WO2018013562A1

WO2018013562A1 - Systems, methods and/or apparatus to transport, harvest and/or store thermal energy

Info

Publication number: WO2018013562A1
Application number: PCT/US2017/041530
Authority: WO
Inventors: Daniel Stewart Lang
Original assignee: Electron Holding, Llc
Priority date: 2016-07-11
Filing date: 2017-07-11
Publication date: 2018-01-18

Abstract

The present disclosure is directed to methods, devices and/or systems for harvesting, transporting, storing and/or using acquired thermal energy to increase efficiencies of the system, another system and/or one or more components of one or more systems.

Description

SYSTEMS, METHODS AND / OR APPARATUS TO TRANSPORT, HARVEST

AND/OR STORE THERMAL ENERGY

CROSS-REFERENCE TO RELATED APPLICATIONS

[0001] This application claims priority to U.S. Provisional Application No.

62/360,782, filed on July 11, 2016. The contents of this priority application are herein incorporated by reference in its entirety.

[0002] This application is also related to U.S. Provisional Application No.

61/413,995, filed on November 16, 2010; U.S. Provisional Patent Application No. 61/532, 104, filed on September 8, 2011; PCT/US2012/065170, filed on November 15, 2012; and

PCT/US2012/065174, filed on November 15, 2012. All of these related applications are herein incorporated by reference in their entirety.

FIELD

[0003] This disclosure generally relates to the conservation of harvested thermal energy. This disclosure is also generally related to the use of harvested thermal energy to decrease the generated energy requirements for a wide variety of applications, systems, products, devices and/or components including, for example, Heating, Ventilation, Air Conditioning and Refrigeration (HVACR) systems.

BACKGROUND

[0004] Many systems, products, devices and components used today are designed to accommodate undesirable heat that is generated as a byproduct of high heat flux density and/or environmental heat. Because of such design accommodations, the rejection of unwanted heat adds an embedded cost to goods and services delivered.

[0005] In some products, thermal management adds extra size, weight and components to the overall package, increasing the final product and installation cost. In other cases, for example in the semiconductor industry, inadequate thermal rejection may degrade the overall device performance and may reduce the device's lifespan of usefulness. Further, in certain industries and applications, such as computing, data storage or solid-state lighting, added costs of manufacturing, shipping, maintenance, and a reduced lifespan, may be attributable to the required thermal management systems that are often added to remove the heat generated from the products and/or processes.

[0006] There are certain sectors, such as the Heating, Ventilation, Air Conditioning and Refrigeration (HVACR) sector and the electrical power generation sector, where the focus may be on one of more of the injection or rejection of heat into or out of specific environments such as homes, businesses, food storage and transportation; or consuming a large portion of the total energy supply for that environment in the case of e.g., an HVACR system or to maintaining and/or boosting heat in areas of the power generation process to enhance generation output while in other areas of the process heat may cause a reduction of power generation in the case of e.g., an electrical power generation system.

[0007] There are numerous thermal management methods currently employed to transport heat. Some common examples are: heat spreaders, heat sinks, fans, heat pipes, heat exchangers, the refrigeration cycle, and/or different combinations of these methods. However, these methods generally fall short of increasing energy efficiency and/or extending the life of the system because their primary function and purpose, in most cases, is to dump the unwanted heat at the nearest opportunity or to employ another process in the overall system to address the waste heat.

[0008] Accordingly, there is a need for improved systems, devices and/or methods to harvest and transport heat more efficiently and effectively in order to reduce overall energy consumption. Additionally, because much of heat generation is a derivative of process inefficiencies of components in systems, there is a need for improved systems, devices, and/or methods to store derived heat (thermal energy) so the thermal energy may be used and/or converted into other energy forms, (e.g. mechanical or electrical), to improve overall system energy efficiencies and/or extend system life. The present disclosure is directed to overcoming and/or ameliorating at least one of the disadvantages of the prior art.

SUMMARY

[0009] Exemplary embodiments described herein may relate to the harvest, transport, storage and/or conversion of heat (also referred to as thermal energy) acquired from various sources. In exemplary embodiments, the thermal energy may be available on demand and/or at desired temperatures for use to replace or offset other energy needs. For example, the thermal energy rejected from a refrigerator and/or freezer may be used to maintain pre-heat temperatures in a nearby oven, thereby reducing both cooking energy needs and, on hot days, air conditioning energy needs.

[0010] In exemplary embodiments, the acquired thermal energy may be transported and/or stored and therefore made available on demand at a user's desired location. For example, in exemplary embodiments, the systems, methods and/or devices may eliminate or reduce the need for distributed heating fuels.

[0011] In exemplary embodiments, the acquired thermal energy may be stored at various temperatures and/or stored in various materials, at various pressures and/or material phases (e.g. solid, liquid, gas, or plasma).

[0012] In exemplary embodiments, the acquired thermal energy may be transported and/or stored, and therefore made available at a desired location for conversion into other energies (e.g., kinetic or electrical energy) to reduce or eliminate other types of energy usage. For example, in exemplary embodiments, the systems, methods and/or devices may eliminate or reduce the need for a building's demand for distributed electrical energy.

[0013] In exemplary embodiments, the acquired thermal energy may be used to maintain or increase the temperature of a fluid (e.g., water, glycerine, or solvents). For example, the systems, methods and/or devices may eliminate or reduce the need for a building's demand for distributed heating fuel.

[0014] In exemplary embodiments, the acquired thermal energy may be used to maintain or increase the temperature of fluids and/or solids to remove or eliminate unwanted elements. For example, the systems, methods and/or devices may eliminate or reduce the need for distributed heating fuels in waste management or filtering applications.

[0015] In exemplary embodiments, the acquired thermal energy may be used to maintain or increase the temperature, and thereby the pressure, of a working fluid or gas of a system. For example, the systems, methods and/or devices may be used to drive a turbine connected to a generator to provide electrical power (AC or DC). For example, the systems, methods and/or devices may be used to reduce the energy requirements of compressor motors. For example, the systems, methods and/or devices may be used to reduce the energy

requirements of pumps. [0016] In exemplary embodiments, the acquired thermal energy may be used to maintain or increase the temperature of a gas. For example, the systems, methods and/or devices may be used to provide or supplement heating of indoor, ambient air.

[0017] In exemplary embodiments, the acquired thermal energy may be used to evaporate the working fluid that drives an Organic Rankine cycle turbine connected to a generator to provide electrical power (AC or DC).

[0018] In exemplary embodiments, the acquired thermal energy may be used to release water vapor from the desiccant material in dehumidification systems.

[0019] In exemplary embodiments, the acquired thermal energy may be used to drop the voltage requirements of current-driven electrical components and thereby reduce that component's power (wattage) requirements under Ohms Law that states; R = V/ 1. Additionally, in exemplary embodiments, the acquired thermal energy may be used as the energy source for thermophotovoltaic systems, designed to convert thermally radiated photons into electrical current and thereby reduce that components power (wattage) requirements.

[0020] In exemplary embodiments, the acquired thermal energy may be converted to kinetic energy (e.g., rotating or linear motion).

[0021] In exemplary embodiments, the acquired thermal energy may be used to induce a phase change of a material.

[0022] In exemplary embodiments, the acquired thermal energy may be used to heat or assist in heating magnetized antiferromagnetic materials above the Neel temperature.

[0023] In exemplary embodiments, the acquired thermal energy may be used to heat or assist in heating magnetized ferromagnetic materials above the Curie temperature.

[0024] In exemplary embodiments, the acquired thermal energy may be used to heat or assist in heating nitinol to effect martensitic transformation to produce mechanical work.

[0025] In exemplary embodiments, the thermal energy may be harvested from passive solar radiation. For example, the systems, methods and/or devices may employ solar thermal collectors (e.g., flat panel collectors, evacuated tube collectors, or parabolic trough collectors).

[0026] In exemplary embodiments, the thermal energy may be harvested from the condensing coils of HVACR systems or from other materials in thermal contact with the evaporation coils of HVACR systems. [0027] In exemplary embodiments, the thermal energy may be harvested from high heat-flux density semiconductors and other electronic components in devices (e.g., processors, LEDs, transistors, transformers, electromagnets).

[0028] In exemplary embodiments, the thermal energy may be harvested from manufacturing process heat systems.

[0029] In exemplary embodiments, the thermal energy may be harvested from machines converting energy contained in fuels to do mechanical work or to generate electrical energy.

[0030] In exemplary embodiments, the thermal energy may be harvested from other types of anthropogenic heat (i.e., heat generated by humans or human activity).

[0031] In exemplary embodiments, thermal energy may be more rapidly transported, away from thermally sensitive components via a thermally remote thermally conductive channel, by spreading and dissipating the thermal energy two dimensionally across a nano/micro material layer (e.g., graphene, phosphene, diamond powder).

[0032] In exemplary embodiments, the thermal energy transport may be contained, or substantially contained, by directing thermal energy conductance through a thermally conductive material in at least a first direction while blocking thermal energy conductance in at least a second direction using, for example, nano or micro interfacial thermal resistance layers as the boundary of a desired conduction path. For example, exemplary embodiments may use a nano layer of bismuth in physical contact with a nano layer of hydrogen-terminated diamond to cause a directional thermal barrier at the interface of these two nano layers due to the thermal conductance mismatch of bismuth and that of hydrogen -terminated diamond.

[0033] In exemplary embodiments, the thermal energy transport rate may be controlled, substantially controlled, or partially controlled by expanded surface area diffusion employing, for example, materials such as metallic foam or mesh.

[0034] In exemplary embodiments, the thermal energy transport may be controlled, substantially controlled or partially controlled by expanded surface area diffusion employing a three dimensional granular mass of micro/nano materials such as graphite, diamond, other thermally conductive granules or combinations thereof.

[0035] In exemplary embodiments, the thermal energy transport may be controlled, substantially controlled or partially controlled by expanded surface area diffusion employing metallic foam embedded in a granular mass, mesh embedded in a granular mass or combinations thereof.

[0036] In exemplary embodiments, the thermal energy may be transported via a working fluid of a heat pipe or a refrigeration cycle.

[0037] In exemplary embodiments, the thermal energy may be transported via the expansion coil and/or the condensing coil of a refrigeration cycle, wherein the thermal storage material also acts as a thermal stabilizer and insulator to the respective coil.

[0038] In exemplary embodiments, thermal energy may be transported into or out of a capillary tube, using thermoelectric modules or by embedment or partial embedment into a PCM storage vessel at specific temperatures and/or temperature ranges.

[0039] In exemplary embodiments, the thermal energy may be transported via a thermoelectric device.

[0040] In exemplary embodiments, the thermal energy may be transported passively, during the lower outdoor temperature of a diurnal temperature cycle.

[0041] In exemplary embodiments, the thermal energy may be transported to a secondary storage device to prevent thermal saturation of the primary storage device.

[0042] In exemplary embodiments, the thermal energy may be stored in organic phase change material(s) and/or other types of phase change materials (i.e., PCMs).

[0043] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of HVACR systems may comprise: a compressor, a fan and a condensing coil with one end of the condensing coil connected to a discharge port of the compressor; an evaporation coil embedded in a volume of a Low Temperature Phase Change Material (PCM) with one end of the evaporation coil connected to a suction port of the compressor; one or more thermoelectric modules in thermal contact with a capillary coil in-line between the condensing coil and the evaporation coil; a volume of working fluid in the coils' closed-loop; a temperature-sensing switch connected to the PCM volume to control the on/off state of the compressor; and a cold air exchanger substantially thermally isolated from the evaporation coil but in thermal contact with the Low Temperature PCM volume.

[0044] In exemplary embodiments, a system for harvesting, transporting, storing, and/or using the acquired thermal energy to increase efficiencies of HVACR systems may comprise: a compressor; a condensing coil at least partially embedded in a volume of a High Temperature Phase Change Material (PCM) with one end of the condensing coil connected to a discharge port of the compressor; an evaporation coil at least partially embedded in a volume of a Low Temperature PCM with one end of the coil connected to a suction port of the compressor; one or more thermoelectric modules in thermal contact with a capillary coil in-line between the condensing coil and the evaporation coil; a volume of working fluid in the coils' closed-loop; temperature-sensing switches connected to the PCM volumes to control the on/off state of the compressor; a hot air exchanger substantially thermally isolated from the condensing coil and in thermal contact with the High Temperature PCM volume; and a cold air exchanger substantially thermally isolated from the evaporation coil but in thermal contact with the Low Temperature PCM volume.

[0045] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of HVACR systems may comprise: a compressor; a condensing coil at least partially embedded in a volume of a High Temperature Phase Change Material (PCM) with one end of the coil connected to a discharge port of the compressor; an evaporation coil at least partially embedded in a volume of a Low Temperature PCM with one end of the coil connected to a suction port of the compressor; one or more thermoelectric modules in thermal contact with an expansion valve in-line between the condensing coil and the evaporation coil; a volume of working fluid in the coils' closed-loop; temperature-sensing switches connected to the PCM volumes to control the on/off state of the compressor; a hot air exchanger substantially thermally isolated from the condensing coil and in thermal contact with the High Temperature PCM volume; and a cold air exchanger substantially thermally isolated from the evaporation coil and in thermal contact with the Low Temperature PCM volume.

[0046] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of HVACR systems may comprise: a compressor; a condensing coil embedded in a volume of a High Temperature Phase Change Material (PCM) with one end of the coil connected to a discharge port of the

compressor; an evaporation coil embedded in a volume of a Low Temperature PCM with one end of the coil connected to a suction port of the compressor; one or more thermoelectric modules in thermal contact to a capillary coil in-line between the condensing coil and the evaporation coil; a rejection loop coil and a heat exchanger located within the system or in proximity to the system which may be accessed by a working fluid through thermally controlled automatic valves; a volume of working fluid in the coil closed-loop; one or more temperature- sensing switches connected to the PCM volumes and/or other parts of the system to control the on/off state of the compressor and valve flow direction; a hot air exchanger substantially thermally isolated from the condensing coil and in thermal contact with the High Temperature PCM volume; a cold air exchanger substantially thermally isolated from the evaporation coil and in thermal contact with the Low Temperature PCM volume; and an exhaust port in-line with the rejection loop.

[0047] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of HVACR systems may comprise: a Stirling engine, a Stirling engine regenerator, a thermosiphon coil, including a volume of a working fluid within the coil, wherein the coil is embedded, at least in part, in a volume of a Low Temperature PCM; one or more thermoelectric chillers wherein one or more of the thermoelectric chillers has a cold side portion and a hot side portion; the cold side portion of the one or more thermoelectric chillers is in thermal contact with the Stirling engine regenerator and the hot side portion of the one or more thermoelectric chillers is in thermal contact with a High Temperature PCM volume; a rejection loop coil, a first portion of which is embedded in the High Temperature PCM volume and a second portion of which is in a heat exchanger; and a temperature-sensing switch connected to the High temperature PCM volume to control the on/off state of the Stirling engine.

[0048] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to generate electrical energy may comprise: a solar thermal collector; a compressor with a motor (AC or DC); one or more pressure relief valves, one of the one or more pressure relief valves connected to a suction port of the compressor and one of the one or more pressure relief valves connected to a discharge port of the compressor; and an expansion coil, including a volume of working fluid within the coil, embedded, at least in part, in a High Temperature PCM volume, with each end of the coil connected to one of the one or more pressure relief valves.

[0049] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to generate electrical energy may comprise: a rejection loop with a heat exchanger connected to a condensing coil of a system; a compressor with a motor (AC or DC); one or more pressure relief valves, one of the one or more pressure relief valves connected to a suction port of the compressor and one of the one or more pressure relief valves connected to a discharge port of the compressor; and an expansion coil, including a volume of working fluid within the coil, embedded, at least partially, in a High Temperature PCM volume, with each end of the coil connected to one of the one or more pressure relief valves. In certain embodiments, the system may be an HVACR system or a system that is HVACR like.

[0050] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to harvest atmospheric water vapor and convert the water vapor to liquid water may comprise: a compressor; a condensing coil, wherein the condensing coil is at least partially embedded in a volume of a High Temperature PCM and/or is at least partially located within a melting chamber, so a rejection loop coil may be at least partially submerged with accumulated frost and/or liquid water, with one end of the condensing coil connected to a discharge port of the compressor; an evaporation coil at least partially embedded in a volume of a Low Temperature PCM with one end of the evaporation coil connected to a suction port of the compressor; one or more thermoelectric modules in thermal contact to a capillary coil substantially in-line between the condensing coil and the evaporation coil; a volume of working fluid within the interconnected compressor, condensing coil, capillary coil, and evaporation coil (together, a closed-loop); a temperature-sensing switch connected to the Low Temperature PCM volume to control the on/off state of the compressor; a frost collection surface area, thermally isolated from the evaporation coil and in thermal contact both with the Low Temperature PCM volume and with environmental air containing some level of humidity; a frost remover; and an in-line water filter at the exit of the melting chamber.

[0051] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to harvest atmospheric water vapor and convert the water vapor to liquid water may comprise: a Stirling engine, a Stirling engine regenerator, a thermosiphon coil, including a volume of working fluid within the coil, wherein the coil is embedded, at least in part, in a volume of a Low Temperature PCM; one or more thermoelectric chillers wherein one or more of the thermoelectric chillers has a cold side portion and a hot side portion; the cold side portion of the one or more thermoelectric chillers is in thermal contact with the Stirling engine regenerator and the hot side portion of the one or more thermoelectric chillers is in thermal contact with a High Temperature PCM volume; a rejection loop coil, a first portion of that is embedded in the High Temperature PCM volume and a second portion of which is at least partially located within a melting chamber, so a rejection loop coil may be at least partially submerged with accumulated frost and/or liquid water; and a temperature-sensing switch connected to the Low temperature PCM volume to control the on/off state of the Stirling engine; a frost collection surface area, thermally isolated from the evaporation coil and in thermal contact both with the Low Temperature PCM volume and with environmental air containing some level of humidity; a frost remover; and an in-line water filter at the exit of the melting chamber.

[0052] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of water heating systems may comprise: a rejection loop with a heat exchanger connected to a condensing coil of a -system; and a closed loop coil at least partially embedded in a High Temperature PCM volume, with a volume of working fluid within the closed loop of the coils, with one side of the closed loop coil taking in heat from the heat exchanger and the other side of the closed loop coil delivering heat to a hot water tank. In certain embodiments, the closed loop coil may include one or more inline regulating valves and/or an in-line pump. In certain embodiments, the system may be an HVACR system or a system that is HVACR like.

[0053] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of water heating systems may comprise: a solar thermal collector; a closed loop coil embedded in a High Temperature PCM volume, with a volume of working fluid within the coil, with one side of the coil taking in heat from the solar thermal collector; and a PCM volume heat exchanger delivering heat to a hot water tank. In certain embodiments, the closed loop coil may include one or more in-line regulating valves and/or an in-line pump.

[0054] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of a drying system may comprise: a rejection loop with a heat exchanger connected to a condensing coil of a system; and a closed loop coil at least partially embedded in a High Temperature PCM volume, with a volume of working fluid within the closed loop coil, with one side of the closed loop coil taking in heat from a heat exchanger and the other side of the closed loop coil delivering heat to a dryer. In certain embodiments, the closed loop coil may include one or more in-line regulating valves and/or an in-line pump. In certain embodiments, the system may be an HVACR system or a system that is HVACR like.

[0055] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of an electronic system may comprise: a thermal transfer material of an electronic device; a thermally insulating substrate (e.g. plastic, glass, etc.) coated on one or more sides with a nano/micro layer of a thermal spreading material, attached to and spreading the heat emitted by the electronic device away from the electronic device; a thermal conductor thermally in communication with some portion of the thermal spreading material (relatively remote from the initial thermal transfer point of the electronic device); a thermal storage medium (e.g. PCM, metallic foam, granular mass, etc.) connected to the thermal conductor; a thermal interface material at least partially encapsulating the thermal storage medium; a thermal output conduit from the thermal storage medium to a second electronic device, whereby a portion of the thermal energy is delivered to reduce the voltage requirements of the second electronic device.

[0056] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of an electronic system may comprise: a thermal transfer material of an electronic device; a thermally insulating substrate (e.g. plastic, glass, etc.) coated on one or more sides with a nano/micro layer of a thermal spreading material attached to and spreading the heat emitted by the electronic device away from the electronic device; a thermal conductor thermally attached to some portion of the thermal spreading material (relatively remote from the initial thermal transfer point of the electronic device); a thermal storage medium (e.g. PCM, metallic foam, granular mass, etc.) connected to the thermal conductor; a thermal interface material at least partially encapsulating the thermal storage medium; a thermal output conduit from the thermal storage medium; and a thermal energy conversion device (e.g., thermoelectric, thermo-magnetic, thermomechanical, thermal actuators, etc.).

[0057] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to generate mechanical energy may comprise: a rejection loop with a heat exchanger connected to a condensing coil of a system; and a closed loop coil at least partially embedded in a High Temperature PCM volume, with a volume of working fluid within the closed loop coil, with one side of the closed loop coil taking in heat from the heat exchanger and the other side of the closed loop coil delivering heat to a

thermomechanical device (e.g., magnetized antiferromagnetic materials, magnetized

ferromagnetic materials, nitinol device, thermal actuators, Stirling engine, etc.). In certain embodiments, the system may be an HVACR system or a system that is HVACR like.

[0058] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to generate mechanical energy may comprise: a solar thermal collector; a closed loop coil at least partially embedded in a High Temperature PCM volume, and with a volume of working fluid within the closed loop coil, with one side of the closed loop coil taking in heat from the solar thermal collector; and a PCM volume heat exchanger delivering heat to a thermomechanical device (e.g., magnetized antiferromagnetic materials, magnetized ferromagnetic materials, nitinol device, thermal actuators, Stirling engine, etc.).

[0059] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to dehumidify indoor air may comprise: acquiring thermal energy from a condensing coil at least partially embedded in a High Temperature PCM volume, and thereby transferred and stored in that High Temperature PCM volume; a desiccant filter; and an exhaust system to the outdoor air. In certain embodiments, the system having the condensing coil may be a HVACR system or a system that is HVACR like. Air may be drawn in from outdoors or other volume of air through a duct with an in-line fan and directed through a heat exchanger, encapsulated by, and in thermal communication with a High Temperature PCM volume. The air traveling through the heat exchanger gains heat as it passes through and exits the heat exchanger. The now heated air may be accelerated by a second fan towards a saturated desiccant filter used to absorb humidity indoor air. As the hot air is forced through the desiccant filter water vapor contained within desiccant filter is forced out of the desiccant filter becoming a part of the air volume traveling onwards where it may eventually exit to the outdoor volume of air through a vent.

[0060] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to humidify indoor air may comprise: acquiring thermal energy from a condensing coil at least partially embedded in a High Temperature PCM volume, and thereby transferred and stored in that High Temperature PCM volume; a water source; a vaporizing chamber; and a delivery system of the generated water vapor to the indoor air. Air may be drawn in from a volume of indoor air through a duct with an in-line fan and directed through a heat exchanger, encapsulated by, and in thermal communication with a High Temperature PCM volume. The air traveling through the heat exchanger gains heat as it passes through and exits the heat exchanger where a water source pumps a mist of water into the heated air passing by the mister vaporizing and combining with the heated air flow. The now heated humid air exits the system and back into the indoor air volume. The cycle continues until a desired humidity level is achieved. In certain embodiments, the system having the condensing coil may be an HVACR system or a system that is HVACR like.

[0061] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to sanitize indoor air and also clean the filters for extended use may comprise: acquiring thermal energy from a condensing coil at least partially embedded in a High Temperature PCM volume, and thereby transferred and stored in that High Temperature PCM volume; a heating chamber, encapsulated by, and in thermal communication with a High Temperature PCM volume, with a volume of granulated micro carbon that may trap water vapor from humid air entering the system and/or be supplied an amount of water vapor from a separate source; a HEPA filter, in-line fans, an indoor air inlet, an indoor air outlet, an outdoor air inlet, and an outdoor exhaust port. To sanitize indoor air, air may be drawn in from a volume of indoor air through an indoor air inlet and into a duct by a first in-line fan and directed through a heat exchanger, encapsulated by, and in thermal communication with a High

Temperature PCM volume. The air traveling through the heat exchanger gains heat as it passes through and exits the heat exchanger where it is pushed through a HEPA filter, removing unwanted particulates and then through a volume of granulated micro carbon, that may be also be heated to a much higher temperature, stripping the air flow it of some amount of water vapor while sterilizing the remaining water vapor within the airflow as it passes through the heated volume of granulated micro carbon. The now heated, filtered and sanitized air may be accelerated by a second reversible fan and pushed through the duct and an indoor air outlet back into the indoor volume. This process continues until a desired level of sanitization is achieved to the indoor air. To clean the filters of the system outdoor air may be drawn by a third inline fan within a duct through an outdoor air inlet where it is directed to be pushed through, in the opposite direction, the heated volume of granulated micro carbon, still containing the water vapor acquired through the sterilization cycle and then also pulled through the HEPA filter, now as a heated steam, by a fourth in-line fan dislodging the particulates lodged into the HEPA filter and carrying them to the outdoor air through an outdoor exhaust outlet. In certain exemplary embodiments, other filter types may be used, either alone or in addition to the HEPA filter. For example, a UV filter may be added to filter biological elements. In certain embodiments, the system having the condensing coil may be an HVACR system or a system that is HVACR like.

[0062] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to purify waste water may comprise: acquired thermal energy from a condensing coil at least partially embedded in a High Temperature PCM volume and thereby transferred and stored in that High Temperature PCM volume; one or more heating chambers in thermal communication with a High Temperature PCM volume, having a designed volume, or if more than one each heating chamber having a designed volume, of specific granulated filtration absorbers( i.e., carbon, germanium, lithium, calcium, etc.) relative to the specific element to be removed from the water as it is pumped under pressure by a water pump. Certain exemplary embodiments may also include a UV filtration chamber. In certain embodiments, the system having the condensing coil may be an HVACR system or a system that is HVACR like.

[0063] In exemplary embodiments, a system for harvesting, transporting, storing and/or using the acquired thermal energy to purify water may comprise the same or partially the same components as the previous exemplary embodiment, however, the acquired thermal energy may be from a solar thermal collection system instead of or in combination with a condensing coil from an HVACR system or a system that is HVACR like.

[0064] As well as the embodiments discussed in the summary, other embodiments are disclosed in the specification, drawings, and claims. The summary is not meant to cover each and every embodiment, combination, or variation contemplated for the present disclosure.

DESCRIPTION OF THE DRAWINGS

[0065] Exemplary embodiments will now be described, by way of example only, with reference to the accompanying drawings in which: [0066] FIG. 1 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0067] FIG. 2 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0068] FIG. 3 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0069] FIG. 4 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0070] FIG. 5 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle as applied to an HVAC in cooling mode.

[0071] FIG. 6 is a schematic drawing of the exemplary embodiment of FIG. 5, wherein the HVAC is in a heating mode.

[0072] FIG. 7 is a schematic drawing of the exemplary embodiment of FIG. 5, wherein the HVAC is in an exhaust mode.

[0073] FIG. 8 is a three-dimensional graphic representation of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle as applied to HVAC.

[0074] FIG. 9 is a cross-sectional view of the exemplary embodiment of an HVAC system described in FIG. 8.

[0075] FIG. 10 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0076] FIG. 11 is a schematic drawing of the exemplary embodiment of FIG. 10, except described in thermal purge mode. [0077] FIG. 12 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0078] FIG. 13 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0079] FIG. 14 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0080] FIG. 15 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0081] FIG. 16 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle.

[0082] FIG. 17 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy of the refrigeration cycle to convert the thermal energy into electrical energy.

[0083] FIG. 18 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy of the refrigeration cycle to convert the thermal energy into electrical energy.

[0084] FIG. 19 is a schematic drawing of an exemplary embodiment of a system to harvest, transport, store, and use solar radiation for electrical energy generation.

[0085] FIG. 20 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle when used to collect atmospheric water vapor and convert the water vapor to water.

[0086] FIG. 21 is a schematic drawing of an exemplary embodiment of a system to harvest, transport, store and use solar radiation for electrical energy generation. [0087] FIG. 22 is a schematic drawing of a commonly known method for transporting unwanted thermal energy away from the component generating it.

[0088] FIG. 23 is a schematic drawing of an exemplary embodiment of a system to transport unwanted thermal energy away from the component generating it.

[0089] FIG. 24 is a schematic drawing of an exemplary embodiment of a system to transport unwanted thermal energy away from the component generating it.

[0090] FIG. 25 is a schematic drawing of an exemplary embodiment of a system to transport unwanted thermal energy away from the component generating it.

DETAILED DESCRIPTION

[0091] Exemplary embodiments described herein are directed to reducing a system's energy consumption by using waste heat ("thermal energy") that has been generated by the system or another system in order to perform some work function and/or work process in the system or in another system. The waste energy may be harvested, transported, stored and/or used as disclosed herein.

[0092] Exemplary embodiments described herein are directed to reducing a component's energy consumption by using the thermal energy generated by a component that is typically wasted, to do work on the component generating the thermal energy or another nearby component that would benefit by the addition of thermal energy. The waste energy may be harvested, transported, stored and/or used as disclosed herein.

[0093] Exemplary embodiments are directed to the transport, harvest, storage and/or use of thermal energy, (for example, waste heat, from numerous system sources and/or components), to decrease a device's, a component's and/or a system's energy consumption. Solar thermal energy may also be used to supplement a device's, a component's and/or a system's energy requirements. The exemplary embodiments described herein may be beneficial for the natural and built environments as well as for economic reasons. In exemplary

embodiments, the systems, methods and/or devices may eliminate or reduce the need for external electricity transmission into the system or the environment, at least for certain applications. In exemplary embodiments, the thermal energy may be stored. In other exemplary embodiments, the thermal energy may be stored and may be transported to another location. In exemplary embodiments, the system may include a biodegradable organic phase change material, for storing the thermal energy. One advantage of certain embodiments is a reduction in the accumulation of consumable waste products subsequent to disposal (e.g., biodegradable PCMs in contrast to a system that uses PCMs that are not biodegradable). Another advantage of certain embodiments is that the system is configured to minimize the number of phase change cycle events undergone by a PCM in contrast to more typical applications of PCMs. This may be in part because, rather than using the latent energy of the PCM as a high frequency thermal exchange mechanism, the system uses the latent energy of the PCM as a low frequency thermal barrier. Since the PCM' s phase cycling may be less frequent, replacement of consumable PCMs in a system may be reduced or substantially eliminated over the lifecycle of the system.

[0094] In certain embodiments, systems, methods and/or devices may provide, for one or more of the following: comfort heating, comfort cooling, hot water heating, refrigeration, water harvesting, electrical energy generation, electromagnetic radiation generation,

humidifying, dehumidifying, material composition, material decomposition, wherein such embodiments may be partially, substantially, or completely independent of electrical grid energy and/or fossil fuels. Certain embodiments may be at least 10% or as much as 100% independent of electric grid energy and/or fossil fuels. Certain embodiments may be at least 20%, 40%, 50%, 60%), 75%), 85%), 90%), 95%, or 99% independent of the electric grid energy and/or fossil fuels. Certain embodiments may be between 20% to 99%, 20% to 40%, 10% to 30%, 20% to 50%, 40% to 99%, 50% to 100%, 70% to 95%, 65% to 100%, 80% to 95%, 80% to 100%, 90% to 99%) or 90%) to 100% independent of the electric grid energy and/or fossil fuels. Certain embodiments may produce additional energy over and above the required energy to maintain the system that may be used by other systems or devices. Certain embodiments may provide a return on investment in less than 3 months to no more than 10 years. In exemplary

embodiments, buildings or other structures may be retrofitted or built without the need of natural gas, or a reduced need of natural gas, that would otherwise be delivered for heating and/or cooking requirements. In certain embodiments, this could be done at a cost that is at least 10% or as much as 99% less than that of conventional methods. In certain embodiments, buildings or other structures may be retrofitted or built wherein at least 10% or as much as 100% of the natural gas used for providing heating and/or cooking requirements may be eliminated. In certain embodiments, buildings or other structures may be retrofitted or built wherein at least 10%) or as much as 100%) of the natural gas used for providing heating and/or cooking requirements may be eliminated. Combinations of reducing the need for grid electricity, power plant generated electricity, fossil fuel generated power, and/or natural gas are also contemplated.

[0095] In certain embodiments, land vehicles may be manufactured and/or retrofitted to eliminate or reduce the use of fossil fuels or, on electric vehicles, the use of chemical batteries. Certain embodiments may reduce the need for fossil fuels and/or chemical batteries by at least 10% or as much as 100%. Certain embodiments may be at least 20%, 40%, 50%, 60%, 75%, 85%), 90%), 95%), and/or 99% independent of the electric grid energy and/or fossil fuels. Certain embodiments may be between 20% to 99%, 20% to 40%, 10% to 30%, 20% to 50%, 40% to 99%, 50% to 100%, 70% to 95%, 65% to 100%, 80% to 95%, 80% to 100%, 90% to 99% and/or 90% to 100%) independent of the electric grid energy and/or fossil fuels. Such systems, methods and/or devices may reduce the initial cost, the maintenance cost, and/or the recurring fuel cost associated with land vehicles.

[0096] In certain embodiments, marine vessels may be manufactured or retrofitted to eliminate or reduce the need for fossil fuels by at least 10% or as much as 100%, or in the case of electric marine vessels, to eliminate or reduce the need for chemical batteries and/or the electrical energy cost of recharging those batteries by at least 10% or as much as 100%. Certain embodiments may be at least 20%, 40%, 50%, 60%, 75%, 85%, 90%, 95%, and/or 99% independent of the electric grid energy and/or fossil fuels. Certain embodiments may be between 20% to 99%, 20% to 40%, 10% to 30%, 20% to 50%, 40% to 99%, 50% to 100%, 70% to 95%, 65% to 100%, 80% to 95%, 80% to 100%, 90% to 99% and/or 90% to 100% independent of the electric grid energy and/or fossil fuels. In certain embodiments, the associated cost of disposing of chemical batteries may be eliminated or reduced. In certain embodiments, building cost may be reduced, or substantially reduced, by the elimination, or reduction, of grid tie methods such as transformers and large gauge wiring. In certain embodiments, the size and cost of solar and/or wind energy generation systems may be reduced, or substantially reduced. Due to the efficiency of the thermal storage, the use of batteries and/or solar tracking systems may be eliminated or reduced, reducing the costs of photovoltaic energy generation. Additional advantages will be apparent to a person of ordinary skill in the art.

[0097] As used herein, the terms "first temperature" and "second temperature" indicate a comparison, wherein the first temperature is higher than the second temperature.

These terms may cover temperature ranges as well, wherein the "first temperature" and the "second temperature" cover temperature ranges, wherein the first temperature range is higher, or substantially higher, than the second temperature range. In certain embodiments, there may be a partial overlap of the first temperature range and the second temperature range. In certain embodiments, the overlap may be between 0% to 10%, 0% to 20%, 1% to 8%, 2% to 5%, 4% to 8%, 0.5% to 3%, 0% to 5%, 0% to 2%, etc. In certain embodiments, the "first temperature" may vary ± 0.5 %, ±1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%), or ± 200%). In certain embodiments, the "first temperature" may vary by at least ± 0.1%, ± 0.25%, ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%), ± 200%), etc. In certain embodiments the "first temperature" may vary by less than ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%), etc. In certain embodiments, the "second temperature" may vary by ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. In certain embodiments, the "second temperature" may vary by at least ± 0.1%, ± 0.25%, ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. In certain embodiments, the "second temperature" may vary by less than ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. Combinations of the variation in the "first temperature" and the "second temperature" are also possible in certain embodiments. In certain embodiments, there may also be additional temperatures such as a "third temperature," a "fourth temperature," etc. In certain embodiments, at least 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, or more temperature differences may be used.

[0098] Using the "first temperature" and "second temperature" as exemplary illustrations, this could mean a first temperature and a second temperature wherein both are greater (i.e., hotter) than a typical room temperature; a first temperature and a second

temperature wherein both are less (i.e., cooler) than a typical room temperature; or a first temperature and a second temperature wherein the first temperature is greater than a typical room temperature and the second temperature is less than a typical room temperature. As used herein, the terms "high temperature" and "low temperature" are also used in terms of a comparison where the high temperature is greater than the low temperature. As used herein, the terms "higher temperature and "lower temperature" also are used in terms of a comparison where the higher temperature is greater than the lower temperature. [0099] As used herein, the terms a "first pressure" and a "second pressure" are used in terms of a comparison wherein the first pressure is higher than the second pressure. These terms also may cover pressure ranges as well, wherein the "first pressure" and the "second pressure" cover pressure ranges and wherein the first range is higher, or substantially higher, then the second pressure range. In certain embodiments, there may be a partial overlap of the first pressure range and the second pressure range. In certain embodiments, the overlap may be between 0% to 10%, 0% to 20%, 1% to 8%, 2% to 5%, 4% to 8%, 0.5% to 3%, 0% to 5%, 0% to 2%), etc. In certain embodiments the "first pressure" may vary ± 0.5 %, ± ±1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, or ± 200%. In certain embodiments the "first pressure" may vary by at least ± 0.1%, ± 0.25%, ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. In certain embodiments, the "first pressure" may vary by less than ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. In certain embodiments, the "second pressure" may vary by ± 0.1%, ± 0.25%, ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. In certain embodiments, the "second pressure" may vary by at least ± 0.1%, ± 0.25%, ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. In certain embodiments, the "second pressure" may vary by less than ± 0.1%, ± 0.25%, ± 0.5%, ± 1%, ± 5%, ± 10%, ± 20%, ± 40%, ± 50%, ± 60%, ± 80%, ± 100%, ± 125%, ± 150%, ± 200%, etc. Combinations of the variation in the "first pressure" and the "second pressure" are also possible. In certain embodiments, there may also be additional pressures such as a "third pressure," a "fourth pressure" etc. In certain embodiments, at least 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, or more pressure differences may be used.

[00100] Using the "first pressure" and "second pressure" as exemplary illustrations, this could mean a first pressure and a second pressure wherein both are higher than local atmospheric pressure; a first pressure and a second pressure wherein both are lower than local atmospheric pressure; or a first pressure and a second pressure wherein the first pressure is greater than local atmospheric pressure and the second pressure is less than local atmospheric pressure. As used herein, the terms "high pressure" and "low pressure" are also used in terms of a comparison where the high pressure is greater than the low pressure. As used herein, the terms "higher pressure" and "lower pressure" also are used in terms of a comparison where the higher pressure is greater than the lower pressure.

[00101] Certain embodiments are directed to systems that use a substantial proportion, or at least a portion, of harvested and stored, high temperature thermal energy to raise the pressure level of the working fluid of a system, reducing the workload of the system's compressor or pump. Certain embodiments are directed to systems that use a substantial portion, or at least a portion, of the harvested and stored, low temperature thermal energy to drop the pressure level of the working fluid of a system, reducing the workload the system's compressor or pump. Certain embodiments are directed to systems that use ambient thermal differences that are available to a system to raise and/or lower working fluid pressure levels at different points of the working fluid's cycle. Certain embodiments are directed to systems that cause thermal differences by maintaining both high and low stored temperatures that are employed to assist in maintaining beneficial working fluid pressure level at different locations of the refrigeration cycle. For example, if a system can optimize its working fluid pressures by taking advantage of the high temperature thermal energy of the system's condensing coil to raise the pressure of the working fluid within the condensing coil and by using the low temperature thermal energy of the system's evaporation coil to drop the pressure of the working fluid within the evaporation coil, in a manner that also moderates and/or stabilizes the temperature ranges of the working fluid while in the respective coils of the refrigeration cycle during system operation, then the system's compressor or pump may operate more efficiently, using substantially less electrical energy and under reduced mechanical stress, thus extending compressor or pump operating life. Certain embodiments are directed to systems that use working fluids to absorb or reject thermal energy where potential energy is caused or used by pumps. As used herein, the terms pump,

compressor, turbine and/or any other thermodynamic heat engine may be used interchangeably.

[00102] Certain embodiments are directed to systems that use designable thermal storage masses to reduce the energy requirements of the compressor that drives the working fluid of the system's refrigeration cycle. The designable thermal storage masses may encapsulate, substantially encapsulate, or partially encapsulate the condensing and/or evaporator coils. For example, using thermal masses with higher densities and higher thermal conductivity than air as thermal transport rate moderators between the working fluid of the closed loop of the

refrigeration cycle and the thermal exchangers interacting with the air of the environment to be tempered, the system may more efficiently utilize the high frequency thermal transport effort of the refrigeration cycle. Certain embodiments are directed to systems that use phase change materials as the thermal storage mass, using the phase change properties of the materials as a thermal barrier by which to minimize (i) the range of work the compressor is subjected to by the system per operating cycle, (ii) the duration of the compressor operating cycle, and (iii) the number of compressor operating cycles per time period. Further, by severely restricting and limiting the phase change material's number of phase cycles per time period, the system subjects the system's working fluid of the refrigeration cycle to designed temperature ranges of the PCM storage rather than to the substantially larger latent heat energies released during repeated and frequent phase changes of phase change materials. The desired PCM temperature ranges may be achieved by limiting the thermal energy added or reduced to a PCM mass, to that of specific heat capacity or heat capacity range, either above or below the PCM's phase change temperature, within a defined temperature range of the PCM.

[00103] In exemplary embodiments, the phase change material may be a material or combination of materials that achieves and maintains the desired or acceptable temperature, temperatures, or temperature range. The phase change materials may be formulations derived from petroleum products, salts, water, or combinations thereof. For example, water, water-based salt hydrates, various forms of paraffins, fatty acids and esters, trimethylolethane, organic thermal salts, inorganic thermal salts, ionic liquids, thermal composites, vegetable-based fats or oils, or combinations thereof. The type of, and/or temperature specific phase change material used the disclosed in embodiments may vary even for the same embodiment used under different environmental or other conditions. PCM's limited in a specific thermal attribute, such as to degrade after 20 phase change cycles, for example, may exhibit other thermal attributes superior to another PCM, for example one that degrades after 2,000 phase change cycles, such as containment methods, density, specific heat capacity and/or latent heat capacities or other attributes, that more than compensates for the PCM's limited attribute.

[00104] A phase change material is a material that uses phase changes (e.g., solidifies, liquefies, evaporates, and/or condenses) to absorb or release large amounts of latent heat at a specific temperature. Phase change materials may leverage latent heat to help maintain a product's temperature for extended periods of time. In exemplary embodiments, the phase change material may be manufactured from renewable resources, such as with natural vegetable

's- based phase change materials. For example, in exemplary embodiments, the phase change materials may be a type manufactured by Entropy Solutions and sold under the name PureTemp. For example, PureTemp PT 133 and PT -21 may be used in combination, wherein PT 133 serves as the higher temperature phase change material used for storing thermal energy and PT -21 serves as the lower temperature phase change material used for absorbing thermal energy.

Another example would be using PureTemp PT 48 and PT 23 wherein PT 48 serves as the higher temperature phase change material used for storing thermal energy and PT 23 serves as the lower temperature phase change material used for absorbing thermal energy.

[00105] In certain embodiments, phase change materials can be used in numerous applications, so a variety of containment methods for the phase change materials may be employed, such as micro-encapsulation (e.g., 10 to 1000 microns, 80-85% core utilization for example, 25, 50, 100, 200, 500, 700, 1000 microns, etc.), macro encapsulation (e.g., 1000+ microns, 80-85% core utilization, for example, 1000, 1500, 2000, 2500, 300, 4000, 5000+ microns etc.), flexible films, metals, rigid panels, spheres and other containment methods.

[00106] In certain embodiments, the number of thermal cycles that the phase change material may go through and still perform in a suitable manner may be at least 400, 1,000, 3,000, 5,000, 10,000, 30,000, 50,000, 75,000 and/or 100,000 thermal cycles. In certain embodiments, the number of cycles that the phase change material may go through and still perform in a suitable manner may be between 400 and 100,000, 5000 and 20,000, 10,000 and 50,000, 400 and 2000, 20,000 and 40,000, 50,000 and 75,000, or 55,000 and 65,000 thermal cycles. For example, PureTemp organic phase change material has been reported by the manufacturer to retain peak performance through more than 60,000 thermal cycles. In other embodiments, the number of thermal cycles that the phase change material may go through may be intentionally limited, to use the phase change temperature as a thermal barrier. Certain embodiments may control the amount of thermal energy stored in the phase change material volume, by controlling the amount of thermal energy added to or subtracted from the phase change material while maintaining the phase change material mass some number of degrees below or above its phase change temperature. For example, a thermal storage mass for cooling purposes may use a phase change material with a liquid-to-solid phase change temperature of -21°C; however, the system may maintain, for long periods of time, the phase change material's temperature range between -55°C to -22°C. By not allowing the phase change material to phase back to a liquid (i.e., to achieve a temperature above -21°C) the system beneficially conserves the energy the system had to use to initially cool the PCM from ambient temperature to below its phase change point of -21°C. This is an example of how the system beneficially exploits the attribute of a PCM to remain "in phase" (in this case as a solid) through a broad range of relevant temperatures, so that the phase change material may serve as what may be termed a "thermal barrier," as opposed to employing a PCM perhaps more traditionally, that is, by exploiting its phase change properties to some effect through frequent phase change cycles. Conversely, a thermal storage mass for heating purposes may use a phase change material with a solid to liquid phase change temperature of 78°C; however, the system may maintain, for long periods of time, the phase change material's temperature range between 80°C to 110°C. By not allowing the phase change material to phase back to a solid (i.e., to achieve a temperature below 78°C), the system beneficially conserves energy the system had to use initially to heat the PCM from ambient temperature to above its phase change point of 78°C.

[00107] In exemplary embodiments, the temperature difference between the hot and cold phase change materials may be anywhere from a fraction of a degree to several hundred degrees, at least in part depending on the stored thermal energy's ultimate end use. In certain exemplary embodiments, only a single phase change material may be used to store acquired thermal energy, while in other exemplary embodiments two or more phase change materials may be used.

[00108] Certain embodiments are directed to systems that transport a substantial portion, or at least a portion of excess/waste thermal energy into a thermal storage mass, and when that thermal mass reaches a temperature higher than desired, the excess/waste thermal energy may be used beneficially for a secondary process of the system. Other embodiments are directed to systems that transport a substantial portion, or at least a portion of excess/waste thermal energy into a thermal storage mass, and when that thermal mass has reached a temperature higher than desired, an amount of the excess/waste thermal energy may be transported a different thermal mass partially comprising or serving a separate system, for example, hot water heating or clothes drying. Certain embodiments may exhaust the stored excess/waste thermal energy from the thermal storage mass to the outdoor environment.

[00109] Certain embodiments are directed to systems that use a substantial portion, or at least a portion, of the harvested and stored, high temperature thermal energy to raise and/or lower the pressure level of the working fluid in a system to perform mechanical work to operate an electrical generator. Certain embodiments are directed to systems that use a substantial portion, or at least a portion, of the harvested and stored, low temperature thermal energy to raise and/or lower the pressure level of the working fluid in a system to perform mechanical work to operate an electrical generator.

[00110] Certain embodiments are directed to systems that use a volume of granular materials, for example, granular graphite, as thermal transport regulators, directing and controlling the rate of thermal flow from a heat source to a thermal storage mass and/or within a PCM storage mass to increase or decrease the thermal conductivity of a PCM and/or from a thermal storage mass to another portion of the system that is either not adversely affected or may benefit from the thermal energy. Using various types, amounts, and/or grain sizes of granular material, certain parameters of the thermal transport may be designed for regulating thermal transport at least in part due to the thermal boundary resistance at granular interfaces. In certain embodiments, a volume of granular material, placed between separate thermal conductors, eliminates or reduces the need for heat sinks. Certain embodiments disclose one or more methods of thermal transport and/or thermal storage for use in a system, a plurality of systems, or a portion of a system based on: (i) the dimensions of the heat source, (ii) the dimensions of the thermal path, (iii) the density of the thermal path, (iv) the energy flux from the heat source, (v) other systems interacting with the system, the plurality of systems, or the portion of the system, (vi) the attributes of the environment that the system, the plurality of systems, or the portion of the system is operating within or interacting with, or (vii) combinations thereof.

[00111] FIG. 1 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needed of the refrigeration cycle. The exemplary embodiment of FIG. 1 is an improvement of a current refrigeration cycle, also known as a thermodynamic heat pump cycle. The current refrigeration cycle is described here first in order to adequately disclose the improvement and its advantages. In a current cycle, a circulating working fluid, typically a refrigerant enters a compressor 1 through the compressor's suction port 14 as a vapor in a direction of flow 4 as indicated. The compressor 1, powered by input energy 2, compresses the working fluid vapor, causing the vapor to become superheated as the vapor is pushed or discharged through the compressor's discharge port 3. The working fluid, now a superheated vapor, enters the condensing coil 5, where the "pumping action" of the compressor condenses the vapor into a liquid thereby causing the now liquid working fluid to reject heat, at near constant pressure and temperature, by conduction to an adjacent environment, through the walls of the condensing coil 5 the working fluid is contained within. The adjacent environment is commonly augmented with fans or another separate process to prevent overheating of the condensing coil and, ultimately, to prevent thermal saturation of the working fluid. The high pressure 8 acting upon the working fluid inside the condensing coil 5 is the result of the work of the compressor's 1 "pumping action" pushing working fluid into one end of the condensing coil 5 at a fast rate and a throttle, called an expansion device 9, located at the other end of the condensing coil 5 slowing the rate of the working fluid's exit from the condensing coil 5. The working fluid continues, now as a liquid, through a confined expansion device 9 and exits the expansion device 9 into a much less restricted area of the evaporation coil 11 connected to the other end of the expansion device 9. The evaporation coil's 11 pressure is significantly lower than that of both the condensing coil 5 expansion device 9 due to the compressor suction port 14 pulling working fluid back into the compressor 1 (the completion of a "working fluid cycle") at the opposite end of the evaporation coil 11 than the end connected to the expansion device 9 restricting the rate and amount at which the working fluid can enter the low pressure environment of the evaporation coil 11. The low pressure environment of the evaporation coil 11 causes an abrupt decrease of pressure on the working fluid entering the evaporation coil 11, resulting in flash evaporation and auto-refrigeration, of a portion of the working fluid that, in turn, results in a mixture of liquid and vapor at a lower temperature and pressure than prior to passing through the expansion device 9. The cold liquid-vapor mixture of the working fluid then travels through the evaporation coil and vaporizes, being "pulled" by the "pumping action" of the compressor 1, gaining additional heat via conduction from the adjacent environment through the walls of the evaporation coil 11. The resulting vaporized working fluid is pulled or sucked into the compressor suction port 14 to complete the thermodynamic cycle, this cycle repeating until the desired heating or cooling for the application is achieved.

[00112] In the exemplary embodiment described in FIG. 1, no components have been replaced or eliminated when compared to current systems employing the refrigeration cycle, as previously described, except for the elimination of the fan, or other separate process, used to augment the adjacent environment of the condensing coil. Further, the thermodynamic cycle of the exemplary embodiment described in FIG. 1 goes through the same, or similar, processes as compared to current systems used today. The exemplary embodiment of FIG. 1 is similar to current systems employing the refrigeration cycle, except the embodiment adds at least two additional components to the system to reduce the input energy 2 consumed by the compressor 1, thereby increasing overall system efficiency. The two additional components are: (i) a high temperature thermal storage mass 7 and, (ii) a low temperature thermal storage mass 12. Since the specific thermal mass materials to be used may be dependent on several application-specific factors, defining certain items is useful, as examples only, in order to describe and discuss the embodiment. Therefore, the application shall be defined to replace a split system HVAC

(specifically in cooling mode), the working fluid shall be defined as commodity R134a refrigerant, the compressor 1 shall be defined as a hermetically sealed reciprocating compressor, and the expansion device 9 shall be defined as a capillary coil. The high temperature thermal storage mass 7, in this example, is an Entropy Solutions PT 18 organic phase change material, and the low temperature thermal storage mass 12 is, in this example, an Entropy Solutions PT - 21 PCM. In this example, these PCM's are selected for at least the following reasons: (i) their respective thermal properties, (ii) their respective densities; (iii) their general commercial availability, and (iv) their low cost.

[00113] In the refrigeration cycle shown in FIG. 1, a circulating working fluid, R134a, enters the compressor 1 through the compressor's suction port 14 as a vapor in a direction of flow 4 as indicated. The compressor 1, powered by input energy 2, compresses the vapor, causing the vapor to become superheated vapor as the vapor is pushed or discharged out of the compressor's discharge port 3. The working fluid, now a superheated vapor, enters the condensing coil 5, where the "pumping action" of the compressor condenses the vapor into a liquid thereby causing the now liquid working fluid to reject heat, at near constant pressure and temperature, by conduction to the adjacent high temperature thermal storage mass 7 through the walls of the condensing coil 5. Encapsulation of the condensing coil 5, using a high temperature thermal storage mass, substantially eliminates or reduces the need to split the HVAC system into indoor and outdoor halves because the thermal properties of PT 18 are superior for absorbing the thermal energy and provide a controlled thermal rejection environment than that of the augmented outdoor air of current systems.

[00114] The addition of such thermal storage masses to current systems further enables the complete refrigeration cycle for comparably capable whole-house or whole-building "central" HVAC to be more optimally engineered by eliminating site specific variables that current system engineering typically needs to allow for. For example, current engineering practices for outdoor "split system" condensing units typically allows for broad variations of the working fluid's temperature and pressure while in the condensing coil to accommodate: (i) interacting with various broad, outdoor temperature gradients, (ii) unknown, site specific distances from the condensing coil to the expansion device, (iii) unknown actual volume of refrigerant in the system, (iv) unknown quality or completeness of insulation protecting the line from the condensing coil to the expansion device and, (v) potential substandard workmanship or site specific design by the installer. By encapsulating the condensing coil, as described in this disclosure, the complete refrigeration cycle may now be contained in a single unit, which may be mounted indoors. As a single, manufactured unit, temperature/pressure curves of the condensing coil during operation may be fixed, because the condensing coil interacts with a mass with well- defined thermal properties, carefully selected for and tailored to this specific part of the cycle and a specific application, but applicable across a variety of installations. Further, the distances from the condensing coil to the expansion device, the insulation quality and completeness, the volume of refrigerant in the system, as well as quality control as pertains to fabrication of the full refrigeration cycle may now be more controlled and more narrowly specified because these design and quality aspects may be undertaken at a factory with controlled tolerances rather than on a construction site by construction contractors on a location by location basis.

[00115] The addition of a high temperature thermal storage mass 7 material, such as PT 18, encapsulating at least a portion of the condensing coil 5, assists in stabilizing and/or maintaining temperatures and pressures of the working fluid within the condensing coil 5 even between working fluid operating cycles, therefore conserving a portion, or a substantial portion, of the work of the compressor performed in the previous cycle. For example, PT 18 is a phase change material with the properties, shown in Table 1, which when used to encapsulate at least a portion of the condensing coil provides stable and predictive temperatures and pressures of a refrigerant (such as R134a) as the refrigerant cycles through the condensing coil. One advantage of this exemplary embodiment is that the refrigerant operates in a stable and predictive temperature and pressure range. By using thermal storage materials to encapsulate at least a portion of the condensing coil, which materials have properties that are complementary to those of the refrigerant cycling within the condensing coil and, which are also capable of withstanding environmental and/or other thermally inconsistent conditions of air or other mediums a system may eliminate, reduce, and/or temper unwanted thermal variations from interacting with the refrigerant, thereby narrowing the temperature and pressure ranges of the refrigerant within the condensing coil, which reduces the work required of the compressor, that is, the work of compressing the refrigerant within the condensing coil. Moreover, narrowing the temperature and pressure ranges of the refrigerant within the condensing coil may also serve to reduce the amount of refrigerant volume and/or pressures in the system. In certain embodiments the reduction may be 20%, 40%, 50%, 60%, 75%, 85%, 90% and/or any percent reduction in between of refrigerant volume and/or pressure requirements in the system.

TABLE 1

PureTemp 18 Technical Information

PureTemp 18 is a USDA Certified Biobased product.

Melting point 18°C

Heat storage capacity 192 J/g

Thermal conductivity (liquid) 0.15 W/m² °C

Thermal conductivity (solid) 0.25 W/m² °C

Density (liquid) 0.86 g/ml

Density (solid) 0.86 g/ml

Specific heat (liquid) 1.74 J/g °C

Specific heat (solid) 1.47 J/g °C

[00116] System efficiency is improved as compared to a more conventional system that is designed to provide a comparable amount of heating and/or cooling. This improved efficiency is achieved by reducing the power demands of the compressor, since the work being done by the compressor is reduced, due at least in part to the reduced volume of working fluid that is used and/or the engineering of more precise refrigerant ranges to achieve optimum minimum/maximum thermal energy rejection.

[00117] Continuing through the refrigeration cycle, in the exemplary embodiment of FIG. 1, the working fluid, now a liquid, but because of the addition of high temperature thermal mass storage 7 encapsulating the condensing coil, is at a lower "high" pressure and lower "high" temperature than that of comparable current systems, exits the condensing coil 5, the high pressure 8 acting upon the working fluid inside the condensing coil 5 is the result of the work of the compressor's 1 "pumping action" pushing working fluid into one end of the condensing coil 5 at a fast rate and a throttle, called an expansion device 9, located at the other end of the condensing coil 5 slowing the rate of the working fluid's exit from the condensing coil 5. The working fluid continues, now as a liquid, through the confining expansion device 9 and exits the expansion device 9 into a much less restricted area of the evaporation coil 11, encapsulated in a low temperature thermal storage mass 13. The working fluid's entrance into the less confined area of the evaporation coil 11 connected to the other end of the expansion device 9. The evaporation coil's 11 pressure is significantly lower than that of both the condensing coil 5 expansion device 9 due to the compressor suction port 14 pulling working fluid back into the compressor 1 (the completion of a "working fluid cycle") at the opposite end of the evaporation coil 11 than the end connected to the expansion device 9 restricting the rate and amount at which the working fluid can enter the evaporation coil 11. The low pressure environment of the evaporation coil 11 causes a decrease (e.g., an abrupt decrease) of pressure on the working fluid entering the evaporation coil 11, flash evaporation and auto-refrigeration, which in turn, results in a mixture of liquid and vapor at a lower temperature and pressure than prior to passing through the expansion device. The auto-refrigeration process is enhanced by the much lower temperature of the evaporation coil 11 being encapsulated in a low temperature thermal storage mass 13. The cold liquid-vapor mixture of the working fluid then travels through the

evaporation coil 11 and vaporizes by gaining additional heat, via conduction from the low temperature thermal storage mass 13 through the walls of the evaporation coil 11.

[00118] Encapsulation, or partial encapsulation, of the evaporation coil 11 within a low temperature thermal storage mass 13 eliminates (or reduces) contact between the coil and the warm air to be cooled. This further improvement to current systems also enables the complete refrigeration cycle for comparably capable whole-house or whole-building "central" HVAC to be more optimally engineered by eliminating site specific variables that current system engineering typically needs to allow for. For example, current engineering practices for indoor "split system" evaporation coils typically allows for broad variations of the working fluid's temperature and pressure while in the evaporation coil to accommodate, for example: (i) interacting with various broad indoor temperature gain rates, (ii) unknown, site specific distances from the evaporation coil to the compressor, (iii) unknown actual volume of refrigerant in the system, (iv) unknown quality or completeness of insulation protecting the line from the evaporation coil to the compressor, and, (v) potential substandard workmanship or site specific design by the installer. Encapsulating the evaporation coil as disclosed prevents (or reduces) the system of this embodiment from having to re-chill the heat exchangers when the compressor cycles on and off. This may result in the advantage that the low temperature of the working fluid of the compressor is preserved. Known HVAC system compressors commonly cycle on and off multiple times per hour, losing a portion of work done each cycle to the warm air surrounding the evaporation coil; however, when the evaporation coil 11 is encapsulated with a low temperature thermal storage mass, the work of each cycle is conserved because the low temperature thermal storage mass 13 acts as an insulating barrier between the air and the evaporation coil 11. The addition of a low temperature thermal storage mass 13 material, such as PT -21, maintains the temperature and low pressure of the working fluid even in between operating cycles, therefore conserving much or most of the work done by the compressor during the previous cycle.

[00119] PT -21 is also a phase change material that begins to phase, from solid to liquid at -21°C. Table 2 below shows properties that are considerations when selecting thermal mass storage material for interacting with R134a refrigerant working fluid through the walls of an evaporation coil. Using the appropriate materials, the pressure and temperatures within this part of the refrigeration cycle become more stable. Moreover, appropriate materials selection allows for a reduction of the amount of working fluid required in the system. In certain embodiments the reduction may be 20%, 40%, 50%, 60%, 75%, 85%, or 90% of working fluid requirements in the system.

TABLE 2

PureTemp -21 Technical Information

PureTemp -21 is a USD A Certified Biobased product.

Melting point -21°C

Heat storage capacity 239 J/g

Thermal conductivity (liquid) 0.15 W/m² °C

Thermal conductivity (solid) 0.25 W/m² °C Density (liquid) 1.06 g/ml

Density (solid) 1.17 g/ml

Specific heat (liquid) 3.43 J/g °C

Specific heat (solid) 1.83 J/g °C

[00120] As is the case on the compression side of the system, the work performed on the working fluid within the evaporation coil 11 is performed by the compressor. Maintaining low temperatures and pressures on the evaporation side of the system equates to less energy consumed by the system. The addition of low temperature thermal storage mass 13 material encapsulating the evaporation coil makes it advantageous to design the evaporation coil to maintain the low temperature thermal storage mass 13 at extremely low temperatures, for example, -10°C, -15°C, -20°C, -30°C, -40°C, -50°C and/or -60°C. These extremely low

temperatures can be accomplished with substantially less energy consumption than current HVAC systems that are typically set to sustain much higher temperatures at the evaporation coil, for example -11°C. As previously explained with respect to the condensing side of the system, the thermal mass is selected to ease the workload by regulating the temperature in the working fluid, ensuring the working fluid is at a much colder temperature and lower pressure than the working fluid would be without the low temperature thermal storage mass 13.

[00121] Continuing on with the working fluid cycle, as the working fluid comes to the end of the evaporation coil 11, the working fluid is cooler, vaporized, and at lower pressures than in current systems as the working fluid is pulled or sucked into the compressor suction port 14 to complete the thermodynamic cycle, which cycle then repeats until the desired heating or cooling is achieved in both the high temperature thermal storage mass 7 and the low temperature thermal storage mass 13, which temperatures may be set by the manufacturer of the system, rather than by the end user via the thermostat of the system. The user of this improved system interacts with the thermostat only to have chilled air or hot air blown into the space that requires tempering, respectively, cooling or heating; however, the heat exchanger that ordinarily would interact with the evaporation coil of a current system now, in the improved system, interacts with the low temperature thermal storage mass. The entire refrigeration cycle of this embodiment only operates to heat or cool one of the two thermal storage masses if and as the system detects a predefined temperature set point in either of the two thermal storage masses. Whereas a current system refrigeration cycle may have to run every hour of the day for 20 or more minutes, each time the compressor runs. This improved system may only need to run the compressor once per day for less than an hour in many common climates and environments to heat or cool one of the two thermal storage masses.

[00122] In this system, the work done by the refrigeration cycle is conserved in two contained thermal masses that are available to the system. This arrangement may be beneficial if there are other heating or cooling needs. For example, the resulting stored thermal masses may be used to heat or cool other volumes of mass (e.g., gases, liquids, solids etc.) while the cycle that is powered by the compressor 1 is on or off. Exemplary embodiments of this system may use various types of phase change materials (PCMs) as thermal storage masses to limit the amount of thermal energy accepted into or rejected out of them, by using the latent heat requirements of their respective phase change temperatures as a thermal barrier. Using PCMs in this manner isolates the controlled working fluid environment of the system from a relatively thermally unstable or inconsistent environment, putting the unstable environment instead in contact with the more stable and consistent environment of a thermal storage mass. Other exemplary embodiments of this system may use various other types thermal storage masses such as glycol or materials with lesser phase change latent heat properties than those previously discussed but with larger specific heat or of greater density to achieve benefits similar to those of a working fluid instead of, or in combination with, the described PCM storage.

[00123] FIG. 2 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 2 shows an active thermal input/output device 15, whereby a thermoelectric heater/chiller module, for example, is used to inject or reject thermal energy into or out of the working fluid as the working fluid is passing through the expansion device 9. This system arrangement may be beneficial when, for example, a higher temperature is desired to be achieved more rapidly in the high temperature thermal storage mass 7 or a lower temperature is desired to be achieved more rapidly in the low temperature thermal storage mass 13. This system arrangement may have an additional benefit of generating some usable quantity of electrical energy, using the thermal difference between the expansion device 9 temperature on the one side of the thermoelectric device and ambient temperature on the opposite side of the thermoelectric device, during times when there is no need to inject or reject thermal energy into or out of the working fluid. This system arrangement takes advantage of an efficient moment in the refrigeration cycle to inject heat into or reject heat out of the cycle, due at least in part to the confining effect the expansion device 9 has on the working fluid when it is at the end of the condensing portion of the cycle and before the working fluid begins the evaporation portion of the cycle.

[00124] FIG. 3 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 3 shows a fan 16 which is used to blow a gas 17 to be cooled, air for example, through a heat exchanger 18, with a direct thermal connection to the low temperature thermal storage mass 13, thereby allowing a thermal transfer 19 to occur from the gas 17 to the low temperature thermal storage mass 13, resulting in the gas 17 being cooled upon the gas's exit from the heat exchanger 18. In this embodiment the heat exchanger 18 has no direct thermal connection to the expansion coil 11 or to the working fluid within the expansion coil, nor does the compressor 1 need to be operating to effect the cooling of the gas 17 that is passing through the heat exchanger 18. The compressor 1 is controlled to turn on only when an excess amount of thermal energy has been transferred into the low thermal storage mass 13 sufficient to cause the temperature of the low thermal storage mass to rise above the storage mass's design temperature. The compressor turns on, driving the refrigeration cycle, only long enough for the system to transport the acquired excess thermal energy from the low thermal storage mass 13 to the high temperature thermal storage mass 7. This system

arrangement provides the benefit of bifurcating the slower process of cooling a gas, which is slower due to a gas's dilute density when compared to cooling a liquid or solid state of high or low temperature thermal storage masses 7, 13, from the faster process of the refrigeration cycle engaged in cooling a designed thermal mass with system-specific thermal properties, thus maximizing system efficiencies.

[00125] FIG. 4 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 4 may be used to heat or cool a gas. In this case, a second fan 16 blows a gas 17 to be heated, air for example, through a second heat exchanger 18, with a direct thermal connection to the high temperature thermal storage mass 7, thereby allowing a thermal transfer 19 to occur from the high temperature thermal storage mass 7 to the gas 17, resulting in the gas 17 being heated upon the gas's exit from the second heat exchanger 18. In this embodiment, the second heat exchanger 18 has no direct thermal connection to the condensing coil 5 or to the working fluid within the condensing coil, nor does the compressor 1 need to be operating to effect the heating of the gas 17 that is passing through the second heat exchanger 18. The compressor 1 turns on only when an excess amount of thermal energy has been transferred out of the high temperature thermal storage mass 7 sufficient to cause the temperature of the high temperature thermal storage mass to drop below the storage mass's design temperature, and then the compressor turns on only long enough for the system to transport into the high temperature thermal storage mass additional thermal energy acquired from the low temperature thermal storage mass 13. This system arrangement provides the benefit of bifurcating the slower process of heating a gas, due to a gas's dilute density when compared to a liquid or solid state, from the faster process of the refrigeration cycle engaged in heating a designed thermal mass with system-specific thermal properties, thus maximizing system efficiencies.

[00126] FIGs. 5 - 9 are schematic drawings of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIGs. 5-9 is more specific to Heating, Ventilation, and Air Conditioning (HVAC). FIG. 5 is a schematic drawing of an exemplary embodiment of an HVAC system in cooling mode with the gas 17, in this case interior air, entering the system relatively hot, pulled by a fan 16 that draws from the area to be tempered through a return register 20 and into the heat exchanger 18 with a direct thermal connection to the high temperature thermal storage mass 7, which thermal storage mass has a maintained temperature range between 30°C and 70°C, where the passing air is further heated as the air exits the heat exchanger 18. This initial heating of the air 17 intended to be cooled is intentional for at least the following reasons: (i) to maintain any water vapor in the air as vapor, (ii) to elevate the pressure (relative to that of the room) of the air flow on the hot side of the cycle, and/or (iii) to ensure a large thermal difference between the air to be cooled and the low temperature thermal storage mass when the air reaches the cold side of the system.

[00127] The warmed air 17 travels through an insulated duct 21 passing through an air filter 22, a HEPA filter for example, thereby conditioning the air, prior to the air passing through a desiccant filter 23 capturing all or a substantial portion of water vapor in the volume. The removal of water vapor at this point in the cycle is useful so as to prevent (or reduce) such water vapor from phase changing into a liquid (water) and/or into a solid (frost) at the cold exchanger 18. The now warmer, drier air 17, free (or substantially free) of particulates and also at a higher pressure than when the air entered the system, continues through the duct 21, entering the heat exchanger 18, with a direct thermal connection to the low temperature thermal storage mass 13 with a maintained temperature range between, for example, -40°C and -25°C. Due to the expanded thermal and pressure difference at this exchange point of the system, the higher pressure, heated and dried air 17 gives a portion of that air's thermal energy to the much colder heat exchanger 18, which thermal energy subsequently transfers into the low temperature thermal storage mass 13. The air's 17 pressure drops upon loosing thermal energy, as the cooler air 17 is pushed out of the system by the higher pressure air 17 behind it. The lower pressure air 17 may also be pulled out of the system by a second fan 16 through a supply register 24 and thereby blown back into the room colder, cleaner, dehumidified, and at a lower pressure than when the air entered the system.

[00128] This cycle continues until the air temperature in the room is cooled to a desired temperature, as set and controlled by an occupant via a suitable and commonly available thermostat for use in HVAC systems. In this embodiment, the two heat exchangers 18 do not have a direct thermal connection to the condensing coil 5, to the evaporation coil 11, or to the working fluid within either of those coils. Also, the compressor 1 does not need to be operating to effect the heating and cooling process of the air 17 passing through the heat exchangers 18. In cooling mode, the compressor 1 may be configured to operate only when a designed amount of thermal energy has been transferred from the air flow through the heat exchanger 18 into the low temperature thermal storage mass 13, causing the low temperature thermal storage mass to reach a control temperature, -25°C for example, and then the compressor will turn on only long enough for the system to transport enough of the added, conducted thermal energy out of the low temperature thermal storage mass 13 into the high temperature thermal storage mass 7, and the compressor will turn off when the temperature of the low temperature thermal storage mass 13 reaches a second control temperature, -40°C, for example. This system arrangement provides the benefit of bifurcating the slower process of heating and/or cooling air, due to air's dilute density, from the much faster process of the refrigeration cycle engaged in heating and/or cooling designed thermal masses, selected for system-specific thermal properties to maximize efficiencies of the refrigeration cycle of the system. This system arrangement provides the additional benefit of shielding the system from the latent heat energies of water, by separating the water (as vapor) from the air prior to cooling the air. Other benefits provided by this system arrangement are: (i) a reduced workload on both fans, facilitated by the deliberate increase or decrease in air pressure, achieved as a secondary effect of increasing or decreasing the thermal energy within the air at specific points of the cycle, and, (ii) further reduced workload on the second fan 16, because of the air having been dehumidified inside the system.

[00129] FIG. 6 is a schematic drawing of the same exemplary embodiment of an HVAC system as shown in FIG. 5, except now described in heating mode, with the air 17 entering the system cold, pulled by a fan 16 that draws the air from the area to be tempered through a return register 20 and then pushed into and through the heat exchanger 18 with a direct thermal connection to the low temperature thermal storage mass 13, thermal storage mass has a maintained temperature range between 15°C and 25°C, where the passing air is preheated and exits the heat exchanger 18 into an insulated duct 21. The degree to which the air 17 is preheated may vary and is dependent upon the initial temperature of the air 17 when the air enters the system. This initial preheating of the air 17 to prior to the air's final heating is intentional for one or more of the following reasons: (i) to prevent (or limit) water vapor from condensing into a liquid inside the system, (ii) to increase the air's pressure as the air enters the insulated duct 21, so as to maintain an acceptable velocity between exchangers, and, (iii) to assist the desiccant filter in absorbing water vapor from the air.

[00130] The preheated air 17 continues to travel through the insulated duct 21 and may pass through a desiccant filter 23, dehumidifying the air 17. The removal (or reduction) of the water vapor in the air at this point in the cycle is optional while the system is in heating mode, so the desiccant filter may be bypassed if dehumidification is not desired, as there is no longer a possibility of the water vapor condensing to a liquid within the system. As the air 17 moves through the insulated duct 21, the air 17 passes through an air filter 22, such as a HEP A filter, to trap particulates. Once beyond the filter(s) 22 and 23, the air 17 enters heat exchanger 18, having a direct thermal connection to the high temperature thermal storage mass 7, with a maintained temperature range, for example, between 50°C and 70°C. The broadened thermal difference between the surfaces of the heat exchanger 18 and the air 17 and the higher pressure caused by the constraints of the heat exchanger 18 facilitates the air 17 readily absorbing thermal energy from the exchanger 18 and subsequently absorbing thermal energy from the high temperature thermal storage mass 7, heating the air 17 as the air travels through the heat exchanger 18. The heated air 17 is pushed forward by that air's expansion inside the exchanger while the air is also pulled out by a second fan 16 through a supply register 24 and blown back into the room as hotter, cleaner, higher pressure air (either dehumidified or not) than when the air entered the system.

[00131] This cycle continues until the air temperature in the room is heated to a desired temperature, as set and controlled by an occupant via a suitable and commonly available thermostat of the type used in HVAC systems. In this embodiment, the two heat exchangers 18 do not have a direct thermal connection to the condensing coil 5, to the evaporation coil 11, or to the working fluid within them. Also, the compressor 1 does not need to be operating to effect the heating and cooling of the air 17 passing through the heat exchangers 18. In heating mode, the compressor 1 may be configured to operate only when a designed amount of thermal energy has been transferred through the heat exchanger 18 from the high temperature thermal storage mass 7, causing the high temperature thermal storage mass to drop to a control temperature, 50°C for example, and then the compressor will turn on only long enough for the system to add more thermal energy into the system via the thermal input/output device 15 and the compressor will turn off when the temperature of the high temperature thermal storage mass 7 reaches a second control temperature, for example, of 70°C . This system arrangement provides the benefit of bifurcating the slower process of heating and/or cooling air, due to air's relative dilute density, from the faster process of the refrigeration cycle engaged in heating and/or cooling designed thermal masses, selected for system-specific thermal properties to maximize efficiencies of the refrigeration cycle of the system, as described in FIG. 1. This system arrangement provides the additional benefit of shielding the system from the latent heat energies of water (as vapor) by separating the water from the air prior to cooling.

[00132] FIG. 7 is a schematic drawing of an exemplary embodiment of an HVAC system similar to that shown in FIG. 5 and FIG. 6, except now described in thermal exhaust mode. In certain climate zones, even after sunset environmental temperatures can remain higher than is comfortable for most people. An indoor HVAC unit, as described in FIGs. 5 - 9, which have set thermal storage capacities, may eventually reach a thermal saturation point (excess heat) while running in cooling mode and may no longer provide effective cooling. Thermal saturation frequency may be daily, weekly, monthly or at some other fractional frequency of those intervals, depending on at least: (i) the climate zone in which the system is operating, (ii) the thermal loads placed on the system, (iii) the frequency of thermal transport cycles from the low temperature thermal storage mass to the high temperature thermal mass, and, (iv) the fixed thermal properties of the components of the system. Additionally, different climate zones exhibit different humidity levels, which may vary seasonally; therefore, the required frequency of removing the water vapor trapped within the desiccant filters is a second consideration and form of saturation. In such cases where it is not desired or advantageous or practicable to transport and use the system's excess heat beneficially as an input to another system within the building, for example to heat water or for clothes drying, exhausting the excess heat to the outdoor environment may become necessary. Further, in such cases where it is not desired or advantageous or practicable to transport and use the system's trapped water vapor for other purposes, exhausting the excess water vapor to the outdoor environment may become necessary. FIG. 7 describes the exhaust method of the embodiment shown in FIG 5 and FIG 6. FIG. 7 shows an efficient manner that may be employed where the unit is being installed within a wall, an attic, a ceiling space, a floor joist bay, a mechanical closet, or other location within a building.

[00133] FIG. 7 is a schematic drawing of the exemplary embodiment of an HVAC system described in FIG. 5, except now described in exhaust mode. Thermal saturation does not typically occur when the system is in heating mode. Therefore FIG. 6 will be disregarded for this portion of the disclosure. The exhaust process begins by setting the exhaust path, that may include (i) closing the supply register 20, (ii) closing the return register 24, and (iii) closing the heat exchanger 18 of the low temperature thermal storage mass 13 with supply dampers 25, which may be automated, and by (iv) opening the exhaust dampers 35, which may be automated or which may be "normally closed" and then opened by an airflow of proper direction and velocity from the exhaust duct into and though the remaining open insulated duct 21 and at the exit of the heat exchanger 18 surrounded by the high temperature thermal mass 7. The process of FIG. 7 begins by allowing air 26 from the outside 27 with a temperature of, for example 32°C, to enter an inlet vent 28, on the outside 27 of the building, which inlet vent may also include a filter and a damper. In some applications the exhaust air 26 may be pulled in by an in-line fan 16 or by an air pump and then pushed through an inlet duct 30 on the inside 29 of the building to enter the insulated duct 21 of the system through the open exhaust damper 35. The location where the exhaust damper 35 opens into the insulated duct 21 may be in close proximity of, and may be oriented to direct the exhaust air 26 toward and through the desiccant filter 23, relieving the exhaust air of some water vapor and trapped particulates. Also, during this process, the direction the exhaust air 26 travels may be the opposite direction than the air 16, in FIG. 5, while in cooling mode. Due to the near thermally saturated state of the system, the temperature in this relatively confined section of the insulated duct 21, between the desiccant filter 23 and the air filter 22 is elevated, for example, above 50°C, causing the now water-vapor-laden exhaust air 26 to further rise in temperature as the air approaches the air filter 22. The high temperature, water- vapor-laden exhaust air 26 is traveling in the opposite direction as the air 16, in FIG. 5, and, acting much like a steam cleaning mechanism, dislodges particulates caught in the air filter 23 as the air is pushed through the air filter 23 and enters a less confined, but higher temperature heat exchanger 18, surrounded by the high temperature thermal storage mass 7 that may be at a temperature as high as, for example, 71°C. The exhaust air 26 travels into and through the heat exchanger 18, absorbing excess heat out of the high temperature thermal storage mass 7 via the heat exchanger 18, exiting the heat exchanger 18 as much hotter and much higher pressure air 26, relative to when the air entered the process, and the air rushes through the second open exhaust damper 35 into and through the relatively low pressure exhaust duct 30, to exit to the outside 27 through an exhaust vent 31. This cycling of relatively cooler outdoor environmental air through the described exhaust path, rejecting excess heat from the system, continues until the temperature of the high temperature thermal storage mass 7 is in equilibrium with the ambient temperature of the outside 27.

[00134] During this exhaust process, the refrigeration cycle, driven by the compressor, is turned off. If a fan 16 or an air pump is used at the inlet vent 28, the fan or air pump would require a small amount of electrical energy to draw new exhaust air 26 into the process, because the system design can use the excess heat as the energy to do most of the work. For example, in many cases, due to the large thermal differences involved with the disclosed exhaust process, this system arrangement without the aid of a fan or air pump may be designed to use the stack effect commonly used in chimneys. This system arrangement provides the benefit of a no-cost or low- cost exhaust process of the excess heat to prevent or alleviate thermal saturation of the system. This system arrangement also provides an automatic cleaning process of both the air filter and the desiccant filter, extending the time they are useful in the system before needing manual cleaning or replacement.

[00135] FIG. 8 is a three-dimensional graphical representation similar to the exemplary embodiment of an HVAC system described in FIG. 5, FIG. 6, and FIG. 7, except a normally-closed two-way valve has been added between the expansion valve 15 and the evaporation coil 11, to prohibit thermal migration within the working fluid of the refrigeration cycle when the compressor 1 is turned off, effectively separating the high pressure side 8 from the low pressure side 10 of the closed loop. FIG. 9 is a cross-sectional view of the exemplary embodiment of an HVAC system described in FIG. 8.

[00136] FIG. 10 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 10 is similar to the embodiment of FIG. 1, except a second condensing coil 37, a second high temperature thermal storage mass 38, and four three-way valves 36 have been added to the system. These system additions allow the system to purge acquired thermal energy from the first high temperature thermal storage mass 7 into the second high temperature thermal storage mass 38. FIG. 10 shows the system in normal operation mode. The second high temperature thermal storage mass 38 may be the same or different thermal storage material as the first high temperature thermal storage mass and may be maintained at higher, lower, or substantially the same or exactly the same temperature as the first high temperature thermal storage mass 7. The thermal energy stored in the second high temperature thermal storage mass 38 may be used beneficially by another system that requires thermal energy, for example by a hot water heater.

[00137] FIG. 11 is a schematic drawing of the exemplary embodiment of an HVAC system described in FIG. 10 except now described in thermal purge mode. In FIG. 11, four three-way valves 36 are in their secondary position, closing off the evaporation coil 11 and the low temperature thermal mass 13 from the refrigeration cycle. In this configuration, the first high temperature thermal storage mass 7 now acts as the low temperature thermal storage mass to allow the refrigeration cycle to transfer an amount of the thermal energy acquired during normal operation into the second high temperature thermal storage mass 38. Therefore, the condensing coil 5 now becomes the evaporation coil 11 and works in cooperation with the second condensing coil 37 to transfer the thermal energy. [00138] FIG. 12 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 12 is similar to the embodiment of FIG. 1, except a second condensing coil 37, a second high temperature storage thermal mass 38, and two three-way valves 36 have been added to the system to augment the high temperature thermal capacity of the system. The second high temperature thermal storage mass 38 may be the same, substantially the same, or a different thermal storage material and may be maintained at a temperature higher, lower, substantially same or exactly the same as the first high temperature thermal storage mass 7. The thermal energy stored in the second high temperature thermal storage mass 38 may be used beneficially by another system that requires thermal energy, for example, by a clothes dryer or for power generation.

[00139] FIG. 13 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 13 is similar to the embodiment of FIG. 12, except a second evaporation coil 39, a second high temperature thermal mass 40, and two additional three-way valves have been added to the system to augment the low temperature thermal capacity to the system. The second low temperature thermal mass 40 may be the same, substantially the same, or a different thermal storage material and may be maintained at a temperature higher, lower, substantially the same or exactly the same as the first low temperature thermal mass 13. The thermal energy stored in the second low temperature thermal mass 40 may be used beneficially by another system that requires thermal energy, for example by a food refrigerator.

[00140] FIG. 14 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 14 is similar to the embodiment of FIG. 12, except the second high temperature thermal mass 38 is a volume of water (or other liquid) with a pump 41 used to transfer the water into a second water tank 42 for hot water storage and use.

[00141] FIG. 15 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 15 is similar to the embodiment of FIG. 14, except a second high temperature thermal storage mass 38 is used in part to heat, through a thermally conductive surface 43, a separate volume of water (or other liquid) surrounding the high temperature thermal storage mass. The additional thermal storage of FIG. 15 is described as "high temperature" with embedded condensing coil, however, it may also be "low

temperature" with embedded evaporation coil. Any number or combination of additional thermal storages may be added to the system.

[00142] FIG. 16 is a schematic drawing of another exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle. The exemplary embodiment of FIG. 16 is similar to the embodiment of FIG. 14, except the system is configured with a second high temperature thermal storage mass 38, a second low temperature thermal storage mass 40, a second condensing coil 37, and a second evaporation coil 39. Additional high temperature and/or low temperature thermal storage masses with embedded condensing and/or evaporation coils may be added to the base system as needed.

[00143] FIG. 17 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy of the refrigeration cycle by converting all or part the unwanted thermal energy into electrical energy. The exemplary embodiment of FIG. 17 is similar to the embodiment of FIG. 2, except for the addition of thermoelectric modules 44 that are thermally connected to the low temperature thermal storage mass 13, generating DC electrical power 45, by using the thermal difference between the ambient temperature and the low temperature thermal storage mass 13 and the addition of thermoelectric modules 44, thermally connected to the high temperature thermal storage mass 7, generating DC electrical power 45, by using the thermal difference between the ambient temperature and the high temperature thermal storage mass 17.

[00144] FIG. 18 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy of the refrigeration cycle by converting all or part of the unwanted thermal energy into electrical energy. The exemplary embodiment of FIG. 18 is similar to the embodiment of FIG. 12, except the second high temperature thermal storage mass 37 is encapsulated by a separate working fluid 46, for example nitrogen, helium, or acetone, methanol etc., in a container, therefore transferring the heat of the condensing coil embedded within the high temperature thermal storage mass 37 into the working fluid 46. The heated working fluid 46 may be used to drive a pump, turbine or compressor 49 to generate mechanical or electrical power. The working fluid 46 after driving the pump, turbine or compressor 49 is returned to the container in thermal contact with the second high temperature thermal storage mass 37 to repeat the cycle. A second low temperature thermal storage mass may be added to the system to aid to condense the working fluid as it returns to the container.

[00145] FIG. 19 is a schematic drawing of an exemplary embodiment of a system to harvest, transport, store, and put to use solar radiation for electrical energy generation. The exemplary embodiment of FIG. 19 may be used separately or combined with one of the embodiments disclosed in FIG's 1 to 18 and FIG. 20. The exemplary embodiment of FIG. 19 uses the same method of electrical generation as the embodiment of FIG. 18, except the thermal energy source is solar. Solar thermal energy is harvested using a solar collection method, for example an evacuated tube solar thermal collector 53, concentrated by the use of parabolic mirrored troughs 52, and stored in two high temperature thermal storage masses 7,

interconnected by a working-fluid-filled closed loop heat exchanger 50 with two control valves 48, controlling the flow of thermal energy between the two high temperature thermal storage masses 7. The system may also be configured with a low temperature thermal storage mass to aid to condense the working fluid for example in an Organic Rankine Cycle system as it exits the turbine prior to returning to the evaporator.

[00146] The exemplary embodiment of FIG. 19 when combined with one of the embodiments disclosed in FIGs. 1-18 and FIG. 20 may use additional low temperature thermal storage mass to acquire thermal energy from other sources to be transferred as disclosed in FIGs. 1-18 and FIG. 20 to the working fluid 46.

[00147] FIG. 20 is a schematic drawing of an exemplary embodiment of a system that takes advantage of unwanted thermal energy to reduce the electrical energy needs of the refrigeration cycle when used to collect atmospheric water vapor and convert the water vapor to liquid water. The exemplary embodiment of FIG. 20 may be used separately or combined with one of the embodiments disclosed FIGs. 1 to 19 and FIG. 21. Because of the efficiencies gained by the previous disclosures, clean and low cost water may be harvested from environments with a wide range of humidity levels, even below 10% humidity. The environment may be outdoor or indoor. This embodiment is similar to the embodiment described in FIG. 1, except this embodiment contains other elements that are useful in, for example, the harvest of atmospheric water. This embodiment, as with previously discussed embodiments, also separates the working fluid of the refrigeration process from direct interaction with the end substance being heated or cooled. This embodiment describes a method to maintain the low temperature thermal storage mass 12 at a temperature range between -25°C and -65°C to cause the ambient atmosphere to react at a wide range of humidity levels with the thermally conductive surface 43 that is exposed to the ambient environment, as the ambient environment attempts to equalize the temperature difference between the ambient environment and the thermally conductive surface 43. One purpose of exposing an extreme low temperature to the warmer ambient environment is to cause a continual water deposition of water vapor from the ambient humid air 64 upon the thermally conductive surface 43 of the system. Water deposition is the thermodynamic phase process of water vapor (gas) transforming directly to ice (solid). This reaction causes a layer of frost 67 to form on the thermally conductive surface 43 of the system. The frost 67 may be continually removed from the thermally conductive surface 43 by, for example, a scraper 55 and collected in a frost catch trough 57. This atmospheric reaction produces a secondary reaction beneficial to harvesting atmospheric water, which is a drop in local pressure 65 around the system, that pressure drop encouraging a fresh supply chain of higher pressure water vapor to be drawn toward and interact with the extremely cold, thermally conductive surface 43.

[00148] By maintaining a temperature far below both the dew point and the freezing point of water, the thermally conductive surface 43 of the system only conducts into the low temperature thermal storage mass 12 a fraction of the latent heat energy released during the water deposition process, Instead, the bulk of the latent heat energy that is released during the water deposition process is absorbed by the non-water-vapor volume of the ambient atmosphere, such as nitrogen and oxygen, in close proximity to the process, further contributing to the process flow cycle around the thermally conductive surface 43. In fact, an amount of frost 67 may be created before the water vapor in the air actually contacts the thermally conductive surface 43. The actual percentage of the amount of water vapor that is present in the

environment is based on at least the following: the temperature, the relative humidity, the barometric pressure, and the saturated vapor density, however, the extreme thermal difference this embodiment achieves allows water harvest even from the driest atmospheric environments.

[00149] The water harvester of FIG. 20 may be powered by a hermetically sealed compressor 1, by a Stirling cycle engine, or by other pump to enable the refrigeration cycle. The system may be powered using input energy 2 of various types, for example, AC or DC electric, propane, or other power sources. A circulating working fluid, R134a for example, enters the compressor 1, through the compressor's suction port 14 as a vapor. The compressor 1 compresses the vapor causing the vapor to become superheated vapor as the vapor is "pushed" or "discharged" through the compressor's discharge port 3. The working fluid, now a superheated vapor, enters the condensing coil 5. The condensing coil 5 is encapsulated in a high temperature thermal storage mass 7, for example Entropy Solutions, PT 151, and sealed within a stainless steel container. Some of the thermal properties of the high temperature thermal storage mass 7, are: (i) a melting point above 120°C, (ii) solid density above 1.3 g/ml, (iii) solid thermal conductivity above 0.2 W/m°C, and, (iv) solid specific heat above 2.0 J/g°C. During operations of this embodiment, the high temperature thermal storage mass 7 should typically not phase into a liquid, with a maximum internal temperature of 100°C. This component of the system is thermally isolated both from the environment in which the system is operating and from other parts of the system, to prevent the heat that the high temperature thermal storage mass 7 acquires from rejecting into anything other than the harvested water collection basin 59 that encloses the high temperature thermal storage mass 7. The condensing coil 5 first cools and removes the superheat of the working fluid and then condenses the working fluid from vapor to liquid by removing additional heat, at near constant pressure and temperature, via conduction, to the adjacent high temperature thermal storage mass 7 through the condensing coil's 5 walls. The working fluid is now a liquid, but because of the high temperature thermal storage mass 7 encapsulating the condensing coil 5, the liquid is at a high pressure and high temperature as the liquid exits the condensing coil 5 and enters the confining expansion device 9. The expansion device 9 is a capillary tube coil. The expansion device 9 is seated between two thermoelectric chillers, a thermal input/output device 15, to reject an amount of thermal energy from the working fluid before the working fluid enters the evaporation coil 11. After flowing through the expansion device 9, the working fluid enters the much less restricted area of the evaporation coil 11, that is one-third longer than the overall length of the condensing coil 5 and that is

encapsulated in a low temperature thermal storage mass 13, for example Entropy Solutions PT - 21.

[00150] Some of the thermal properties of the low temperature thermal storage mass 13, are: (i) a melting point below -20°C, (ii) solid density above 1.0 g/ml, (iii) solid thermal conductivity above 25 W/m°C, (iv) solid specific heat above 1,5 J/g°C and, (v) latent heat energy above 200 J/g. After initial start up, the low temperature thermal storage mass 13 should typically not phase into a liquid, maintaining a maximum internal temperature of -25 °C and reduced to -65°C during the refrigeration cycles. This low temperature thermal storage mass 13 is thermally isolated from both the environment in which the system is operating and from the rest of the system, to limit the low temperature thermal storage mass 13 to acquiring thermal energy only through the thermally conductive surface 43 that is interacting with the ambient environment. The schematic drawing of this embodiment suggests the shape of the low temperature thermal storage mass 13 being a downward pointing cone; however, other suitable shapes and sizes may also be used. The working fluid continues through to the end of the evaporation coil 11, and the resulting cool, vaporized, low pressure working fluid is "pulled" or "sucked" into the compressor suction port 14 to complete the thermodynamic cycle, which repeats continually until the desired cooling is achieved in the low temperature thermal storage mass 13. Once the system is "thermally charged," meaning the thermally conductive surface 43 and the low temperature thermal storage mass are at a temperature of -65°C, then the thermally conductive surface 43 is opened and exposed to the environment.

[00151] When the thermally conductive surface 43 is exposed to ambient humid air 64, water deposition begins, as previously described, and the thermally conductive surface 43 obtains a layer of frost 67. The thermally conductive surface 43 is scraped frequently by, for example, a scraper blade 55 along a path shown as 54 in Figure 20. The dislodged frost, falls into a frost catch trough 58, eventually entering, by gravity, the collection basin 59, through a collection inlet 58, where the frost is warmed into a liquid by the high temperature thermal storage 7 mass that encapsulates the condensing coil. Harvested water held in the collection basin 59 may be delivered for use through the collection outlet 60. In certain embodiments, the water harvester may be installed at an elevation sufficiently higher than the intended final destination of the harvested water to facilitate the insertion of one or more water turbines 61 along or within the water flow, for the additional benefit of electrical generation 45 before the water is cleaned through a filter 62, prior to end use.

[00152] FIG. 21 is a schematic drawing of another exemplary embodiment of a system to harvest, transport store and put to use solar radiation for electrical energy generation. The exemplary embodiment of FIG. 21 is similar to the embodiment of FIG. 19 and also may be used separately or in various combinations with FIGs. 1 tol8 and FIG. 20. The exemplary embodiment of FIG. 21 uses a wind turbine 68 and an air pump 69 to pump air out of the environment and into a containment vessel, compressing the air for use as a working gas 46. Solar thermal energy 54 may also be employed to increase the energy potential of the working gas 46, similar to the embodiment described in FIG. 19. The compressed working gas 46 may be used for electrical generation, to power a system based on the refrigeration cycle, or to do other useful work.

[00153] FIG. 22 is a schematic drawing of a commonly known system and method to transport unwanted thermal energy away from an electronic component that is generating heat, commonly used by the electronics and semiconductor industries. FIGs. 23 to 25 illustrate improved methods for thermal transport of unwanted thermal energy away from an electronic component that is generating the heat. FIG. 22 uses an electronic component such as a light emitting diode (LED) as the heat source. FIGs. 23 through 25 illustrate embodiments of the present disclosure that show an electronic component as a heat source, such as an LED. Other electronic components of various sizes, uses, or thermal output properties may be substituted as the source of the unwanted heat. For example, the component package 75 may be a MOSFET, a photovoltaic cell, an integrated circuit, or other type of electronics component requiring thermal management.

[00154] FIG. 23 is a cross-sectional drawing of an exemplary embodiment of a system to quickly transport unwanted thermal energy away from the component generating the unwanted thermal energy, and/or away from other components within close proximity, without (or in conjunction with) commonly used heat sinks, heat pipes, or fans. The embodiment of FIG. 23 uses a light emitting diode (LED) as the component, as an example only. Other electronic components of various sizes, uses, or thermal output properties may be substituted as the source of the unwanted heat. For example, the component package 75 may be a MOSFET, a photovoltaic cell, an integrated circuit, or other type of electronics component requiring thermal management. FIG. 23 is a cross-sectional view depicting an LED semiconductor 74 in the system's semiconductor package 75, including the lens, the electrodes 77, the anode, and the cathode of the LED package. The LED's electrodes 77 are mounted/attached by solder 79, or by electrically conductive epoxy, to the electrically and thermally conductive layer 78 of a printed circuit board (PCB) substrate 80 with a thickness and thermal properties that are selected relative to the electrodes used 77. The PCB substrate 80 is attached to a metallic or composite thermal conduit 88 by a thermal bonding layer 87, for example, by a thermally conductive epoxy that causes a scattering effect of the unwanted thermal energy. The propagation path of the thermal energy has been altered to become much more linear (than that shown in FIG. 22) as the thermal energy travels away from the source. A thermal substrate 86 attached to the opposite side of the thermal conduit 88 by a second thermal bonding layer 87 scattering the thermal energy and increasing the linear effect to the primary propagation path 83. Thermal conduits 88 that are thermally attached to a thermal backplane 89 may be placed three-dimensionally at a suitable angle to linearly conduct the thermal energy away from the semiconductor 74. The spaces created between the thermal conduits 88 are filled with a volume of micro-granular mass 90, creating a secondary phonon path 91 of thermal energy that will migrate out of the thermal conduits 88. The material of the mass may be graphite powder, for example, with the granular size and packing density dictating the flow rate of the thermal energy through the void. The micro-granular mass 90 can also use different types of granular materials separated by thin film layers of materials. The described method takes advantage of the characteristics of thermal migration waves to transport thermal energy away from the source without a local thermal buildup around the source. To do so, the described method uses thermal interference at the interfaces of thin layers of nano/micro materials or three-dimensional arrangements. Although the described method herein is shown as an electronic semiconductor, this method may be applied to other applications, whether, for example, the heat source is as small as a

semiconductor or as large as a steam turbine.

[00155] FIG. 24 is a cross-sectional drawing of another exemplary embodiment of a system to quickly transport unwanted thermal energy away from the component generating the unwanted thermal energy, or away from other electronic components in close proximity, without (or in conjunction with) commonly used heat sinks, heat pipes, or fans. The embodiment of FIG. 24 is similar to FIG. 23, except embodiment of FIG. 24 uses an adhesive 92 to attach an insulating substrate 93 to the back of the thermal substrate 86 to confine most of the primary phonon path 83. The embodiment of FIG. 24 also uses a thermal conduction break 94 in the thermal substrate 86 to limit flow direction of thermal migration. In certain embodiments, such as LED lighting, directing the heat emission 96 in the same, or substantially the same, direction as the light emission 95 is advantageous, because light is most often directed to an open space. [00156] FIG. 25 is a cross-sectional and isometric drawing of another exemplary embodiment of a system to quickly transport unwanted thermal energy away from the

component generating the unwanted thermal energy, or away from other electronic components in close proximity, without (or in conjunction with) commonly used heat sinks, heat pipes, or fans. The embodiment of FIG. 25 is similar to FIG. 23, except FIG. 23 shows the method using multiple LEDs 97 and multiple micro-granular masses 90, separated by thermal conduits 88. An insulating substrate 93 is also used to reduce thermal migration at the back.

[00157] While embodiments of the disclosure have been shown and described herein, it will be obvious to those skilled in the art that such embodiments are provided by way of example only. It is intended that the following claims define the scope of the invention and that methods and structures within the scope of these claims and their equivalents be covered thereby.

[00158] In the exemplary embodiments described herein, the following reference numerals have the identified label/structure/operation:

1. Compressor

2. Input energy

3. Compressor discharge port

4. Direction of flow

5. Condensing coil

6. Thermal energy out

7. High temperature thermal storage mass

8. High pressure side

9. Expansion device

10. Low pressure side

11. Evaporation coil

12. Thermal energy in

13. Low temperature thermal storage mass

14. Compressor suction port

15. Thermal input/output device

16. Fan

17. Gas

18. Heat exchanger 19. Thermal transfer

20. Return register

21. Duct

22. Desiccant filter

23. Air Filter

24. Supply register

25. Supply damper

26. Outdoor Air

27. Outside

28. Inlet vent

29. Inside

30. Exhaust duct

31. Exhaust vent

32. Two-way valve

33. Power supply

34. Control / logic circuit

35. Exhaust damper

36. Three-way valve

37. Second Condensing coil

38. Second high temperature thermal storage

39. Second Evaporation coil

40. Second low temperature thermal storage

41. Pump

42. Water Storage

43. Thermally conductive surface

44. Thermoelectric generator

45. Electrical power out

46. Working Fluid or Gas

47. Pressure control valve

48. Control valve

49. Reciprocating compressor 0. Closed loop heat exchanger

1. Compression tank

2. Parabolic mirrored trough

3. Evacuated tube solar thermal collector 4. Solar thermal energy

5. Scraper

6. Scraper path

7. Frost catch trough

8. Collection inlet

9. Collection basin

0. Collection outlet

1. Water turbine generator

2. Water filter

63. Water outlet

64. Humid air

65. Dry air

66. Air pressure drop

67. Ice or frost

68. Wind turbine

69. Air pump

70. Tank inlet

71. Tank outlet

72. Pneumatic generator

73. Support ties

74. Semiconductor

75. Semiconductor package

76. Lens

77. Electrode

78. Conductive layer

79. Solder

80. PCB substrate 81. Heat sink

82. Thermal grease

83. Primary phonon path

84. Heat source mass

85. Thermal management mass

86. Thermal substrate

87. Thermal bonding layer

88. Thermal conduit

89. Thermal backplane

90. Micro-granular mass

91. Secondary phonon path

92. Adhesive

93. Insulating substrate

94. Thermal conduction break

95. Direction of light emission

96. Direction of heat emission

97. Light emitting diode

98. Thermally conductive shell

NAI-l 502846578V 1

Claims

WHAT IS CLAIMED IS:

1. A system for harvesting, transporting, storing and/or using acquired thermal energy to increase efficiencies of HVACR systems comprising:

a compressor;

a fan and a condensing coil with one end of the condensing coil connected to a discharge port of the compressor;

an evaporation coil embedded in a volume of a Low Temperature Phase Change Material (PCM) with one end of the evaporation coil connected to a suction port of the compressor;

one or more thermoelectric modules in thermal contact with a capillary coil in-line between the condensing coil and the evaporation coil;

a volume of working fluid in the coils' closed-loop;

a temperature-sensing switch connected to the PCM volume to control the on/off state of the compressor; and

a cold air exchanger substantially thermally isolated from the evaporation coil but in thermal contact with the Low Temperature PCM volume.

2. The system of claim 1, wherein the acquired thermal energy is used to maintain or increase the temperature, and thereby the pressure, of a working fluid or gas of a system.

3. The system of claim 1 of 2, wherein the system is used to drive a turbine connected to a generator to provide electrical power (AC or DC).

4. The system of any of claim 1-3, wherein the system is used to reduce the energy requirements of compressor motors.

5. The system of any of claim 1-4, wherein the system is used to reduce the energy requirements of pumps.

6. The system of any of claim 1-5, wherein the system is used to maintain or increase the temperature of a gas.

7. The system of any of claim 1-6, wherein the system is used to provide or supplement heating of indoor, ambient air.

8. The system of any of claim 1-7, wherein the acquired thermal energy is used to evaporate the working fluid that drives an Organic Rankine cycle turbine connected to a generator to provide electrical power (AC or DC).

9. The system of any of claim 1-8, wherein the acquired thermal energy is used to release water vapor from the desiccant material in dehumidification systems.

10. The system of any of claim 1-9, wherein the acquired thermal energy is converted to kinetic energy (e.g., rotating or linear motion).

11. The system of any of claim 1-10, wherein the acquired thermal energy is used to induce a phase change of a material.

12. The system of any of claim 1-11, wherein the acquired thermal energy is used to heat or assist in heating magnetized antiferromagnetic materials above the Neel temperature.

13. The system of any of claim 1-12, wherein the acquired thermal energy is used to heat or assist in heating magnetized ferromagnetic materials above the Curie temperature.

14. The system of any of claim 1-13, wherein the acquired thermal energy is used to heat or assist in heating nitinol to effect martensitic transformation to produce mechanical work.

15. The system of any of claim 1-14, wherein the thermal energy is harvested from passive solar radiation.

16. The system of any of claim 1-15, wherein the thermal energy is harvested from the condensing coils of HVACR systems or from other materials in thermal contact with the evaporation coils of HVACR systems.

17. The system of any of claim 1-16, wherein the thermal energy is harvested from high heat-flux density semiconductors and other electronic components in devices (e.g., processors, LEDs, transistors, transformers, electromagnets).

18. The system of any of claim 1-17, wherein the thermal energy is harvested from manufacturing process heat systems.

19. The system of any of claim 1-18, wherein the thermal energy is harvested from machines converting energy contained in fuels to do mechanical work or to generate electrical energy.

20. The system of any of claim 1-19, wherein the thermal energy is harvested from other types of anthropogenic heat (i.e., heat generated by humans or human activity).

21. The system of any of claim 1-20, wherein the thermal energy is more rapidly transported, away from thermally sensitive components via a thermally remote thermally conductive channel, by spreading and dissipating the thermal energy two dimensionally across a nano/micro material layer (e.g., graphene, phosphene, diamond powder).

22. The system of any of claim 1-21, wherein the thermal energy is transported via a thermoelectric device.

23. The system of any of claim 1-22, wherein the thermal energy is transported passively, during the lower outdoor temperature of a diurnal temperature cycle.

24. The system of any of claim 1-23, wherein the thermal energy is transported to a secondary storage device to prevent thermal saturation of the primary storage device.

25. The system of any of claim 1-24, wherein the thermal energy is stored in organic phase change material(s) and/or other types of phase change materials (i.e., PCMs).

26. A system for harvesting, transporting, storing, and/or using acquired thermal energy to increase efficiencies of HVACR systems comprising:

a compressor;

a condensing coil at least partially embedded in a volume of a High Temperature Phase Change Material (PCM) with one end of the condensing coil connected to a discharge port of the compressor;

an evaporation coil at least partially embedded in a volume of a Low Temperature PCM with one end of the evaporation coil connected to a suction port of the compressor;

a volume of working fluid in the coils' closed-loop;

temperature-sensing switches connected to the PCM volumes to control the on/off state of the compressor;

a hot air exchanger substantially thermally isolated from the condensing coil and in thermal contact with the High Temperature PCM volume; and

27. A system for harvesting, transporting, storing and/or using acquired thermal energy to increase efficiencies of HVACR systems comprising:

a compressor;

a condensing coil at least partially embedded in a volume of a High Temperature Phase Change Material (PCM) with one end of the coil connected to a discharge port of the

compressor;

one or more thermoelectric modules in thermal contact with an expansion valve in-line between the condensing coil and the evaporation coil;

a volume of working fluid in the coils' closed-loop; temperature-sensing switches connected to the PCM volumes to control the on/off state of the compressor; a hot air exchanger substantially thermally isolated from the condensing coil and in thermal contact with the High Temperature PCM volume; and

a cold air exchanger substantially thermally isolated from the evaporation coil and in thermal contact with the Low Temperature PCM volume.

28. A system for harvesting, transporting, storing and/or using the acquired thermal energy to increase efficiencies of HVACR systems comprising:

a compressor;

a condensing coil embedded in a volume of a High Temperature Phase Change Material (PCM) with one end of the coil connected to a discharge port of the compressor;

an evaporation coil embedded in a volume of a Low Temperature PCM with one end of the evaporation coil connected to a suction port of the compressor;

one or more thermoelectric modules in thermal contact to a capillary coil in-line between the condensing coil and the evaporation coil;

a rejection loop coil and a heat exchanger located within the system or in proximity to the system which may be accessed by a working fluid through thermally controlled automatic valves;

a volume of working fluid in the coil closed-loop;

one or more temperature- sensing switches connected to the PCM volumes and/or other parts of the system to control the on/off state of the compressor and valve flow direction;

a hot air exchanger substantially thermally isolated from the condensing coil and in thermal contact with the High Temperature PCM volume;

a cold air exchanger substantially thermally isolated from the evaporation coil and in thermal contact with the Low Temperature PCM volume; and

an exhaust port in-line with the rejection loop.