Q = (k / s) A dT U A dT

[0060] where,

[0061] Q = heat transfer W

[0062] k = material thermal conductivity W / m o K

[0063] s = material thickness m

[0064] A = heat transfer area m

[0065] U k / s = heat transfer coefficient W m² o K

[0066] dT t1 t2 = temperature gradient - difference - across material (°C)

[0067] In simpler terms, and with all other conditions of the above equation being static, the greater the dT between the hot and cold bodies, the greater the heat transfer. For example, using 40°C as the temperature of the ambient water vapor 13 (hot body) and -1°C as the system design temperature of the frost collection surface 9 (cold body), dT equals 41°C. Reducing the system design temperature of the frost collection surface 9 to, for example, -50°C widens dT to 90°C, thereby increasing the rate of heat energy transfer.

[0068] ​​​​​​​​​​A well-established conclusion, detailed in many published scientific studies over the past 50 years, is that the largest factor affecting the rate of frost growth is the dT between water vapor 13 and the frost collection surface 9. These studies were primarily to understand the conditions of frost growth rate in order to help engineers develop methods to slow down or limit the process of frost in the aerospace and refrigeration industries, as frost accumulation has a negative impact on systems within these industries. In Figure 1 atmospheric water harvesters, the goal is the opposite, it is to accelerate and promote frost growth.

[0069] Another factor in the growth of frost rate found in the studies is that the frost rate growth slows down as the frost layer thickens. Most studies conclude that this slowing of the frost growth is primarily due to two influences, the first is the crystalline nature of the frost, which causes air pockets or voids in the frost that become the point of contact for incoming water vapor 13, instead of the frost collection surface 9. The second is the influence of the frost layer itself, as the frost layer thickens, it creates a thermal barrier or insulating layer between the incoming water vapor 13 and the frost collection surface 9. The dT narrows, and other heat transfer characteristics in the equation such as k, s, and A are no longer static. The water vapor 13 is no longer in direct thermal interface connection with the frost collection surface 9, it is in interface connection with the frost layer. However, in a system designed for atmospheric water harvesting, it is extremely important to utilize the deposition process to optimize the fast frost growth rate of water vapor 13 from the second process of Figure 1 atmospheric water harvesters. Figure 1 systems can benefit from keeping the temperature of the frost collection panel 9 at a low temperature, for example -50, by the refrigeration process described above, to ensure a large dT with the water vapor 13, for example, can be 40°C, and to provide a means or process to peel the accumulated frost layer 14 from the frost collection surface 9 and away from the frost collection surface 9, which will be described below.

[0070] Therefore, Figure 1 the third process of the atmospheric water harvester of Figure 1 atmospheric water harvesters is a scraper 10 driven by a scraper actuator 11 powered by electrical input energy 1. The scraper 10 moves along a fixed timed scraper path 12, thereby removing and moving away the new frost layer 14 from the frost collection surface 9. For example, the scraper actuator can be programmed to allow the layer of frost 14 to reach a maximum depth of 0.1 mm before scraping occurs. When the frost 14 is scraped from

[0071] Figure 2is a schematic of another exemplary embodiment of a system that harvests atmospheric water vapor by means of a thermodynamic process known as deposition. Figure 2 With Figure 1 Similar to Figure 2 , some of the cooling work done by the refrigeration cycle is saved by embedding the evaporative coil 8 in a low temperature PCM 17 encapsulated in a PCM enclosure 16, which can reduce the overall system cooling energy requirements.

[0072] Encapsulating the evaporative coil 8 in a low temperature thermal storage device PCM 17 eliminates the contact between the evaporative coil 8 and the warmer water vapor 13 to be cooled. In addition, sealing the disclosed evaporative coil 8 prevents or reduces the need for the system of this embodiment to re-cool the frost collection surface 9 during the compressor on and off cycles. Doing so also maintains the low temperature of the evaporative coil 8 while the compressor 2 is working. Known refrigeration cycle system compressors typically cycle on and off many times a day, with most or in some cases all of the work being lost to the warm air surrounding the evaporative coil; however, when the evaporative coil 8 is encapsulated in a low temperature thermal storage device PCM 17, a portion of the work time per cycle is preserved due to the low temperature thermal storage device PCM 17 acting as a thermal barrier between the water vapor 13 and the evaporative coil 8. In addition, with the addition of an automatic valve, the low temperature thermal storage device PCM 17 can maintain the temperature and low pressure of the working fluid within the evaporative coil 8 during the “off’ period of the system operating cycle at the beginning and end of the evaporative coil 8, thereby saving the associated work done by the compressor 2 during the previous “on” cycle.

[0073] The selection of the optimal low temperature thermal storage device PCM 17 to encapsulate the evaporative coil 8 can be based primarily on the desired design temperature of the frost collection surface 9 in order to maintain the desired dT with the incoming water vapor 13. For example, on an atmospheric water collection system in an environment that frequently reaches ambient temperatures above 30°C and the desired design temperature of the frost collection surface 9 is determined to be -40°C, a low temperature thermal storage device PCM 17 with a phase change temperature from solid to liquid phase of, for example, -30°C can be selected.

[0074] In the above example, the low temperature thermal storage device PCM 17 of -30°C was chosen for two main reasons. First, in order to maintain the frost collection surface 9 at -40°C, the low temperature thermal storage device PCM 17 will have to be cooled intermittently to between -42°C and -45°C due to the incoming thermal energy of the water vapor 13 and the cooling capacity of the refrigeration cycle system. In this temperature specific design of the system, the temperature sensor 5 of the compressor 2 can be set to for example turn the system “on” at -42°C and again “off” at -45°C, so that the refrigeration cycle cools only 3°C dT instead of 75°C dT of the difference between the desired -45°C of the frost collection surface 9 and the 30°C of the incoming water vapor 13. Additionally, PCMs in their solid phase generally require about 50% less energy to cool / heat than they do in their respective liquid phase. For example, water with a phase transition point of 0°C from liquid to solid or solid to liquid requires only 2.06 J / g°C in the solid state, while it requires 4.18 J / g°C in the liquid state. Furthermore, a phase transition of 1°C temperature change at the phase transition point requires an additional 334 J / g for that 1°C temperature change.

[0075] Most refrigeration systems have lower cooling capacity and efficiency when their evaporator temperature is below -20°C, and all solids have lower specific heat capacity in their respective solid state and are generally better thermal conductors than in their liquid state. In short, heating or cooling a substance in its respective solid state requires much less work, and thus much less energy, than in its liquid state. Therefore, in operation, it requires much less work to maintain a predetermined mass of PCM at a temperature below -42°C than it does for the refrigeration cycle to cool the incoming amount of water vapor and air from the varying outdoor environment to -45°C. In this way, the refrigeration cycle of the system only cools the low temperature PCM 17 substance from for example -42°C to -45°C, while the low temperature PCM 17 substance cools the incoming water vapor 13 from the incoming temperature of the water vapor 13 to -45°C.

[0076] Second, the atmospheric water collection system can not need to be operated continuously. For example, if the liquid water collection basin 21 is full, the entire system can be shut down by the user, whereby the compressor will no longer circulate. The system can be shut down for routine cleaning or maintenance work. The cryogenic PCM 17 material will warm slowly at a rate that depends primarily on how well the PCM enclosure 16 is insulated from the warmer ambient environment. However, if the cryogenic PCM 17 has a phase transition temperature of -30°C, as in the example above, the latent heat of fusion will extend the time required to warm from -30°C to -29°C by a time factor of more than 100 times the previous temperature increase per degree Celsius. If the PCM enclosure 16 is well insulated from the warmer temperatures, the cryogenic PCM 17 can remain at -30°C for days rather than minutes. In contrast, the standard evaporative coil 8 without cryogenic PCM 17 encasement, even well insulated, will warm to very close to ambient temperature within a few minutes of the system being shut down. Furthermore, the system can require a hot "pull down" of 95°C to achieve a frost collection surface temperature of -40°C without the cryogenic PCM 17 encasement, whereas with the addition of the cryogenic PCM 17 encasement around the evaporative coil 8, the system can require only a hot "pull down" of, for example, 15°C, thus saving time and energy upon restart.

[0077] Figure 3 and Figure 4 is Figure 2 schematic diagram of an embedded evaporative coil 8 within the PCM enclosure 16 disclosed in Figure 3 and Figure 4Exemplary embodiments of the PCM enclosure 16 disclose useful design methods of selecting materials and material properties that are beneficial to the water deposition process. The front and back surfaces of the PCM enclosure 16 are each a frosting surface 9. Impervious materials with good thermal conductivity are applied to the PCM enclosure 16 structure. Additionally, wall thickness, material thickness, reactivity to atmosphere, reactivity to PCM, finish, ease of manufacturing, and material availability are important features in proper selection. For example, the PCM enclosure 16 will be exposed to water vapor, maintained at temperatures below -30°C for extended periods of time, and hold cryogenic PCM 17 that can include, for example, distilled water and ethanol mixed in percentages to set the phase change design temperature of the cryogenic PCM 17. The smoother the finish of the outer surface of the PCM enclosure 16, which is also a frosting surface 9, the easier it is to remove accumulated frost 14. Aluminum sheet grades such as 1100, 3003, 3004, and 5052 can be used as the PCM enclosure 16 housing, considering that these grades are corrosion resistant, have high thermal conductivity, are lightweight, and are readily available in the market. Stainless steel 316 sheet can also be used as the PCM enclosure 16 housing over the aforementioned aluminum grades due to the Young’s modulus and tensile strength of stainless steel exceeding the aluminum grades that can be selected based on price and weight. The aluminum and stainless steel grades described herein are by way of example only, and other materials can be selected based on the values of the aforementioned material properties. Since the frosting surface 9 should be flat, a corrosion resistant epoxy capable of withstanding temperatures below -45°C is used to attach the inner enclosure bracket 23 channel to the inner surface of the enclosure to prevent surface deformation.

[0078] The evaporator coil 8 enters the PCM enclosure 16 through the evaporator inlet hole 24. The evaporator coil 8 is shaped to bend around the inner enclosure bracket 23 channel and can be evenly distributed within the PCM enclosure 16 to optimally provide equal cooling of the cryogenic PCM 17 enclosed within the PCM enclosure 16, which is enclosed in the PCM enclosure 16. The evaporator coil 8 exits the PCM enclosure 16 through the evaporator outlet hole 25. The evaporator inlet hole 24 and the evaporator outlet hole 25 need to be sealed to the outside of the PCM enclosure 16 to prevent the cryogenic PCM 17 from degrading over time. Additionally, a temperature sensor tube 28 can be installed and affixed to the inside of the PCM enclosure 16. The temperature sensor tube 28 needs to be sealed to the outside of the PCM enclosure 16 to prevent the cryogenic PCM 17 from degrading over time. The PCM enclosure 16 edges can be mechanically closed using adhesive and / or welding to form the enclosure. The PCM enclosure 16 can be sealed to prevent the cryogenic PCM 17 from degrading over time.

[0079] Figure 5 This is a schematic diagram of another exemplary embodiment of a system for harvesting atmospheric water vapor by means of a thermodynamic process called deposition. Figure 5 Similar to Figure 2 In addition to Figure 5 In the middle, the end of the condenser coil 6 and the expansion device 7 are also encapsulated in Figure 2 , Figure 3 and Figure 4 The PCM enclosure 16 disclosed herein. It is well understood in the refrigeration industry that refrigerant subcooling is a reliable way to improve system performance and save energy. Many methods for subcooling the refrigerant in the condenser coil 6, compressor 2, and similar separate systems are known and in use. These methods generally increase the complexity and cost of the refrigeration cycle system. Extensive research has been conducted on this subject, primarily due to a sufficient understanding that the quality of the refrigerant before entering the evaporator affects the overall system performance. The novel method described herein is possible because the evaporator coil 8 is embedded in a cryogenic encapsulated PCM 17 held within the PCM enclosure 16. Refrigerant subcooling can be performed at the condenser coil 8—industrially also known as the “liquid line”—terminus and the capillary expansion device 7. Subcooling at these two locations is much easier and simpler than at other locations in the refrigeration cycle, as the amount of refrigerant at these locations is relatively small in a given time. The refrigerant at these locations is more or less “captive” and easily affected by heat. Furthermore, the temperatures of the PCM enclosure 16, the cryogenic PCM 17, and the evaporator coil decrease during the cycle, resulting in a large heat sink compared to a small amount of refrigerant. Subcooling the refrigerant before the expansion unit 7 has two additional benefits, further reducing the subcooling workload on the compressor 2 and the condenser coil 6. The first benefit is ensuring that the refrigerant is indeed in a liquid state when it enters the evaporator coil 8 through the expansion unit 7. The second benefit is that the lower-temperature liquid refrigerant has a higher viscosity, resulting in greater resistance within the expansion unit. Therefore, placing the liquid line within the bladder inside the PCM enclosure 16 effectively reduces the workload on the compressor 2 and the condenser coil 8 without increasing system costs.

[0080] Figure 5 and Figure 2The system disclosed in the middle differs in that it includes two ball valves 30. One ball valve 30 is inline immediately before the expansion device 7, and the second ball valve 30 is inline immediately after the evaporating coil 8. The purpose of the two ball valves 30 is to save the cooling work of the refrigeration cycle on the low temperature PCM 17 by stopping the flow of refrigerant by closing both ball valves 30 when the compressor 2 is "off. Without the addition of the two ball valves 30 to the cycle, the refrigerant on the high pressure side of the system inside the condensing coil 6 will continue to flow to the low pressure side even though the compressor 2 is off until the two sides are at equal pressure. Without the compressor 2 "on", this flow brings heat from the condensing coil 6 into the evaporating coil 8 which will be absorbed by the cooler low temperature PCM, increasing unnecessary work in the next "on" cycle. When the compressor 2 is "on", the two ball valves 30 are open to allow the refrigerant to circulate normally.

[0081] Figure 6 is a schematic of another exemplary embodiment of a system for harvesting atmospheric water vapor by means of a thermodynamic process known as condensation. Figure 6 Similar to Figure 5 , except that in Figure 6 a brazed plate heat exchanger 18 replaces the fan 3 and condensing coil 6, transferring the harvested thermal energy to a secondary system. In at least some applications, it can be useful to transfer the thermal energy 15 harvested from the refrigeration cycle to a separate system that can utilize the thermal energy 15. In the exemplary embodiment of Figure 6 , the refrigerant flow exiting the compressor 2 flows through the brazed plate heat exchanger 18 before entering the expansion device 7 of the system. The working fluid of the secondary system enters the opposite side of the brazed plate heat exchanger 18 through an inlet pipe 19. As the working fluid of the secondary system passes through the brazed plate heat exchanger 18 in the opposite direction of flow of the refrigeration cycle of the compressor 2, the thermal energy 15 from the refrigeration cycle after the compressor 2 is transferred to the working fluid of the secondary system and thereby condenses the working fluid of the refrigeration system, accomplishing the work normally done by the condensing coil 8 and fan. As an example, the secondary system can be used as a water heater or for space heating an environment.

[0082] Figure 7 is a schematic of the exemplary embodiments disclosed in Figure 1 , Figure 2 , Figure 5 and / or Figure 6 , which disclose a method of attracting, directing and circulating atmospheric water vapor 13 into and out of the collection area of the system. In the exemplary embodiment of Figure 7 , until previously in Figure 1 , Figure 2 , Figure 5 and / or Figure 6The refrigeration process disclosed in the middle has reached the desired design temperature of the frost collection surface 9, for example -40°C, the process of drawing, directing and circulating atmospheric water vapor 13 into and out of the collection area of the system begins. While the refrigeration cycle is running during this "pull down" process, the insulated lid 33 is in the closed position and sealed by the lid seal 34. The collection area is thermally protected by the insulated housing 31. The liquid water collection basin 21 is attached to the bottom of the collection area by the tank seal 36. Once the frost collection surface 9 is at the appropriate temperature, the scraper actuator 11 raises the insulated lid 32 with the attached scraper panel 42 along the scraper path 12 until it reaches the open position. After a predetermined time, the scraper actuator 11 reverses and the insulated lid 33 closes and reseals the collection area. The lid remains closed for a predetermined time and the process is repeated until the process is stopped by the water float valve 38, which indicates that the liquid water collection basin 21 is full. When the water float valve 38 indicates that the water level in the liquid water collection basin 21 has dropped, the above process restarts and repeats. While the insulated lid 32 with the attached scraper panel 42 is in the open position, warm ambient air and water vapor 13 are drawn into the collection area by both heat and pressure. While the insulated lid 33 with the attached scraper panel 42 is in the closed position, the water vapor 13 is momentarily attached to the frost collection surface 9 as frost 14. The remaining air in the collection area is cooled and drops down the collection area into the liquid water collection basin 21 and exits through the cold dry air vent 39 to the outside ambient environment after passing through the air float valve 40. When the insulated lid 32 with the attached scraper panel 42 is opened again, the frost 14 collected on the frost collection surface 9 is scraped off the frost collection surface 9 by the scraper panel 42 upwards and outwards, where the frost 14 falls and eventually falls into the liquid water collection basin 21. The bottom of the liquid water collection basin 21 is fitted with a tank radiator 37 to ensure that the bottom of the tank is above 0°C, ensuring that the frost 14 melts into liquid water 22. The above process is repeated until the process is stopped when the water float valve 38 indicates that the liquid water collection basin 21 is full, and the process is restarted when the water float valve 38 indicates that the water level in the liquid water collection basin 21 has dropped. The liquid water 22 can be removed from the liquid water collection basin 21 for use through the liquid water outlet 44.

[0083] Figure 8 is Figure 7 schematic details, which discloses a method of thermally isolating a frost collection surface. In Figure 8 example embodiments, special thermal isolation of the collection area of the system from the outside ambient temperature is required due to the very large dT between them. For example, the dT between the collection area temperature and the outside ambient temperature can be 70°C, 80°C, 90°C or more. In order to keep the overall system size reasonable, a layered approach has been designed to limit the thickness of the insulated housing 31 to 2.6 centimeters. Figure 8The layering method of the exemplary embodiment reduces the size of the insulation shell 31 by at least 28 cm compared to normal cooling insulation material. Figure 8 In an exemplary embodiment, the outer wall of the environment interacting with ambient temperature 51 is a fiberglass shell 45, followed by a 0.7 cm aerogel layer 46, and then a cavitation spacer consisting of two staggered layers of a multi-core board 47 with a total thickness of 0.68 cm. Following the multi-core board 47 is a 1 cm thick layer of refrigerant Z48, which is attached to a stainless steel inner structural shell 49 exposed to the collection area temperature 50. This 2.6 cm layering method limits the 90°C dT to only 30 watts transferred per hour over a 1 square meter surface area.

[0084] Figure 9 yes Figure 7 The schematic details further illustrate the flow pattern of water vapor 13 entering the collection area, and show in detail the heat insulation cover (opening) 32, heat insulation cover (closed) 33, cover seal 34, heat insulation housing 31, scraper actuator 11, scraper path 12, PCM enclosure 16, frost collection surface 9 and scraper panel 42.

[0085] Figure 10 yes Figure 9 The schematic details further illustrate the frost 14 scraping flow, which defines the thermal insulation housing 31, the PCM enclosure 16, the frost collection surface 9, the scraper path 12, the scraper panel 42, and the frost dripping direction 43.

[0086] In the exemplary embodiments described herein, the following figures are labeled with identifiers: labels / structures / operations:

[0087] 1. Input energy

[0088] 2. Compressor

[0089] 3. Fan

[0090] 4. Switch

[0091] 5. Temperature sensor

[0092] 6. Condensing coil

[0093] 7. Expansion device

[0094] 8. Evaporator coil

[0095] 9. Collect frost on the surface

[0096] 10. Scraper

[0097] 11. Scraper Actuator

[0098] 12. Scraper path

[0099] 13. Water vapor

[0100] 14. Frost

[0101] 15. Thermal energy

[0102] 16. PCM Packaging Box

[0103] 17. Low-temperature PCM

[0104] 18. Brazed plate heat exchanger

[0105] 19. Inflow catheter

[0106] 20. Outflow tube

[0107] 21. Liquid water collection basin

[0108] 22. Liquid water

[0109] 23. Internal box support

[0110] 24. Evaporator inlet hole

[0111] 25. Evaporator outlet hole

[0112] 26. PCM box filling opening

[0113] 27. PCM box vent opening

[0114] 28. Temperature sensor tube

[0115] 29. Temperature sensor leads

[0116] 30. Ball valve

[0117] 31. Insulated shell

[0118] 32. Heat insulation cover (open)

[0119] 33. Heat insulation cover (closed)

[0120] 34. Cover sealing element

[0121] 35. Box insulation components

[0122] 36. Box seals

[0123] 37. Radiator

[0124] 38. Water float valve

[0125] 39. Cooling and drying ventilation holes

[0126] 40. Air float valve

[0127] 41. Cooling and drying air

[0128] 42. Scraper panel

[0129] 43, frost drip direction

[0130] 44, liquid water outlet

[0131] 45, glass fiber outer shell

[0132] 46, aerogel

[0133] 47, multi-core panel

[0134] 48, refrigerant Z

[0135] 49, internal structure housing

[0136] 50, collection area temperature

[0137] 51, ambient temperature

Claims

1. A system for attracting, capturing and converting atmospheric water vapor into useful liquid water, the system comprising: a plurality of low temperature phase change material (LTPCM) boxes, tubes or containers; wherein the outer surface of each individual LTPCM box, tube or container is thermally conductive and has a smooth finish as a frost collection area for the deposition of water, where water vapor is instantaneously converted to solid water, deposited on their respective outer surfaces; wherein the internal volume of each individual LTPCM box, tube or container contains a mass of low temperature phase change material with thermal properties that remains in its solid state for long periods of time before requiring subsequent cooling to resist melting, to allow long term collection of atmospheric water by deposition; a plurality of evaporator coil heat exchangers of a cooling system, wherein each individual evaporator coil is embedded, submerged and / or encapsulated within an individual LTPCM box, tube or container, to be free from direct contact with water vapor or air; a cooling system to lower and maintain the temperature of the LTPCM within each LTPCM box, tube or container; a timing mechanism to cycle the "on" or "off' cooling system to maintain the LTPCM at a desired temperature to maintain the respective surface temperature of the plurality of LTPCM boxes, tubes and / or containers for the deposition of water; an arrangement of the plurality of LTPCM boxes, tubes and / or containers, wherein each individual LTPCM box, tube or container is arranged in close proximity to, but also spaced apart from, other LTPCM boxes, tubes or containers, to allow unrestricted flow or accumulation of water vapor around the respective outer surfaces of the array of LTPCM boxes, tubes or containers; an insulated chamber surrounding the plurality of LTPCM boxes, tubes and / or containers, capable of thermally protecting the respective surfaces of the plurality of LTPCM boxes, tubes and / or containers from the local ambient temperature and heat of the system; an insulated arrangement of stacking and air pocket spacing to separate the ambient or system temperature from the insulated chamber surrounding the plurality of LTPCM boxes, tubes and / or containers by a thermal difference of greater than 50 °C; a mechanical system to allow, inhibit or regulate the flow of atmospheric water vapor and / or atmospheric air into and / or out of the insulated chamber surrounding the plurality of LTPCM boxes, tubes and / or containers; a plurality of frost scrapers with timed and fixed scraping paths to remove the acquired frost from the frost collection areas of the LTPCM boxes, tubes and / or containers; a scraper drive mechanism outside the insulated chamber surrounding the plurality of LTPCM boxes, tubes and / or containers; a scraper armature to connect the plurality of frost scrapers inside the insulated chamber surrounding the plurality of LTPCM boxes, tubes and / or containers, and to connect the scraper drive mechanism to the outside of the insulated chamber surrounding the plurality of LTPCM boxes, tubes and / or containers; a timing method for the scraper to remove the collected frost when the deposited frost reaches a thickness of less than one millimeter on the collection surface of the LTPCM boxes, tubes and / or containers; a frost collection opening or mechanical port and a frost collection container or box to hold the scraped frost after it has been scraped off the collection surface of the LTPCM containers, tubes and / or containers; an interface between the high temperature side of the cooling system and the frost holding container or tank to melt the held frost into liquid water; and a thermally insulating arrangement of stacked and air pocket spaced insulation separating the frost holding container or tank temperature from the potentially greater than 50°C thermal differential between the insulated room surrounding the plurality of LTPCM tanks, tubes and / or containers.

2. The system of claim 1, wherein, the cooling system is a refrigerant cooling cycle comprising: a compressor; a temperature sensing switch connected to the LTPCM volume to control the "on" / "off state of the compressor; a condensing unit connected to the compressor; a plurality of expansion devices connected at one end to the condensing unit and at the other end to a plurality of evaporator coil heat exchangers embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container; a suction line connected at one end to the plurality of evaporator coil heat exchangers embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container and at the other end to the compressor; and a refrigerant working fluid within the closed loop of the refrigerant cooling cycle system.

3. The system of claim 2 wherein: the plurality of expansion devices are capillary tubes that are also embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container.

4. The system of claim 2 wherein: the plurality of liquid lines have ends connected at one end to the condensing unit and at the other end to the plurality of capillary tubes and are embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container.

5. The system of claim 1 or 4 wherein: one or more valves are inline connected between the unencapsulated ends of the liquid lines attached to the condensing unit and to the other ends of the liquid lines embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container; wherein the one or more valves are closed prior to the compressor "off to evacuate all refrigerant from the plurality of evaporator coils embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container, preventing static heat of the refrigerant cooling cycle from adversely affecting the LTPCM temperature; and wherein the one or more valves are opened only after the compressor is turned back "on" to maintain the evacuated state of all refrigerant from the plurality of evaporator coils embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container, maintaining the compressor to produce the working of the high and low pressure sides of the refrigerant cooling cycle.

6. The system of claim 4 wherein: one or more valves are inline connected between the unencapsulated ends of the suction line attached to the compressor and to the other ends of the evaporator coil lines embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container; the one or more valves are closed prior to the compressor "off to evacuate all refrigerant from the plurality of evaporator coil heat exchangers embedded, immersed and / or encapsulated by the LTPCM within each LTPCM tank, tube or container, preventing static heat from adversely affecting the LTPCM temperature; One or more of the valves are opened only after the compressor has turned back "on" to maintain the evacuated state of all refrigerant within the multiple evaporator coils of the LTPCMs embedded, immersed and / or encapsulated within the individual LTPCM boxes, tubes or vessels, maintaining the operation of the high and low pressure sides of the refrigerant cooling cycle produced by the compressor.

7. The system of claim 2, wherein: The thermodynamic properties of the LTPCMs within the multiple LTPCM boxes, tubes or vessels are also selected to influence, stabilize and preserve the temperature and / or pressure of the refrigerant stream while moving within the multiple evaporator coils to reduce the energy requirements of the compressor.

8. The system of claim 1, wherein, The cooling system is a Stirling cooler cycle, comprising: a Stirling cooler; a cold head; a regenerator; and wherein the multiple evaporator coil heat exchangers of the system, with each individual evaporator coil embedded, immersed and / or encapsulated within an individual LTPCM box, tube or vessel, is a closed loop, filled with hot working fluid and connected to the cold head of the Stirling cooler.

9. The system of claim 1, wherein, The cooling system is a thermoelectric cooler cycle, comprising: a thermoelectric module cooler with its "hot" side connected to a heat sink; the "cold" side of the thermoelectric module cooler connected to a cooling manifold; and wherein the multiple evaporator coil heat exchangers of the system, with each individual evaporator coil embedded, immersed and / or encapsulated within an individual LTPCM box, tube or vessel, is a closed loop, filled with hot working fluid and connected to the cooling manifold.

10. The system of claim 1, wherein, The cooling system is an electro-acoustic transducer cycle, comprising: an electro-acoustic transducer; a resonator; a regenerator; a cryogenic heat exchanger, and wherein the multiple evaporator coil heat exchangers of the system, with each individual evaporator coil embedded, immersed and / or encapsulated within an individual LTPCM box, tube or vessel, is a closed loop, filled with hot working fluid and connected to the cryogenic heat exchanger.

11. The system of claim 1, wherein: The thermal energy from the water deposition process is conducted through the surfaces of the multiple LTPCM boxes, tubes or vessels, through the individual LTPCM blocks, through the evaporator coils into the working fluid stream of the cooling system, and ultimately exhausted from the cooling system into the contained mass of high temperature phase change material, HTPCM, and delivered as useful energy to the individual or auxiliary heating cycle system.

Images