US20110154838A1 - Heat exchange system - Google Patents
Heat exchange system Download PDFInfo
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- US20110154838A1 US20110154838A1 US12/829,060 US82906010A US2011154838A1 US 20110154838 A1 US20110154838 A1 US 20110154838A1 US 82906010 A US82906010 A US 82906010A US 2011154838 A1 US2011154838 A1 US 2011154838A1
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- heat
- heat exchange
- fluid
- exchange system
- sink
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Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D11/00—Central heating systems using heat accumulated in storage masses
- F24D11/02—Central heating systems using heat accumulated in storage masses using heat pumps
- F24D11/0214—Central heating systems using heat accumulated in storage masses using heat pumps water heating system
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
- F24D17/00—Domestic hot-water supply systems
- F24D17/02—Domestic hot-water supply systems using heat pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2339/00—Details of evaporators; Details of condensers
- F25B2339/04—Details of condensers
- F25B2339/047—Water-cooled condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/24—Storage receiver heat
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
- F28D20/0034—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using liquid heat storage material
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
- F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
Definitions
- aspects of the present invention relate to a portable and scalable heat exchange system. More particularly, aspects of the invention relate to a high-efficiency water-to-water heat exchange system for providing an efficient, portable, and/or scalable heating and/or cooling source.
- FIG. 1 shows an exemplary vapor-compression refrigeration cycle 2 used in many heat exchange systems, in which a refrigerant is circulated through a closed-loop compression and expansion cycle.
- the refrigerant begins as a vapor at point A.
- the refrigerant vapor is compressed and circulated by a compressor 10 , resulting in a high-pressure, high-temperature refrigerant vapor.
- the electro-mechanical energy of the compressor 10 is also converted into heat energy carried by the refrigerant vapor, which exits the compressor 10 as a superheated vapor.
- Phase 2 of the cycle the superheated vapor passes through a condenser 20 where a heat exchange process pulls heat energy from the superheated vapor, causing the refrigerant to condense into a high-pressure liquid.
- the hot liquid refrigerant is then directed through a thermal expansion valve 30 , which meters the flow of refrigerant to the evaporator 40 and usually results in a flash lowering of the pressure and temperature of the condensed hot liquid refrigerant.
- the low-pressure, low-temperature liquid or saturated liquid/vapor refrigerant enters the evaporator 40 during Phase 4 of the cycle, wherein a second heat exchange process draws heat energy from a heat source, such as water or air, to the refrigerant, causing the refrigerant to reach a saturation temperature and returning the refrigerant to the vapor state at point A.
- a heat source such as water or air
- the heat exchanging condenser 20 extracts heat energy from the superheated refrigerant vapor during Phase 2 of the cycle by using a blower 50 to direct cool air across condenser coils carrying the hot vapor (see FIG. 1 ).
- the cool air conducts heat energy from the coils and the heated air is supplied by the blower through ducting, for example, to directly heat the home or residence.
- the evaporator typically relies on the air temperature outside the home for drawing heat into the refrigerant during Phase 4 of the cycle.
- the blower 50 may instead be used to direct hot air across evaporator coils carrying the cooler fluid refrigerant during Phase 4 of the cycle 2 .
- the cooler fluid refrigerant conducts heat energy from the hot air, and the resulting cooler air may be supplied to the home.
- the condenser 20 relies on the outside air to cool the superheated vapor during Phase 2 of the vapor-compression cycle 2
- the heat pump may be designed with a reversible valve and specialized heat exchangers, for example, allowing the vapor-compression cycle 2 to operate in either direction, with each heat exchanger serving as either a condenser or an evaporator.
- the cycle of the heat pump can thus be reversed, so that, depending on the desired climate, a single blower may be used to direct hot or cool air across coils, for example, carrying the cooler refrigerant fluid or the superheated refrigerant vapor, respectively.
- a typical air-source heat pump works harder to transfer heat from a cooler place to a warmer place as the temperature difference increases between the cooler and warmer places. Accordingly, the performance of an air-source heat pump deteriorates significantly, for example, during the winter months in a very cold climate, as the temperature difference between the air outside a home becomes significantly less than the desired temperature inside the home.
- a ground source heat pump system which typically extracts heat from the ground, or a body of water, may be used to counteract the effect of significant temperature gradients between the heat source and the heat sink. This is because the ground below a certain depth, and water below a certain level, maintains a fairly constant temperature year round, leading to generally lower temperature differentials throughout significant periods of the year, allowing for increased performance of the heat pump.
- the vapor-compression cycle 2 described in FIG. 1 may be coupled with a ground source loop 3 that carries a heat exchange fluid, such as water, for example.
- the heat exchange fluid conducts heat while flowing through conduits 4 buried in the ground or sunk under a body of water 5 .
- a portion of the heat carried by the heat exchange fluid in the conduits 4 is transferred to the cooler liquid refrigerant by conduction through a heat exchange process performed by the evaporator 40 during Phase 4 of the vapor-compression cycle 2 .
- the refrigerant is vaporized, and the refrigerant vapor is then compressed during Phase 1 of the vapor-compression cycle.
- a blower 50 may be used to direct cool air across condenser coils while carrying the hot vapor during Phase 2 of the vapor-compression cycle 2 in order to provide heat to the interior of a structure.
- a heat sink loop 6 may be coupled with the condenser 20 to capture heat transferred from the heat exchange fluid during Phase 4 of the vapor-compression cycle 2 , along with heat that is added through the electro-mechanical energy input by the compressor 10 during Phase 1 of the vapor-compression cycle 2 , into a heat sink 60 , which could be a tank of hot water, for example.
- the condensed refrigerant exiting the condenser 20 is then expanded during Phase 3 of the vapor-compression cycle 2 and the cooler refrigerant liquid enters the evaporator 40 once again to draw more heat from the heat exchange fluid flowing through the ground source loop 3 .
- a typical ground source system such as the ground source loop 3 described above, is expensive to construct and can be extremely disruptive to install because thousands of feet of piping may need to be placed in horizontally dug trenches or wells dug vertically deep into the ground, to effectively tap into the thermal energy contained therein. And although the thermal conductivity of water is greater than that of the ground, generally allowing for less piping to be placed into a body of water, access to a body of water close enough to the home for the purpose of creating a ground source system is often unfeasible.
- aspects of the present invention provide for a heat exchange system that combines a thermally conductive fluid and a specially tuned vapor-compression cycle in an extremely efficient, modular, portable, and scalable system for providing superior heat exchange capabilities for heating and/or cooling in almost any environment.
- the heat exchange system in accordance with aspects of the present invention may be disassembled and assembled with ease and without causing damage to the structural components of the system to permit convenient installation in residential, commercial and industrial settings.
- aspects of the present invention include operation of the system using a portable generator, allowing deployment in remote locations, such as forward operating military outposts, or to provide heating, cooling, hot water and chilled water to people in need around the world, such as victims in disaster relief centers and in refugee camps.
- aspects of the invention and, in particular, the increased performance of the efficiently designed heat exchange system, including an automated fluid management system, permit enhanced heating and cooling while creating a significantly reduced footprint on the environment over conventional heating and cooling systems that rely on fossil fuels to function.
- FIG. 1 shows an exemplary vapor-compression cycle as typically used in heat exchange systems
- FIG. 2 shows an exemplary ground source heat pump system as is known in the prior art
- FIG. 3 shows a system flow diagram of a heat exchange system, in accordance with aspects of the present invention
- FIG. 4 shows a perspective view of an exemplary heat exchange system, in accordance with aspects of the present invention
- FIG. 5 shows an enlarged view of various components of the exemplary heat exchange unit, in accordance with aspects of the present invention
- FIG. 6 shows a cutaway view of an exemplary heat sink, in accordance with aspects of the present invention.
- FIG. 7 is a system flow diagram of an exemplary heat exchange system with an integrated fluid management system.
- FIG. 8 is a system flow diagram of an exemplary heat exchange system with an integrated fluid management system.
- FIG. 3 is an exemplary flow diagram in accordance with aspects of the present invention.
- the heat exchange system 100 comprises a vapor-compression refrigeration cycle having a compressor 110 , a condenser 120 , an expansion valve 130 , and an evaporator 140 .
- the refrigerant R-410A a mixture of difluoromethane and pentafluoroethane, is preferred for its thermodynamic properties and because R-410A does not contribute to ozone depletion.
- R-410A typically operates at higher pressures than most refrigerants, requiring increased strength in certain components of the system.
- a heat source 200 such as a tank of water, may be provided to work in tandem with the heat exchange system 100 to supply heat energy during Phase 4 of the vapor-compression cycle 2 .
- the heat source 200 may alternatively be a nearby lake or stream, for example.
- the heat source 200 may be connected to the heat exchange system 100 through a circulation system 210 , which may be a closed-loop or open-loop system for circulating a heat exchange fluid, such as water.
- the circulation system 210 may include a pump 215 , for example, for circulating the heat exchange fluid from the heat source 200 , through the evaporator 140 and back to the heat source 200 .
- Fluid flow valves 216 may be installed on either side of the pump 215 , to allow for fluid flow to the pump 215 to be shut off during assembly, or during repair and/or replacement of the pump 215 .
- Fluid flow conduits 217 for carrying the heat exchange fluid 205 through the circulation system 210 may include rigid and/or flexible tubing made of a thermally conductive material, such as copper or a modified polyethylene, for example. As shown in FIG. 4 , the fluid flow conduits 217 may include flexible tubing exterior to the heat exchange system 100 , copper or brass tubing, for example, inside of the heat exchange system 100 , and hard plastic tubing, for example, to form a coiled section of the evaporator 140 .
- the heat exchange fluid 205 is forced by the pump 215 to flow through the stacked coil section 142 of the evaporator 140 in a specified direction.
- the heat exchange function of the evaporator 140 is accomplished by concurrently running a cold refrigerant conduit 132 , which exits the expansion valve 130 , through the stacked coil section 142 of the evaporator 140 .
- the cold refrigerant conduit 132 enters the evaporator 140 at an evaporator entrance junction 134 and exits the evaporator at an evaporator exit junction 136 .
- the cold refrigerant conduit 132 follows, and is contained within, the stacked coil section 142 of the evaporator 140 .
- the cold refrigerant conduit 132 is ideally situated to permit the entire outer surface area of the cold refrigerant conduit 132 to be in direct contact with the warmer heat exchange fluid 205 flowing through the stacked coil section 142 . Accordingly, increased thermal conduction from the heat exchange fluid during Phase 4 of the vapor-compression cycle 2 is provided by the aforementioned arrangement of the structural components.
- the refrigerant flow entering the evaporator 140 has just completed Phase 3 of the vapor-compression cycle, in which the hot refrigerant fluid has passed through the expansion valve 130 and experienced a rapid decrease in pressure and temperature.
- the cooler refrigerant fluid flows through the cold refrigerant conduit 132 in the same direction as the warmer heat exchange fluid flows through the stacked coil section 142 of the evaporator 140 .
- the concurrent tubular flow creates a variable temperature gradient over the length of the stacked coil section 142 , in which the refrigerant absorbs the heat energy of the heat exchange fluid at a greater rate nearer the evaporator entrance junction 134 than towards the evaporator exit junction 136 .
- the cold refrigerant conduit 132 follows, and is contained within, the stacked coil section 142 of the evaporator 140 .
- the refrigerant and the heat exchange fluid both approach an equilibrium temperature as the fluids flow in parallel through the respective conduits in the evaporator 140 .
- the refrigerant has thus completed Phase 4 of the vapor-compression cycle, and, as a vapor, is now ready to enter the compressor 110 .
- the compressor 110 which may be a reciprocating or scroll compressor, for example, supplies the electro-mechanical energy to compress the vapor into a superheated vapor during Phase 1 of the vapor-compression cycle 2 .
- a heat sink 300 such as a tank of water, may be provided to work in tandem with the heat exchange system 100 to store the amplified heat energy extracted from the heat exchange fluid during Phase 4 of the vapor-compression cycle 2 .
- the heat sink 300 may be connected to the heat exchange system 100 through a heat sink circulation system 310 , which may be a closed-loop or open-loop system for circulating a heat absorption fluid 305 , such as water.
- the heat sink circulation system 310 may include a pump 315 , for example, for circulating the heat absorption fluid from the heat sink 300 , through the condenser 120 and back to the heat sink 300 .
- Fluid flow valves 316 such as ball or butterfly valves, may be installed on either side of the pump 315 , to allow for fluid flow to be shut off to the pump 315 during assembly, or during repair and/or replacement of the pump 315 .
- Fluid flow conduits 317 for carrying the heat absorption fluid through the heat sink circulation system 310 may include rigid and/or flexible tubing made of a thermally conductive material, such as copper or a modified polyethylene, for example. As shown in FIG. 4 , the fluid flow conduits 317 may include rigid copper tubing, for example, insulated to protect heat loss during circulation of the heat absorption fluid through the heat sink circulation system 310 .
- the heat absorption fluid is forced by the pump 315 to flow through the stacked coil section 122 of the condenser 120 in a specified or predetermined direction.
- the heat exchange function of the evaporator 120 is accomplished by concurrently running a hot refrigerant conduit 112 , which exits the compressor 110 , through the stacked coil section 122 of the condenser 120 .
- the hot refrigerant conduit 112 enters the condenser 120 at a condenser entrance junction 114 and exits the condenser at a condenser exit junction 116 .
- the hot refrigerant conduit 112 follows, and is contained within, the stacked coil section 122 of the condenser 120 .
- the hot refrigerant conduit 112 is ideally situated to permit the entire outer surface area of the hot refrigerant conduit 112 to be in direct contact with the cooler heat absorption fluid flowing through the stacked coil section 122 of the condenser 120 . This enables increased thermal conduction from the superheated refrigerant vapor during Phase 2 of the vapor-compression cycle 2 .
- the refrigerant flow entering the condenser 120 has just completed Phase 1 of the vapor-compression cycle, in which the refrigerant vapor was compressed by the compressor 110 and experienced a rapid increase in temperature.
- the superheated refrigerant vapor flows through the hot refrigerant conduit 112 in an opposite direction relative to the cooler heat absorption fluid flowing through the stacked coil section 122 of the condenser 120 .
- the countercurrent tubular flow maintains a nearly constant temperature gradient over the length of the stacked coil section 122 , in which heat is conducted from the superheated refrigerant vapor into the cooler heat absorption fluid at nearly the same rate near the condenser entrance junction 114 as at the condenser exit junction 116 .
- the countercurrent flow in the condenser 120 allows efficient transfer of a substantial portion of the heat energy drawn from the heat exchange fluid, as well as the work energy input from the compressor 110 , into the heat sink 300 .
- a second condenser (not shown) may be provided between the condenser 120 and the expansion valve 130 .
- the refrigerant may still retain a certain amount of thermal energy that was not transferred to the heat absorption fluid during the exchange process in the first condenser 120 .
- the second condenser may be provided to draw additional thermal energy from the refrigerant into a fluid that may be circulated back to the heat source 200 .
- the warm fluid may thus transfer the additional thermal energy back into the heat source 200 for storage and further use as described above.
- the heat exchange system of the present invention draws on the thermal energy contained in the heat source 200 , which may be a tank of water at ambient temperature, for example, and by way of the vapor-compression cycle 2 , deposits the withdrawn thermal energy efficiently into the heat sink 300 , which may be another tank of water, for example.
- the heat sink 300 may thus reach temperatures of more than 150° F.
- the hot water in the heat sink 300 may be drawn and pumped through pipes 400 to a radiant heating system, for example, or a hydronic coil and blower arrangement that is connected to a ducting system, in order to provide a constant and efficient source of heat for the interior of a structure.
- a domestic hot water storage tank 500 may be connected to the heat sink 300 to heat exchange thermal energy into the hot water storage tank 500 for potable water use.
- FIG. 6 shows an enlarged cutaway view of an exemplary heat sink 300 in accordance with aspects of the present invention.
- the fluid flow conduits 317 which may be wrapped in insulating material to prevent the escape of thermal energy to the environment, may run from the heat sink 300 to the heat exchange system 100 and back to complete a closed loop, for example.
- a heat exchange coil 318 comprised of copper, or any other suitable material having high thermal conductivity, may be provided inside the heat sink 300 to facilitate heat exchange from the hot water in the fluid flow conduits 317 into the heat sink 300 .
- the hot water may then be drawn into the pipes 400 to supply a radiant heating system, for example.
- the domestic hot water storage tank 500 may connect to the heat sink 300 by pipes 502 , which may be insulated, to conduct heat from the hot water in the heat sink 300 by way of heat exchange coils 504 , also placed in the heat sink 300 .
- the domestic hot water system may be completely separate from the heat sink circulation system 310 , the efficient heat exchange system thus providing the thermal energy for potable hot water use in a safe and cost-effective manner.
- an electronic control unit (ECU) 540 may be provided to control operation of the compressor 110 and the circulation pumps 215 and 315 .
- the ECU 540 may operate with one or more thermostats, for example, to maintain the system in an efficient operating range.
- the ECU 540 may set the compressor 110 and the circulation pumps 215 and 315 to run if the temperature of the water in the heat sink 300 drops below a certain efficiency threshold temperature, for example, or alternatively, if the temperature of the water in the heat source 200 rises above a certain efficiency threshold temperature.
- a certain efficiency threshold temperature for example, or alternatively, if the temperature of the water in the heat source 200 rises above a certain efficiency threshold temperature.
- a thermal energy source 220 may provide supplemental thermal energy to the heat source cycle when a temperature gauge in the heat source 200 indicates to the ECU 540 that the temperature of the heat source 200 has dropped below a predetermined efficiency threshold.
- the thermal energy source 220 may be any suitable source for heating the heat exchange fluid 205 , such as a conventional hot water heating element of a predetermined wattage, for example, placed within the fluid flow conduit 217 .
- Other exemplary thermal energy sources in accordance with aspects of the present invention may include the abundant heat sources in restaurants from which the thermal energy can be drawn upon and deposited, through heat exchangers, for example, into the heat source 200 .
- thermo energy source 220 Any ready source of heat that can be practically transferred into the heat source 200 may be used as the thermal energy source 220 , including “hot spots” found in swimming pools, drain pipes, transformer rooms, data centers, computer rooms, and the upper space in certain high-ceiling rooms, to name just a few.
- the techniques to capture and transfer the thermal energy from a thermal energy source 220 may typically include hydronic systems, but any suitable method of transferring thermal energy from a secondary source of heat to the heat source 200 is contemplated herein.
- the heat exchange system 100 may be fitted with an electronic pressure control unit 550 .
- the electronic pressure control unit 550 may be set up to monitor the sensed pressure at any point in the system, including the intake (suction) pressure and the discharge (head) pressure of the compressor 110 . Accordingly, measurement of the evaporator pressure and/or the condenser pressure can provide valuable insight into the efficiency of the system and whether the refrigerant charge is too low or excessive, for example.
- a sight glass 135 may also be used to aid in the inspection of the refrigerant charge level, as bubbles in the line generally indicate an undercharge.
- the sight glass 135 is preferably located on the high-pressure liquid side of the compressor 110 .
- a filter drier 137 may be installed in the refrigerant path, preferably on the high-pressure liquid side of the compressor 110 , to adsorb unwanted moisture in the refrigerant cycle.
- the refrigerant charge in the vapor-compression cycle 2 may be precisely determined in accordance with a length of the refrigerant run and the desired characteristics of a well-balanced heat exchange system.
- the R-410A refrigerant charge may be intentionally set to a level that allows the system to continue to operate at maximum efficiency, while increasing the discharge temperature of the superheated vapor discharged from the compressor 110 .
- the unexpected results of the present invention call for a substantially lower refrigerant charge than normal to achieve the desired results of an efficient heat transfer between the heat source 200 and the heat sink 300 .
- R-410A enhances the ability to increase the temperature on the discharge side of the compressor 110 , but requires much higher pressures to operate compared to previously used refrigerants. For example, to achieve a condensing temperature value of 140°, an R-410 high-side pressure must approach 550 psi. In other words, for the heat absorption fluid running through the condenser coil section 122 , which is generally maintained at a temperature of 140° or higher, to condense the superheated vapor of the refrigerant in the conduit 116 , the pressure on the condenser side of the heat exchanger must approach 550 psi or higher.
- the heat exchange system 100 can handle the higher pressures required to produce the higher compressor discharge temperatures necessary to ensure heat exchange occurs in the condenser at temperatures above 140° F.
- the temperature of the heat source 200 lowers. Depending on the heat load demand, and the size of the body of water, for example, that is serving as the heat source 200 , the temperature of the heat source 200 may drop significantly. Due to the parallel, concurrent tubular flow design of the evaporator 140 , and the ability to generally maintain the heat source 200 in an ambient environment, the liquid refrigerant typically draws enough latent heat to effectively boil the liquid refrigerant and deliver vapor with enough pressure to the compressor 110 to function highly efficiently.
- a slight lowering of the refrigerant charge so that the intake side pressure is slightly lowered, while still preventing liquid refrigerant from being delivered to the compressor 110 may slightly elevate the compression ratio of the compressor 110 .
- the higher compression ratio in turn may transfer more compression energy to the refrigerant during compression resulting in an even higher discharge temperature so that the heat absorption fluid can be heated to even higher temperatures.
- the colder heat source 200 may also be used as a cooling medium for chilling water or providing cool air by employing the same water-to-water or water-to-air heat transfer means discussed above with respect to the hot water side.
- hydronic coils which draw upon the cold water created in the heat source 200 , may be used in combination with a fan to blow hot air across the hydronic coils to produce cooler air for the air conditioning of a particular structure.
- a separate cold water heat exchange system and storage tank for example, can provide chilled water for a variety of uses.
- a housing unit 600 may have multiple shelves 601 and 602 for vertically stacking and/or creating compartments for the storage and mounting of the various components of the heat exchange system 100 , such as the compressor 110 , the condenser 120 , the expansion valve 130 , and the evaporator 140 .
- Various quick install features may be included to enable the easy installation and/or disassembly of the heat source 200 and/or the heat sink 300 , including hose bibs (not shown), for example, for quickly connecting/disconnecting the fluid flow conduits 217 and 317 to the heat exchange system 100 .
- Mounting brackets may be provided to allow for quick and efficient mounting of the various components, such as the compressor 110 , the condenser 120 , the evaporator 140 and the circulation pumps 215 and 315 .
- Rubber padding, insulation, panels, doors and/or a cover may be provided that permit easy assembly/disassembly and access to the interior components for maintenance, while reducing the vibration, sound and heat loss that may be generated during operation of the heat exchange system 100 .
- the housing unit 600 may be provided with a surface for mounting an integrated electric panel. As such, the heat exchange system may be prewired and ground to the integrated electric panel to provide a single, efficient connection to an external power source.
- Light Emitting Diode (LED) panels may be mounted to the housing unit to provide visible operational feedback to an observer with respect to various aspects or components of the heat exchange system 100 .
- LED Light Emitting Diode
- the unit 100 may be transported to and employed easily in remote locations.
- a generator may be used for producing the electricity needed by the compressor 110 and the circulation pumps 215 and 315 , and access to a water source may provide both a heat source 200 and a heat sink 300 for heating and cooling purposes.
- FIG. 7 depicts aspects of an exemplary fluid management system 700 in accordance with the present invention that may be integrated with various aspects the heat exchange system 100 to provide precision balance and control for efficiently managing the varying heating and cooling load demands for an enclosed structure, for example.
- the housing unit 600 may house the primary components of the vapor compression cycle 2 , such as the compressor 110 , the condenser 120 , the expansion valve 130 , the evaporator 140 , the pumps 215 and 315 , and/or the ECU 540 .
- the heat source circulation system 210 includes the heat source 200 , which may be a 225 gallon water tank, for example, connected to the evaporator 140 in the housing unit 600 by fluid flow conduits 217 .
- the heat sink circulation system 310 includes the heat sink 300 , which may be a 55 gallon water tank, for example, connected to the condenser 120 in the housing unit 600 by fluid flow conduits 317 .
- the heat sink circulation system 310 may include a secondary heat sink 350 , which may be a 160 gallon water tank, for example, also connected to the condenser 120 in the housing unit 600 .
- Three way valves 360 and 365 may be provided to control the fluid flow between the primary and secondary heat sinks, 300 and 350 respectively.
- the valves 360 and 365 are controlled to operate in tandem so that when the valve 360 shuts off fluid flow in the direction of the heat sink 300 and instead directs the fluid flow to the secondary heat sink 350 , the valve 365 opens to receive the fluid flow from the secondary heat sink 350 and is closed to receiving fluid flow from the heat sink 300 . Similarly, when the valve 360 shuts off the fluid flow in the direction of the secondary heat sink 350 and instead directs the fluid flow to the heat sink 300 , the valve 365 opens to receive the fluid flow from the heat sink 300 and is closed to receiving fluid flow from the secondary heat sink 350 . In this manner, the heat exchange system 100 may select either the heat sink 300 or the secondary heat sink 350 into which to deposit the thermal energy drawn from the heat source 200 .
- the components of the fluid management system 700 in conjunction with the components of the heat exchange system 100 , must be sized appropriately to achieve a symbiotic balance between the thermal mass of the heat sinks 300 and 350 , any associated hot side heat exchange systems, the thermal mass of the heat source 200 , and any associated cold side heat exchange systems, while accommodating the varying heating and cooling load demands.
- Factors such as ambient outdoor temperatures during summer and winter months, construction materials used for building the structure, including insulation and windows, and the habits of inhabitants or tenants, for example, may have a large impact on the various system configurations used to calibrate the heat exchange system in response to the required heating and cooling load demands.
- a heat source temperature gauge 230 may be provided to monitor a core temperature of the heat source 200 .
- temperature gauges 302 and 352 may be provided to respectively monitor core temperatures of the heat sink 300 and the secondary heat sink 350 .
- the various temperature gauges 230 , 302 and 352 may communicate with the ECU 540 by a set of relay switches, or any suitable circuit devices, including wireless thermostats, for example.
- the fluid management system 700 operates in balanced synchronization with the heat exchange system 100 by monitoring the core temperatures of the heat source 200 and the heat sinks 300 and 350 .
- the temperature of the heat source 200 may be maintained to have a core temperature reading between 45 and 60° F. by cycling the heat exchange system 100 as required while the heat sink 300 maintains a temperature of 140° F.
- the increased draw of stored thermal energy from the heat source 200 in order to keep the heat sink 300 at a particular temperature, 140° F. may drop the temperature of the heat source 200 below a threshold temperature, impacting the efficiency of the heat exchange system 100 .
- the fluid management system 700 may be set to signal the ECU 540 to turn on the heater 220 when the heat source temperature gauge 230 reads a core temperature below 38° F., for example.
- the ECU 540 may be programmed, for example, to continue operation of the heat exchange system 100 until the heater 220 provides enough supplemental thermal energy to the fluid flow to raise the core temperature of the heat source 200 to a preset threshold winter temperature, 45° F. for example.
- a supplemental solar heating system 800 may be configured to operate in tandem with either the heat sink 300 or the heat source 200 through a heat exchange process in which solar thermal units convert solar energy into thermal heat energy that is supplied to the fluid flow of the heat exchange system 100 .
- Three way valves 810 and 820 may be provided to control the fluid flow between the solar heating system 800 and either the heat sink 300 or the heat source 200 , respectively.
- the valves 810 and 820 are controlled to operate in tandem so that when the valve 810 shuts off fluid flow in the direction of the heat sink 300 and instead directs the fluid flow to the heat source 200 , the valve 820 opens to receive the fluid flow from the heat source 200 and is closed to receiving fluid flow from the heat sink 300 . Similarly, when the valve 810 shuts off the fluid flow in the direction of the heat source 200 and instead directs the fluid flow to the heat sink 300 , the valve 820 opens to receive the fluid flow from the heat sink 300 and is closed to receiving fluid flow from the heat source 200 . In this manner, the heat exchange system 100 may select either the heat sink 300 or the heat source 200 as the beneficiary of the thermal energy produced by the solar thermal units of the supplemental solar heating system 800 .
- the fluid management system 700 may be programmed to maintain the core temperature of the heat source 200 at a lower threshold summer temperature, 38° F. for example. Under these circumstances, the amount of thermal energy drawn from the heat source 200 may raise the core temperature of the heat sink 300 to levels too high for the condenser heat exchange process to function efficiently. To keep the condenser section operating at lower temperatures, the fluid management system 700 may thus be controlled to open the valve 360 in the direction of the secondary heat sink 350 to direct fluid from the condenser 120 to the larger secondary heat sink 350 rather than the heat sink 300 .
- the fluid management system 700 is controlled to open the valve 365 to receive fluid from the secondary heat sink 350 rather than from the heat sink 300 .
- the secondary heat sink 350 may serve as a large depository of excess thermal energy during peak cooling demand, allowing the system to maintain the core temperature of the heat source 200 at a lower desirable temperature without distressing the efficiency of the system.
- Another feature in accordance with aspects of the present invention may include providing a further mechanism for drawing off excess thermal energy in the event that the secondary heat sink 350 also reaches a core temperature considered too elevated for the efficient operation of the condenser 120 of the heat exchange system 100 .
- a pipe or conduit may be provided so that fluid can be pumped from the secondary heat sink 350 to an area where a fan and/or hydronic coils may be used to transfer the excess energy to an ambient air environment external to the structure, for example.
- a neutral tank 900 may be configured to operate in combination with the fluid management system 700 to serve as a temperature buffer for the heat sinks 300 and 350 and the heat source 200 . Because many aspects of the heat exchange system 100 and the fluid management system 700 will function as described above, a majority of the structure and functional aspects of the heat exchange system 100 and the fluid management system 700 are not repeated here.
- the piping of the heat exchange system 100 and fluid management system 700 may be modified, for example, to accommodate the introduction of the neutral tank 900 .
- the neutral tank 900 may be configured to respectively segregate the fluid flow to the heat exchangers 120 and 140 from the fluid flow returning from the heat exchange system, such as a hydronic coil and air handling system, or other secondary heat exchangers, used to heat and/or cool an objective space.
- the heat source circulation system 210 may be configured so that the heat exchange fluid is supplied to the evaporator 140 from the neutral tank 900 , with the heat exchange fluid being returned from the evaporator 140 directly to the cold tank.
- the heat sink circulation system 310 may be configured so that the heat absorption fluid is supplied to the condenser 120 from one of the heat sinks 300 , 350 or the neutral tank 900 , or a combination of the heat sinks 300 , 350 and the neutral tank 900 , and the heat absorption fluid is returned from the condenser 120 directly to the heat sink 300 or 350 .
- the heat exchange fluid returning from the hydronic coils, for example, that is used to heat or cool the objective space may be deposited directly into the neutral tank 900 .
- both the heat sinks 300 , 350 and the heat source 200 may be spared from the influence of the reduced or elevated temperature of the fluid returning from the heat exchange process (e.g., hydronic coils and air handler) that resulted in the respective heating or cooling of the objective space.
- the heat exchange process e.g., hydronic coils and air handler
- the neutral tank 900 permits the cooler fluid returning from the hydronic coils to be deposited into the neutral tank 900 , rather than back into the heat sink(s) 300 , 350 .
- the temperature of the fluid supplied from the heat source 200 to the hydronic coils is elevated through the heat exchange process (e.g., hydronic coils and air handler) in order to cool the objective space.
- the neutral tank 900 permits the warmer fluid to be deposited into the neutral tank 900 , rather than back into the heat source 200 .
- the heat sinks 300 , 350 and the heat source 200 may deliver fluid at temperatures that have not been tempered by fluid returning from the heat exchange process used to heat or cool the objective space.
- the fluid delivered to the hydronic coils may be maintained at temperatures that are more effective for heating or cooling of the structure, while the temperatures of the fluids in the heat sinks 300 , 350 and heat source 200 may be more consistently controlled, enhancing the operation and efficiency of the system.
- the neutral tank 900 may thus buffer the heat sinks 300 , 350 and the heat source 200 from large fluctuations in temperatures that may be associated with peak system demand, for example.
- the operation and efficiency of the heat exchangers 120 and 140 may be effectively controlled due to the consistent maintenance of the temperatures of the heat exchange fluids supplied from the heat sinks 300 , 350 and the heat source 200 .
- the neutral tank 900 may be any suitable receptacle for the storage and maintenance of a heat exchange medium in accordance with aspects of the present invention.
Abstract
A modular heat exchange system having a refrigerant system for cycling a refrigerant through a compressor, a condenser, an expansion valve, and an evaporator, a heat source circulation system which circulates a heat exchange fluid between a heat source and the evaporator, a heat sink circulation system which circulates a heat absorption fluid between a heat sink and the condenser, a heat exchanger for exchanging thermal energy between one of the heat exchange fluid or the heat absorption fluid; and a neutral tank, wherein the one of the heat exchange fluid or the heat absorption fluid is deposited in the neutral tank upon returning from the heat exchanger.
Description
- This is a Continuation-in-Part of application Ser. No. 12/752,585 filed Apr. 1, 2010, now pending, which is a Continuation-in-Part of application Ser. No. 12/543,268 filed Aug. 18, 2009, now pending. The disclosures of the prior applications are hereby incorporated by reference herein in their entirety.
- 1. Field of the Invention
- Aspects of the present invention relate to a portable and scalable heat exchange system. More particularly, aspects of the invention relate to a high-efficiency water-to-water heat exchange system for providing an efficient, portable, and/or scalable heating and/or cooling source.
- 2. Background of the Technology
-
FIG. 1 shows an exemplary vapor-compression refrigeration cycle 2 used in many heat exchange systems, in which a refrigerant is circulated through a closed-loop compression and expansion cycle. As shown inFIG. 1 , the refrigerant begins as a vapor at point A. DuringPhase 1 of the cycle, the refrigerant vapor is compressed and circulated by acompressor 10, resulting in a high-pressure, high-temperature refrigerant vapor. The electro-mechanical energy of thecompressor 10 is also converted into heat energy carried by the refrigerant vapor, which exits thecompressor 10 as a superheated vapor. DuringPhase 2 of the cycle, the superheated vapor passes through acondenser 20 where a heat exchange process pulls heat energy from the superheated vapor, causing the refrigerant to condense into a high-pressure liquid. As shown atPhase 3 of the cycle, the hot liquid refrigerant is then directed through athermal expansion valve 30, which meters the flow of refrigerant to theevaporator 40 and usually results in a flash lowering of the pressure and temperature of the condensed hot liquid refrigerant. As a result, the low-pressure, low-temperature liquid or saturated liquid/vapor refrigerant enters theevaporator 40 duringPhase 4 of the cycle, wherein a second heat exchange process draws heat energy from a heat source, such as water or air, to the refrigerant, causing the refrigerant to reach a saturation temperature and returning the refrigerant to the vapor state at point A. The cycle is repeated. - In many conventional residential heat pump systems, for example, for supplying heat, the
heat exchanging condenser 20 extracts heat energy from the superheated refrigerant vapor duringPhase 2 of the cycle by using ablower 50 to direct cool air across condenser coils carrying the hot vapor (seeFIG. 1 ). The cool air conducts heat energy from the coils and the heated air is supplied by the blower through ducting, for example, to directly heat the home or residence. The evaporator, on the other hand, typically relies on the air temperature outside the home for drawing heat into the refrigerant duringPhase 4 of the cycle. - For supplying cool air, the
blower 50 may instead be used to direct hot air across evaporator coils carrying the cooler fluid refrigerant duringPhase 4 of thecycle 2. The cooler fluid refrigerant conducts heat energy from the hot air, and the resulting cooler air may be supplied to the home. Under such circumstances, thecondenser 20 relies on the outside air to cool the superheated vapor duringPhase 2 of the vapor-compression cycle 2 - In some conventional systems, the heat pump may be designed with a reversible valve and specialized heat exchangers, for example, allowing the vapor-
compression cycle 2 to operate in either direction, with each heat exchanger serving as either a condenser or an evaporator. The cycle of the heat pump can thus be reversed, so that, depending on the desired climate, a single blower may be used to direct hot or cool air across coils, for example, carrying the cooler refrigerant fluid or the superheated refrigerant vapor, respectively. - A typical air-source heat pump, as described above, works harder to transfer heat from a cooler place to a warmer place as the temperature difference increases between the cooler and warmer places. Accordingly, the performance of an air-source heat pump deteriorates significantly, for example, during the winter months in a very cold climate, as the temperature difference between the air outside a home becomes significantly less than the desired temperature inside the home.
- A ground source heat pump system, which typically extracts heat from the ground, or a body of water, may be used to counteract the effect of significant temperature gradients between the heat source and the heat sink. This is because the ground below a certain depth, and water below a certain level, maintains a fairly constant temperature year round, leading to generally lower temperature differentials throughout significant periods of the year, allowing for increased performance of the heat pump. As shown in
FIG. 2 , the vapor-compression cycle 2 described inFIG. 1 may be coupled with aground source loop 3 that carries a heat exchange fluid, such as water, for example. The heat exchange fluid conducts heat while flowing throughconduits 4 buried in the ground or sunk under a body of water 5. A portion of the heat carried by the heat exchange fluid in theconduits 4 is transferred to the cooler liquid refrigerant by conduction through a heat exchange process performed by theevaporator 40 duringPhase 4 of the vapor-compression cycle 2. The refrigerant is vaporized, and the refrigerant vapor is then compressed duringPhase 1 of the vapor-compression cycle. As described previously, ablower 50 may be used to direct cool air across condenser coils while carrying the hot vapor duringPhase 2 of the vapor-compression cycle 2 in order to provide heat to the interior of a structure. Additionally, aheat sink loop 6 may be coupled with thecondenser 20 to capture heat transferred from the heat exchange fluid duringPhase 4 of the vapor-compression cycle 2, along with heat that is added through the electro-mechanical energy input by thecompressor 10 duringPhase 1 of the vapor-compression cycle 2, into aheat sink 60, which could be a tank of hot water, for example. The condensed refrigerant exiting thecondenser 20 is then expanded duringPhase 3 of the vapor-compression cycle 2 and the cooler refrigerant liquid enters theevaporator 40 once again to draw more heat from the heat exchange fluid flowing through theground source loop 3. - A typical ground source system, such as the
ground source loop 3 described above, is expensive to construct and can be extremely disruptive to install because thousands of feet of piping may need to be placed in horizontally dug trenches or wells dug vertically deep into the ground, to effectively tap into the thermal energy contained therein. And although the thermal conductivity of water is greater than that of the ground, generally allowing for less piping to be placed into a body of water, access to a body of water close enough to the home for the purpose of creating a ground source system is often unfeasible. - There exists a need for a heat exchange system which combines the efficiencies of the thermal conductivity of a fluid, such as water and a specially tuned vapor-compression cycle to produce an efficient, portable, and scalable heat exchange system for simultaneously providing heating and/or cooling.
- Aspects of the present invention provide for a heat exchange system that combines a thermally conductive fluid and a specially tuned vapor-compression cycle in an extremely efficient, modular, portable, and scalable system for providing superior heat exchange capabilities for heating and/or cooling in almost any environment. As a result, the heat exchange system in accordance with aspects of the present invention may be disassembled and assembled with ease and without causing damage to the structural components of the system to permit convenient installation in residential, commercial and industrial settings. Aspects of the present invention include operation of the system using a portable generator, allowing deployment in remote locations, such as forward operating military outposts, or to provide heating, cooling, hot water and chilled water to people in need around the world, such as victims in disaster relief centers and in refugee camps.
- Aspects of the invention, and, in particular, the increased performance of the efficiently designed heat exchange system, including an automated fluid management system, permit enhanced heating and cooling while creating a significantly reduced footprint on the environment over conventional heating and cooling systems that rely on fossil fuels to function.
- Additional advantages and novel features of aspects of the invention will be set forth in part in the description that follows, and in part will become more apparent to those skilled in the art upon examination of the following or upon learning by practice of the invention.
-
FIG. 1 shows an exemplary vapor-compression cycle as typically used in heat exchange systems; -
FIG. 2 shows an exemplary ground source heat pump system as is known in the prior art; -
FIG. 3 shows a system flow diagram of a heat exchange system, in accordance with aspects of the present invention; -
FIG. 4 shows a perspective view of an exemplary heat exchange system, in accordance with aspects of the present invention; -
FIG. 5 shows an enlarged view of various components of the exemplary heat exchange unit, in accordance with aspects of the present invention; -
FIG. 6 shows a cutaway view of an exemplary heat sink, in accordance with aspects of the present invention; -
FIG. 7 is a system flow diagram of an exemplary heat exchange system with an integrated fluid management system; and -
FIG. 8 is a system flow diagram of an exemplary heat exchange system with an integrated fluid management system. -
FIG. 3 is an exemplary flow diagram in accordance with aspects of the present invention. Theheat exchange system 100 comprises a vapor-compression refrigeration cycle having acompressor 110, acondenser 120, anexpansion valve 130, and anevaporator 140. Although many different refrigerants may be used, the refrigerant R-410A, a mixture of difluoromethane and pentafluoroethane, is preferred for its thermodynamic properties and because R-410A does not contribute to ozone depletion. As will be described in further detail, R-410A typically operates at higher pressures than most refrigerants, requiring increased strength in certain components of the system. - As shown in
FIGS. 3 and 4 , aheat source 200, such as a tank of water, may be provided to work in tandem with theheat exchange system 100 to supply heat energy duringPhase 4 of the vapor-compression cycle 2. Theheat source 200 may alternatively be a nearby lake or stream, for example. Theheat source 200 may be connected to theheat exchange system 100 through acirculation system 210, which may be a closed-loop or open-loop system for circulating a heat exchange fluid, such as water. Thecirculation system 210 may include apump 215, for example, for circulating the heat exchange fluid from theheat source 200, through theevaporator 140 and back to theheat source 200.Fluid flow valves 216, such as ball or butterfly valves, may be installed on either side of thepump 215, to allow for fluid flow to thepump 215 to be shut off during assembly, or during repair and/or replacement of thepump 215.Fluid flow conduits 217 for carrying the heat exchange fluid 205 through thecirculation system 210 may include rigid and/or flexible tubing made of a thermally conductive material, such as copper or a modified polyethylene, for example. As shown inFIG. 4 , thefluid flow conduits 217 may include flexible tubing exterior to theheat exchange system 100, copper or brass tubing, for example, inside of theheat exchange system 100, and hard plastic tubing, for example, to form a coiled section of theevaporator 140. - As indicated by the longer arrows in the enlarged view of
FIG. 5 , the heat exchange fluid 205 is forced by thepump 215 to flow through the stackedcoil section 142 of theevaporator 140 in a specified direction. The heat exchange function of theevaporator 140 is accomplished by concurrently running a coldrefrigerant conduit 132, which exits theexpansion valve 130, through the stackedcoil section 142 of theevaporator 140. The coldrefrigerant conduit 132 enters theevaporator 140 at an evaporator entrance junction 134 and exits the evaporator at anevaporator exit junction 136. The coldrefrigerant conduit 132 follows, and is contained within, the stackedcoil section 142 of theevaporator 140. The coldrefrigerant conduit 132 is ideally situated to permit the entire outer surface area of the coldrefrigerant conduit 132 to be in direct contact with the warmer heat exchange fluid 205 flowing through the stackedcoil section 142. Accordingly, increased thermal conduction from the heat exchange fluid duringPhase 4 of the vapor-compression cycle 2 is provided by the aforementioned arrangement of the structural components. - As shown in
FIG. 5 , the refrigerant flow entering theevaporator 140 has just completedPhase 3 of the vapor-compression cycle, in which the hot refrigerant fluid has passed through theexpansion valve 130 and experienced a rapid decrease in pressure and temperature. As shown with the smaller arrows inFIG. 5 , the cooler refrigerant fluid flows through the coldrefrigerant conduit 132 in the same direction as the warmer heat exchange fluid flows through the stackedcoil section 142 of theevaporator 140. The concurrent tubular flow creates a variable temperature gradient over the length of the stackedcoil section 142, in which the refrigerant absorbs the heat energy of the heat exchange fluid at a greater rate nearer the evaporator entrance junction 134 than towards theevaporator exit junction 136. The coldrefrigerant conduit 132 follows, and is contained within, the stackedcoil section 142 of theevaporator 140. The refrigerant and the heat exchange fluid both approach an equilibrium temperature as the fluids flow in parallel through the respective conduits in theevaporator 140. The refrigerant has thus completedPhase 4 of the vapor-compression cycle, and, as a vapor, is now ready to enter thecompressor 110. - As shown in
FIGS. 3 and 4 , thecompressor 110, which may be a reciprocating or scroll compressor, for example, supplies the electro-mechanical energy to compress the vapor into a superheated vapor duringPhase 1 of the vapor-compression cycle 2. Aheat sink 300, such as a tank of water, may be provided to work in tandem with theheat exchange system 100 to store the amplified heat energy extracted from the heat exchange fluid duringPhase 4 of the vapor-compression cycle 2. Theheat sink 300 may be connected to theheat exchange system 100 through a heatsink circulation system 310, which may be a closed-loop or open-loop system for circulating a heat absorption fluid 305, such as water. The heatsink circulation system 310 may include apump 315, for example, for circulating the heat absorption fluid from theheat sink 300, through thecondenser 120 and back to theheat sink 300.Fluid flow valves 316, such as ball or butterfly valves, may be installed on either side of thepump 315, to allow for fluid flow to be shut off to thepump 315 during assembly, or during repair and/or replacement of thepump 315.Fluid flow conduits 317 for carrying the heat absorption fluid through the heatsink circulation system 310 may include rigid and/or flexible tubing made of a thermally conductive material, such as copper or a modified polyethylene, for example. As shown inFIG. 4 , thefluid flow conduits 317 may include rigid copper tubing, for example, insulated to protect heat loss during circulation of the heat absorption fluid through the heatsink circulation system 310. - As indicated by the longer arrows in the enlarged view of
FIG. 5 , the heat absorption fluid is forced by thepump 315 to flow through the stackedcoil section 122 of thecondenser 120 in a specified or predetermined direction. The heat exchange function of theevaporator 120 is accomplished by concurrently running a hotrefrigerant conduit 112, which exits thecompressor 110, through the stackedcoil section 122 of thecondenser 120. The hotrefrigerant conduit 112 enters thecondenser 120 at acondenser entrance junction 114 and exits the condenser at acondenser exit junction 116. The hotrefrigerant conduit 112 follows, and is contained within, the stackedcoil section 122 of thecondenser 120. The hotrefrigerant conduit 112 is ideally situated to permit the entire outer surface area of the hotrefrigerant conduit 112 to be in direct contact with the cooler heat absorption fluid flowing through the stackedcoil section 122 of thecondenser 120. This enables increased thermal conduction from the superheated refrigerant vapor duringPhase 2 of the vapor-compression cycle 2. - As shown in
FIG. 5 , the refrigerant flow entering thecondenser 120 has just completedPhase 1 of the vapor-compression cycle, in which the refrigerant vapor was compressed by thecompressor 110 and experienced a rapid increase in temperature. As shown with the smaller arrows inFIG. 5 , the superheated refrigerant vapor flows through the hotrefrigerant conduit 112 in an opposite direction relative to the cooler heat absorption fluid flowing through the stackedcoil section 122 of thecondenser 120. The countercurrent tubular flow maintains a nearly constant temperature gradient over the length of the stackedcoil section 122, in which heat is conducted from the superheated refrigerant vapor into the cooler heat absorption fluid at nearly the same rate near thecondenser entrance junction 114 as at thecondenser exit junction 116. Particularly with the use of water as the heat absorption fluid, for example, which has a relatively high thermal conductivity, the countercurrent flow in thecondenser 120 allows efficient transfer of a substantial portion of the heat energy drawn from the heat exchange fluid, as well as the work energy input from thecompressor 110, into theheat sink 300. - In accordance with aspects of the present invention, a second condenser (not shown) may be provided between the
condenser 120 and theexpansion valve 130. In this region of the refrigeration cycle, sometimes referred to as the sub cool region, the refrigerant may still retain a certain amount of thermal energy that was not transferred to the heat absorption fluid during the exchange process in thefirst condenser 120. Accordingly, the second condenser may be provided to draw additional thermal energy from the refrigerant into a fluid that may be circulated back to theheat source 200. The warm fluid may thus transfer the additional thermal energy back into theheat source 200 for storage and further use as described above. - The heat exchange system of the present invention draws on the thermal energy contained in the
heat source 200, which may be a tank of water at ambient temperature, for example, and by way of the vapor-compression cycle 2, deposits the withdrawn thermal energy efficiently into theheat sink 300, which may be another tank of water, for example. Theheat sink 300 may thus reach temperatures of more than 150° F. As shown inFIG. 4 , the hot water in theheat sink 300 may be drawn and pumped throughpipes 400 to a radiant heating system, for example, or a hydronic coil and blower arrangement that is connected to a ducting system, in order to provide a constant and efficient source of heat for the interior of a structure. In addition, a domestic hotwater storage tank 500 may be connected to theheat sink 300 to heat exchange thermal energy into the hotwater storage tank 500 for potable water use. -
FIG. 6 shows an enlarged cutaway view of anexemplary heat sink 300 in accordance with aspects of the present invention. Thefluid flow conduits 317, which may be wrapped in insulating material to prevent the escape of thermal energy to the environment, may run from theheat sink 300 to theheat exchange system 100 and back to complete a closed loop, for example. Additionally, aheat exchange coil 318, comprised of copper, or any other suitable material having high thermal conductivity, may be provided inside theheat sink 300 to facilitate heat exchange from the hot water in thefluid flow conduits 317 into theheat sink 300. The hot water may then be drawn into thepipes 400 to supply a radiant heating system, for example. - As shown in
FIG. 6 , the domestic hotwater storage tank 500 may connect to theheat sink 300 bypipes 502, which may be insulated, to conduct heat from the hot water in theheat sink 300 by way of heat exchange coils 504, also placed in theheat sink 300. As such, the domestic hot water system may be completely separate from the heatsink circulation system 310, the efficient heat exchange system thus providing the thermal energy for potable hot water use in a safe and cost-effective manner. - As shown in
FIGS. 3 and 4 , in accordance with aspects of the present invention, an electronic control unit (ECU) 540 may be provided to control operation of thecompressor 110 and the circulation pumps 215 and 315. TheECU 540 may operate with one or more thermostats, for example, to maintain the system in an efficient operating range. For instance, theECU 540 may set thecompressor 110 and the circulation pumps 215 and 315 to run if the temperature of the water in theheat sink 300 drops below a certain efficiency threshold temperature, for example, or alternatively, if the temperature of the water in theheat source 200 rises above a certain efficiency threshold temperature. In another aspect of the present invention, as shown inFIG. 3 , athermal energy source 220 may provide supplemental thermal energy to the heat source cycle when a temperature gauge in theheat source 200 indicates to theECU 540 that the temperature of theheat source 200 has dropped below a predetermined efficiency threshold. Thethermal energy source 220 may be any suitable source for heating the heat exchange fluid 205, such as a conventional hot water heating element of a predetermined wattage, for example, placed within thefluid flow conduit 217. Other exemplary thermal energy sources in accordance with aspects of the present invention may include the abundant heat sources in restaurants from which the thermal energy can be drawn upon and deposited, through heat exchangers, for example, into theheat source 200. Using a hydronic coil, piping and pumps, for example, the heat retained in the elevator penthouses of buildings can be transferred into the heat source cycle. Any ready source of heat that can be practically transferred into theheat source 200 may be used as thethermal energy source 220, including “hot spots” found in swimming pools, drain pipes, transformer rooms, data centers, computer rooms, and the upper space in certain high-ceiling rooms, to name just a few. The techniques to capture and transfer the thermal energy from athermal energy source 220 may typically include hydronic systems, but any suitable method of transferring thermal energy from a secondary source of heat to theheat source 200 is contemplated herein. - As shown in
FIG. 4 , in accordance with aspects of the present invention, theheat exchange system 100 may be fitted with an electronicpressure control unit 550. In combination with one ormore pressure transducers 552, the electronicpressure control unit 550 may be set up to monitor the sensed pressure at any point in the system, including the intake (suction) pressure and the discharge (head) pressure of thecompressor 110. Accordingly, measurement of the evaporator pressure and/or the condenser pressure can provide valuable insight into the efficiency of the system and whether the refrigerant charge is too low or excessive, for example. As shown inFIGS. 3 and 5, asight glass 135 may also be used to aid in the inspection of the refrigerant charge level, as bubbles in the line generally indicate an undercharge. Thesight glass 135 is preferably located on the high-pressure liquid side of thecompressor 110. In another aspect of the present invention, as shown inFIG. 3 , a filter drier 137 may be installed in the refrigerant path, preferably on the high-pressure liquid side of thecompressor 110, to adsorb unwanted moisture in the refrigerant cycle. - According to aspects of the present invention, the refrigerant charge in the vapor-
compression cycle 2 may be precisely determined in accordance with a length of the refrigerant run and the desired characteristics of a well-balanced heat exchange system. The R-410A refrigerant charge may be intentionally set to a level that allows the system to continue to operate at maximum efficiency, while increasing the discharge temperature of the superheated vapor discharged from thecompressor 110. The unexpected results of the present invention call for a substantially lower refrigerant charge than normal to achieve the desired results of an efficient heat transfer between theheat source 200 and theheat sink 300. - The use of R-410A enhances the ability to increase the temperature on the discharge side of the
compressor 110, but requires much higher pressures to operate compared to previously used refrigerants. For example, to achieve a condensing temperature value of 140°, an R-410 high-side pressure must approach 550 psi. In other words, for the heat absorption fluid running through thecondenser coil section 122, which is generally maintained at a temperature of 140° or higher, to condense the superheated vapor of the refrigerant in theconduit 116, the pressure on the condenser side of the heat exchanger must approach 550 psi or higher. By using ascroll compressor 110 rated to handle 650 psi before disengaging, and using tubes and fittings rated to withstand the elevated temperatures and pressures of an R-410A charged system, theheat exchange system 100 can handle the higher pressures required to produce the higher compressor discharge temperatures necessary to ensure heat exchange occurs in the condenser at temperatures above 140° F. - As heat energy is transferred from the
heat source 200 to theheat sink 300, the temperature of theheat source 200 lowers. Depending on the heat load demand, and the size of the body of water, for example, that is serving as theheat source 200, the temperature of theheat source 200 may drop significantly. Due to the parallel, concurrent tubular flow design of theevaporator 140, and the ability to generally maintain theheat source 200 in an ambient environment, the liquid refrigerant typically draws enough latent heat to effectively boil the liquid refrigerant and deliver vapor with enough pressure to thecompressor 110 to function highly efficiently. In fact, a slight lowering of the refrigerant charge so that the intake side pressure is slightly lowered, while still preventing liquid refrigerant from being delivered to thecompressor 110, may slightly elevate the compression ratio of thecompressor 110. The higher compression ratio in turn may transfer more compression energy to the refrigerant during compression resulting in an even higher discharge temperature so that the heat absorption fluid can be heated to even higher temperatures. - The
colder heat source 200 may also be used as a cooling medium for chilling water or providing cool air by employing the same water-to-water or water-to-air heat transfer means discussed above with respect to the hot water side. For example, hydronic coils, which draw upon the cold water created in theheat source 200, may be used in combination with a fan to blow hot air across the hydronic coils to produce cooler air for the air conditioning of a particular structure. Similarly, as in the case of a domestic hot water tank, a separate cold water heat exchange system and storage tank, for example, can provide chilled water for a variety of uses. - Features in accordance with aspects of the present invention include configuring the components of the
heat exchange system 100 to be compact, modular and/or portable, for example. As shown inFIG. 4 , ahousing unit 600 may havemultiple shelves heat exchange system 100, such as thecompressor 110, thecondenser 120, theexpansion valve 130, and theevaporator 140. Various quick install features may be included to enable the easy installation and/or disassembly of theheat source 200 and/or theheat sink 300, including hose bibs (not shown), for example, for quickly connecting/disconnecting thefluid flow conduits heat exchange system 100. Mounting brackets may be provided to allow for quick and efficient mounting of the various components, such as thecompressor 110, thecondenser 120, theevaporator 140 and the circulation pumps 215 and 315. Rubber padding, insulation, panels, doors and/or a cover may be provided that permit easy assembly/disassembly and access to the interior components for maintenance, while reducing the vibration, sound and heat loss that may be generated during operation of theheat exchange system 100. Thehousing unit 600 may be provided with a surface for mounting an integrated electric panel. As such, the heat exchange system may be prewired and ground to the integrated electric panel to provide a single, efficient connection to an external power source. Light Emitting Diode (LED) panels may be mounted to the housing unit to provide visible operational feedback to an observer with respect to various aspects or components of theheat exchange system 100. - By maintaining the modularity and portability of the
heat exchange system 100, theunit 100 may be transported to and employed easily in remote locations. A generator may be used for producing the electricity needed by thecompressor 110 and the circulation pumps 215 and 315, and access to a water source may provide both aheat source 200 and aheat sink 300 for heating and cooling purposes. -
FIG. 7 depicts aspects of an exemplary fluid management system 700 in accordance with the present invention that may be integrated with various aspects theheat exchange system 100 to provide precision balance and control for efficiently managing the varying heating and cooling load demands for an enclosed structure, for example. Thehousing unit 600 may house the primary components of thevapor compression cycle 2, such as thecompressor 110, thecondenser 120, theexpansion valve 130, theevaporator 140, thepumps ECU 540. The heatsource circulation system 210 includes theheat source 200, which may be a 225 gallon water tank, for example, connected to theevaporator 140 in thehousing unit 600 byfluid flow conduits 217. The heatsink circulation system 310 includes theheat sink 300, which may be a 55 gallon water tank, for example, connected to thecondenser 120 in thehousing unit 600 byfluid flow conduits 317. The heatsink circulation system 310 may include asecondary heat sink 350, which may be a 160 gallon water tank, for example, also connected to thecondenser 120 in thehousing unit 600. Threeway valves valves valve 360 shuts off fluid flow in the direction of theheat sink 300 and instead directs the fluid flow to thesecondary heat sink 350, thevalve 365 opens to receive the fluid flow from thesecondary heat sink 350 and is closed to receiving fluid flow from theheat sink 300. Similarly, when thevalve 360 shuts off the fluid flow in the direction of thesecondary heat sink 350 and instead directs the fluid flow to theheat sink 300, thevalve 365 opens to receive the fluid flow from theheat sink 300 and is closed to receiving fluid flow from thesecondary heat sink 350. In this manner, theheat exchange system 100 may select either theheat sink 300 or thesecondary heat sink 350 into which to deposit the thermal energy drawn from theheat source 200. - The components of the fluid management system 700, in conjunction with the components of the
heat exchange system 100, must be sized appropriately to achieve a symbiotic balance between the thermal mass of theheat sinks heat source 200, and any associated cold side heat exchange systems, while accommodating the varying heating and cooling load demands. Factors such as ambient outdoor temperatures during summer and winter months, construction materials used for building the structure, including insulation and windows, and the habits of inhabitants or tenants, for example, may have a large impact on the various system configurations used to calibrate the heat exchange system in response to the required heating and cooling load demands. - As shown in
FIG. 7 , a heatsource temperature gauge 230 may be provided to monitor a core temperature of theheat source 200. Similarly, temperature gauges 302 and 352 may be provided to respectively monitor core temperatures of theheat sink 300 and thesecondary heat sink 350. The various temperature gauges 230, 302 and 352 may communicate with theECU 540 by a set of relay switches, or any suitable circuit devices, including wireless thermostats, for example. - In this manner, the fluid management system 700 operates in balanced synchronization with the
heat exchange system 100 by monitoring the core temperatures of theheat source 200 and theheat sinks heat source 200 may be maintained to have a core temperature reading between 45 and 60° F. by cycling theheat exchange system 100 as required while theheat sink 300 maintains a temperature of 140° F. However, during colder winter months in many areas, the increased draw of stored thermal energy from theheat source 200 in order to keep theheat sink 300 at a particular temperature, 140° F. for example, may drop the temperature of theheat source 200 below a threshold temperature, impacting the efficiency of theheat exchange system 100. In particular, the ability for the heat exchange process in theevaporator 140 to function efficiently may be impacted. As such, the fluid management system 700 may be set to signal theECU 540 to turn on theheater 220 when the heatsource temperature gauge 230 reads a core temperature below 38° F., for example. Under these circumstances, theECU 540 may be programmed, for example, to continue operation of theheat exchange system 100 until theheater 220 provides enough supplemental thermal energy to the fluid flow to raise the core temperature of theheat source 200 to a preset threshold winter temperature, 45° F. for example. - Another feature in accordance with aspects of the present system may be the inclusion of a supplemental
solar heating system 800 to provide yet another source of thermal energy during peak heating demand, such as during the winter months and/or during times of peak hot water demand, for example. As shown inFIG. 7 , the supplementalsolar heating system 800 may be configured to operate in tandem with either theheat sink 300 or theheat source 200 through a heat exchange process in which solar thermal units convert solar energy into thermal heat energy that is supplied to the fluid flow of theheat exchange system 100. Threeway valves solar heating system 800 and either theheat sink 300 or theheat source 200, respectively. Thevalves valve 810 shuts off fluid flow in the direction of theheat sink 300 and instead directs the fluid flow to theheat source 200, thevalve 820 opens to receive the fluid flow from theheat source 200 and is closed to receiving fluid flow from theheat sink 300. Similarly, when thevalve 810 shuts off the fluid flow in the direction of theheat source 200 and instead directs the fluid flow to theheat sink 300, thevalve 820 opens to receive the fluid flow from theheat sink 300 and is closed to receiving fluid flow from theheat source 200. In this manner, theheat exchange system 100 may select either theheat sink 300 or theheat source 200 as the beneficiary of the thermal energy produced by the solar thermal units of the supplementalsolar heating system 800. - During peak summer months in many areas, for example, where the need for cool air may drive a peak demand on the
heat exchange system 100 for chilled water, the fluid management system 700 may be programmed to maintain the core temperature of theheat source 200 at a lower threshold summer temperature, 38° F. for example. Under these circumstances, the amount of thermal energy drawn from theheat source 200 may raise the core temperature of theheat sink 300 to levels too high for the condenser heat exchange process to function efficiently. To keep the condenser section operating at lower temperatures, the fluid management system 700 may thus be controlled to open thevalve 360 in the direction of thesecondary heat sink 350 to direct fluid from thecondenser 120 to the largersecondary heat sink 350 rather than theheat sink 300. Concurrently, the fluid management system 700 is controlled to open thevalve 365 to receive fluid from thesecondary heat sink 350 rather than from theheat sink 300. In this manner, thesecondary heat sink 350 may serve as a large depository of excess thermal energy during peak cooling demand, allowing the system to maintain the core temperature of theheat source 200 at a lower desirable temperature without distressing the efficiency of the system. - Another feature in accordance with aspects of the present invention may include providing a further mechanism for drawing off excess thermal energy in the event that the
secondary heat sink 350 also reaches a core temperature considered too elevated for the efficient operation of thecondenser 120 of theheat exchange system 100. A pipe or conduit may be provided so that fluid can be pumped from thesecondary heat sink 350 to an area where a fan and/or hydronic coils may be used to transfer the excess energy to an ambient air environment external to the structure, for example. - Another feature in accordance with aspects of the present invention may include providing a neutral tank to the configuration of the
heat exchange system 100. For example, as shown inFIG. 8 , aneutral tank 900 may be configured to operate in combination with the fluid management system 700 to serve as a temperature buffer for theheat sinks heat source 200. Because many aspects of theheat exchange system 100 and the fluid management system 700 will function as described above, a majority of the structure and functional aspects of theheat exchange system 100 and the fluid management system 700 are not repeated here. - The piping of the
heat exchange system 100 and fluid management system 700 may be modified, for example, to accommodate the introduction of theneutral tank 900. As shown inFIG. 8 , theneutral tank 900 may be configured to respectively segregate the fluid flow to theheat exchangers source circulation system 210 may be configured so that the heat exchange fluid is supplied to theevaporator 140 from theneutral tank 900, with the heat exchange fluid being returned from theevaporator 140 directly to the cold tank. Similarly, the heatsink circulation system 310 may be configured so that the heat absorption fluid is supplied to thecondenser 120 from one of theheat sinks neutral tank 900, or a combination of theheat sinks neutral tank 900, and the heat absorption fluid is returned from thecondenser 120 directly to theheat sink neutral tank 900. In this manner, both theheat sinks heat source 200 may be spared from the influence of the reduced or elevated temperature of the fluid returning from the heat exchange process (e.g., hydronic coils and air handler) that resulted in the respective heating or cooling of the objective space. - For example, during cool months, the temperature of the fluid supplied from the heat sink(s) 300, 350 to the hydronic coils is reduced through the heat exchange process in order to supply heat to the objective space. As a result, the
neutral tank 900 permits the cooler fluid returning from the hydronic coils to be deposited into theneutral tank 900, rather than back into the heat sink(s) 300, 350. Similarly, during warmer months, the temperature of the fluid supplied from theheat source 200 to the hydronic coils is elevated through the heat exchange process (e.g., hydronic coils and air handler) in order to cool the objective space. As a result, theneutral tank 900 permits the warmer fluid to be deposited into theneutral tank 900, rather than back into theheat source 200. In this manner, theheat sinks heat source 200 may deliver fluid at temperatures that have not been tempered by fluid returning from the heat exchange process used to heat or cool the objective space. Thus, the fluid delivered to the hydronic coils, for example, may be maintained at temperatures that are more effective for heating or cooling of the structure, while the temperatures of the fluids in theheat sinks heat source 200 may be more consistently controlled, enhancing the operation and efficiency of the system. Theneutral tank 900 may thus buffer theheat sinks heat source 200 from large fluctuations in temperatures that may be associated with peak system demand, for example. In turn, the operation and efficiency of theheat exchangers heat sinks heat source 200. Although described above as a tank, theneutral tank 900 may be any suitable receptacle for the storage and maintenance of a heat exchange medium in accordance with aspects of the present invention. - While this invention has been described in conjunction with the exemplary aspects outlined above, various alternatives, modifications, variations, improvements, and/or substantial equivalents, whether known or that are or may be presently unforeseen, may become apparent to those having at least ordinary skill in the art. Accordingly, the exemplary aspects of the invention, as set forth above, are intended to be illustrative, not limiting. Various changes may be made without departing from the spirit and scope of the invention, including increasing the size of various components, including the heat source, the heat sinks, and/or the neutral tank, for example, to scale the system appropriately for different applications. Therefore, the invention is intended to embrace all known or later-developed alternatives, modifications, variations, improvements, and/or substantial equivalents.
Claims (18)
1. A modular heat exchange system comprising:
a refrigerant system which cycles a refrigerant through a compressor, a condenser, an expansion valve, and an evaporator;
a heat source circulation system which circulates a heat exchange fluid between a heat source and the evaporator;
a heat sink circulation system which circulates a heat absorption fluid between a heat sink and the condenser;
a heat exchanger for exchanging thermal energy between one of the heat exchange fluid or the heat absorption fluid; and
a neutral tank, wherein the one of the heat exchange fluid or the heat absorption fluid is deposited in the neutral tank upon returning from the heat exchanger.
2. The modular heat exchange system of claim 1 , wherein the refrigerant is R-410A.
3. The modular heat exchange system of claim 1 , wherein the heat exchange fluid is water.
4. The modular heat exchange system of claim 1 , wherein the heat absorption fluid is water.
5. The modular heat exchange system of claim 1 , wherein the heat source circulation system further comprises a fluid flow conduit connecting the heat source to the evaporator.
6. The modular heat exchange system of claim 1 , wherein the heat exchanger comprises hydronic coils.
7. The modular heat exchange system of claim 1 , wherein the heat source is a body of water.
8. The modular heat exchange system of claim 7 , wherein the body of water is contained in a heat source storage tank.
9. The modular heat exchange system of claim 1 , wherein the heat sink is a body of water contained in a heat sink storage tank.
10. The modular heat exchange system of claim 1 , further comprising a thermal energy source, wherein thermal energy is transferred from the thermal energy source to the heat exchange fluid when the core temperature of the heat source falls below a threshold temperature while the core temperature of the heat sink is maintained at a constant temperature.
11. The modular heat exchange system of claim 10 , wherein the heat absorption fluid is cycled through the solar energy thermal unit to maintain the core temperature of the heat sink.
12. The modular heat exchange system of claim 11 , further comprising a first valve and a second valve, wherein the first valve and the second valve work in tandem to cycle only one of the heat exchange fluid and the heat absorption fluid through the solar energy thermal unit.
13. The modular heat exchange system of claim 1 , wherein the heat sink is one of a primary heat sink or a secondary heat sink.
14. The modular heat exchange system of claim 13 , further comprising a first sink valve and a second sink valve, wherein the first sink valve and the second sink valve work in tandem to cycle the heat absorption fluid to only one of the primary heat sink and the secondary heat sink.
15. The modular heat exchange system of claim 14 , wherein the heat absorption fluid is cycled to the secondary heat sink when the core temperature in the primary heat sink determined by the second temperature gauge rises above a threshold temperature while the core temperature of the heat source determined by the first temperature gauge is maintained at a constant temperature.
16. The modular heat exchange system of claim 10 , wherein the thermal energy source is a solar energy thermal unit.
17. The modular heat exchange system of claim 1 , wherein the heat exchange fluid is supplied to the evaporator by the neutral tank.
18. The modular heat exchange system of claim 1 , wherein the heat absorption fluid is supplied to the condenser by one of the neutral tank or the heat sink.
Priority Applications (1)
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US12/829,060 US20110154838A1 (en) | 2009-08-18 | 2010-07-01 | Heat exchange system |
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US12/543,268 US20110041535A1 (en) | 2009-08-18 | 2009-08-18 | Heat exchange system |
US12/752,585 US9027359B2 (en) | 2009-08-18 | 2010-04-01 | Heat exchange system |
US12/829,060 US20110154838A1 (en) | 2009-08-18 | 2010-07-01 | Heat exchange system |
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US12/752,585 Continuation-In-Part US9027359B2 (en) | 2009-08-18 | 2010-04-01 | Heat exchange system |
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US12/829,060 Abandoned US20110154838A1 (en) | 2009-08-18 | 2010-07-01 | Heat exchange system |
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CN103953966A (en) * | 2014-05-16 | 2014-07-30 | 中国科学院工程热物理研究所 | High-capacity heat storage system and high-capacity heat storage method for increasing wind energy absorption |
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CN105517405A (en) * | 2014-09-22 | 2016-04-20 | 广东申菱环境系统股份有限公司 | Control method of heat pipe internal circulation type server cabinet heat dissipation system |
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US10384982B2 (en) | 2015-09-09 | 2019-08-20 | Planet Found Energy Development, LLC | Waste material processing system |
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CN105430998A (en) * | 2014-09-22 | 2016-03-23 | 广东申菱环境系统股份有限公司 | Control method of fluorine-pump internal-circulation server cabinet heat radiation system |
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